Note : Les descriptions sont présentées dans la langue officielle dans laquelle elles ont été soumises.
CA 02786315 2012-08-24
PISTON-CHAMBER COMBINATION - Vanderblom Motor
NVB Composites International UK Ltd, United Kingdom
O/R: 19618-PCT
Part 1/2 specification
CA 02786315 2012-08-24
0 40
19619 - Piston - Chamber Combination Vanderblom Motor 25-02dar,
1961 Q8 TECHNICAL FIELD
A piston-chamber combination comprising a chamber which is bounded by an inner
chamber
wall and comprising an piston inside said chamber wall to be engagingly
movable relative to said chamber
wall at least between first and second longitudinal positions of said chamber,
said chamber having cross-
sections of different cross-sectional areas and differing cireumpherential
lengths at the first and second
longitudinal positions of said chamber and at least substantially continuously
different cross-sectional
areas and different cireurnpherential length at intermediate longitudinal
positions between the first and
second longitudinal positions thereof, the cross-sectional area at the first
longitudinal position being larger
than the cross-sectional area at the second longitudinal position, said
actuator piston comprising a
container having an elastically deformable container wall for engagingly
contact with the chamber wall,
said container being elastically deformable to provide for different cross-
sectional areas and differing
circrmiferential lengths of the piston for adaptation to said different cross-
sectional areas and different
circumferential lengths of said chamber during the relative movements of said
piston between the first and
second longitudinal positions through said intermediate longitudinal positions
of said chamber the actuator
piston is produced to have a production-size of the container in the stress-
free and undeformed state
thereof in which the circumferential length of the actuator piston is
approximately equivalent to the
circumferential length of said chamber at said second longitudinal position.
Z
1961' BACKGROUND OF THE INVENTION
This invention deals with solutions for alternatively and efficiently
functioning actuators, in relation to
existing actuators, and with the important goal of such actuators for fighting
climate change, in motors,
and specifically car motors. Additionally deals this invention with solutions
for an efficient shock
absorber, and a pump.
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This invention deals specifically with solutions for the problem of obtaining
a motor, which does not use
n bust,tale..teebniques-oLaiLdenivateslike_peteol, diesel, andvabich-can.
competo_with-surnÃnt-maters--
based on said combustible technics. And additionally to comply with the demand
for reducing CO,
emission, so as to compete as well with combustible motors based on Hi, or
even air, as it does not need
new distribution networks for providing the energy source for the motor.
The combustible motor based on oil deverates is after today's technical
standards only an
optimized version of a concept which is approximately one century old. This
means that it does not
comply anymore to today's standards of living: a waist of valuable and limited
available oil, and a
source of pollution, such as emission of amoung others toxic gasses like CO,
and gasses like CO7 which
is an important cause of the climate change. Additionally combustible motors
tend to be heavy, so that
the Transport Weight Ratio (= weight of one person in relation to the weight
of what is being
transported in total) may be approx. 12 (small passenger car) - 33 (limosine,
4 wheel drive) for a
passenger car
The new combustible motors based on H,; or even air are ladling the
distribution network for
deliverance of the energy sources for said motors, such as petrol stations
today for the delivery of petrol,
diesel and NLG gas. Even the rearms motor functioning on air needs 'filling'
stations for providing the
necessary high compressed air in large and heavy cylinders - the lack of such
a distribution network was
the reason why said motor on air is constructed in such a way that is also can
function on combustible
means e.g. petrol or diesel - thus back to the Otto Motor again, which ought
to be avoided
The seeing up of new networks of providers for these last mentioned new to be
used
combustible materials needs very high financial investments, and that gives
difficulties due to the Catch
22 situation: without a proper Cure masked network will these motors not be
distributed, because
moboddy will buy such motor, due to lack of availability, and noboddy wants to
invest in the network,
before there is evidence that there is a market. For a quick introduction and
widespread distribution of a
non-polluting motor, it is necessary that this motor is independant of
networks for providing the energy
source. A current developemnt of a home filling station for H. seems an
interesting but quite on tricky
thought, because this gas is a very dangerous gas, and should only be handled
by instructed personnel.
lR~`~`g 3
tom'.
OBJECT OF THE INVENTION
The object is to provide combinations of a piston and a chamber to be used in
pumps,
actuators, shock absorbers and the use of said actuators in among others a
motor.
~
I SUMMARY OF THE INVENTION
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In the first aspect, the invention relates to a combination of a piston and a
chamber, wherein-
the combination comprises means for introducing fluid from a position
outside said piston said container, thereby enabling pressurization of said
container, and thereby expanding said container and displacingsaid container
between second and first longitudinal positions of the chamber.
A classic actuator piston is positioned in a straight cylinder, and said
piston is comprising a
piston rod It is moving as a consequence of a pressure difference between both
sides of said piston - the
last mentioned may be a piston, which is made of a non-elastic material and
comprising at least a sealing
ring, sealing the piston to the cylinder wall, in which the piston is
relatively moving to said cylinder. A
piston rod may be gabled by a bearing on one or both sides of the cylinder.
The piston rod outside the
cylinder may be pushing or putting an external device. It may also he engaging
a crank shaft, so that a
rotation occurs of the crank shaft axel, which may result in motion of eg- a
vehicle, comprising said
actuator and crank shaft.
The actuator piston, when positioned in a straight cylinder may also be an
inflatable piston, e.g.
a container type piston according to claim 5 and claims 28 and 34 of FP 1 179
140 R1 if said inflatable
piston has been pressurized inside, its, preferably reinforced, wall may
engage or seal, respectively to
the wall of the cylinder, and may act regarding its motion in said cylinder,
as the above mentioned
. classic piston in said straight cylinder. For enabling the motion, a valve
on both sides of the piston, e.g.
in the wall of the chamber, may be necessary, and a fluid in the cylinder on
both sides of said piston
with a certain pressure difference, preferably controlled by control means.
Changing the size of the
pressure inside the last mentioned container ..It may only have an influence
on the ability to engage or
seal of said piston wall, to the wall of the chamber. Still, through the
friction between the wall of the
25- container, and the wall of the chamber, said internal pressure may have
inflnence on the speed ov the
motion of the piston
An actuator according to the invention is a piston chamber combination which
has an iti latable
piston. Inside the piston may preferably be a fluid and/or a foam under a
certain pressure, the piston of
which its wall comprising material(s) and preferably reinforcement(s)) may
allow it to change shape
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and/or she, and the piston may be moving in the chamber or vice versa
preferably withdut the need for
a fluid in the chamber and/or without a pressure difference of said fluid or
foam on both sides of the
piston in the chamber - a fluid in the chamber may of course still be present
as e.g- air at atmospheric
pressure, e.g. for control purposes-
A further necessary parameter may be that the wall of the chamber is not
parallel to the centre
axis of said chamber, while the angle of said chamber wall in the direction of
the intended motion of the
piston has a positive value, so that the piston can expand in said direction
Expansion may preferably be
done from a second longitudinal position of the piston, where the piston has
its smallest circumferential
size: its stressfree production size, to a first longitudinal position of said
piston, where the piston has its
biggest circumferential size - please see EP 1 384 004 BI
The motion of the piston may be initiated by the forces towards the inner
chamber wall of said
container type piston which arise, when the container is expanding. Thos said
motion may be initiated
by reaction forces from the wall of the chamber to the wall of [he container.
These forces are a reaction
on the expansion of the wall of said container, and said expansion may be a
consequence of increasing
the- volume and/or pressure of the fluid in the piston, as a result of the
introduction of more fluid
through an enclosed space from a position outside said piston to said
container.
In a working prototype of a piston according in Figs. 7A-C (WO 2004/031583)
with a
reinforcement of Fig, 8D (WO 2004/031583) is the piston rocketing from a
second longitudinal position
to a first longitudinal position, and if unloaded, with a fluctuating speed to
a chamber with a so-called
constant maximum working force shape (WO2008/025391 - Fig-6B), already at a
few Bars
overpressure inside the piston in relation to the atmospheric pressure, which
was present at both sides of
the piston in the chamber, and with a fluctuating positive angle of the inner
chamber wall with the centre
axis of said chamber in the direction from a second to a first longitudinal
position. Said experienced
fluctuation of the speed of the piston is explained below.
The contact between the wall of the container and the wall of the chamber may
be engagingly
or sealingly. It depends more or less on the load on the piston rod, as said
prototype reveals. With no
load on the actuator, the contact may be engagingly, and not sealingly. With a
load on the actuator, the
driving forces on the container are bigger than in the case without a load on
said actuator, which is why
there may be enough force on the chamber wall from the wall of the container,
so that the contact
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between said walls is sealingly_ It may also be that during a move of the
piston the contact with the wall
of the chamber may be sequencially engagingly and sealingly.
The reasoning why the piston is moving may be as follows. If the longitudinal
component of
the reaction force from the wall of the chamber to the wall of the container,
which is directed to a first
tbsgitudmal piston position, is bigger than the longitudinal component of the
friction force between the
wall of the chamber and the wall of the piston, which is directed to a second
longitudinal piston position,
the total resulting force will be directed toward a first longitudinal piston
position, and consequently the
piston will move from second to first longitudinal positions. As preferably
the end of the container
closest to a second longitudinal piston position is fastened to the piston rod
by a cab (192), the piston rod
will move as well. A self-propelling actuator has been born, which may be the
alternative for a piston
which is moving by a pressure difference outside said piston, inside the
chamber. Preferably is the other
end of the container slidingly movable over the piston rod by means of a cab
(191), which means to that
the expansion of said container brings said cabs (191) and (192) closer to
each other, by the movement
of cab (191) toward the cab (192) over the piston rod. This is due to the
chosen reinforcement-of the
wall of the container, which is preferably a one layer of reinforcement
strengs directed frown cab (191)
to cab (192), which lies in a plane which is parallel to the centre axis of
said chamber (e.g.
W02004/031583, Fig.BD), and optionally with a slight angle with the centre
axis of the chamber and/or
at lest two layers of reinforcements crossing each other with a very small
angle -
Due to the positive slope of the wall relative to the centre axis of said
chamber in the direction
of first longitudinal piston positions, and the fact that the contact surface
of the piston and the wall of the
chamber is positioned in the longitudinal direction preferably under the
middle point of the elastically
deformable Will of the piston, optionally approximately just under said middle
point of the elastically
deformable wall of said piston, said movement will result in au expansion of
the wall of the container.
Thus the original contact area between said walls will become larger, and an
increased friction force
results Said motion may slow down, as the total resulting force toward first
piston positions decreases.
Approximately'at the same fire that the wall of the container between said
increased contact
area and said movable cap is expanding, said motion will result in that the
cap (19)), the movable end of
the piston, is coining closer to the cap (192) which is fastened to the piston
rod. This means that due to
the still present overpressure inside said container (the volume of the
enclosed space may need during
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the motion from second to first longitudinal piston positions to be constant),
the reinforcement in the
wall of said container, said wall is expanding as well more round nearest a
second longitud t odtion
This means that the wall of the container is rolling over the wall of the
chamber, so that said contact
area moves toward first longitudinal positions, thereby increasing the
component of the reaction force of
- the wall of the chamber to the wall of said container. The component of the
resulting force toward first
longitudinal piston positions will increase and will become rapidly bigger
than the friction component,
to that the part of the comaiaer closest to the second longitudinal piston
position is moving with
increasing speed toward first longitudinal piston positions, thereby taking
the non-movable cap (192)
with it, thus also the piston rod - the piston is moving from a second to a
first longitudinal piston
to position. -
The overpressure is measured in relation to the atmospheric pressure, which is
why when the
piston may be positioned inside a dosed chamber, the last mentioned may need
on both sides of the
piston to be able to communicate with its surroundings of the combination,
which may preferably he
under atmospheric pressure.
1 S Instead of the enclosed chamber space may the fluid in the chamber
communicate with an
enclosed chamber space, so that fluid in the chamber is not prohibiting said
movement of said piston.
This is a concept which may be used in a shock absorber.
Whether or not an enclosed chamber space or a channel to the atmospheric
surroundings may
be necessary depends on the sealing ability of the piston to the chamber wall.
A leakage of the piston to
20 [he wall may also dun, and may be present, as a 100% sealing of the piston
to the chamber wall may not
be necessary (engaging). Thus, a channel which connects the spaces of the
chamber on each side of said
container, may be interconnected by a channel, which said piston is
comprising.
Said piston may comprising an enclosed space, e.g. a hollow piston rod. The
inside of said
piston may be communicating with said enclosed space. The volume of said.
enclosed space may be
25 constant or variable, and adjustable. Said enclosed space may be
eommunicaling with a pressure source.
1- the second aspect, the invention relates to a combination of a piston and a
chamber, wherein:
A piston-chamber combination further comprising means for removing fluid
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from said container through said enclosed space to a position outside the
piston,
thereby enahlinn contraction of said con[a ner _~
The movement during the return part of the stroke of said piston from its
first longitudinal
position to a second longitudinal position may be done by at least three
possible ways.
The traditional way, where the piston is seali gty engaging the wall of the
chamber Said movement
however may cost energy, because the surplus of the fluid inside the container
type piston, which is
shrinking and by that is reducing its internal volume, may be transported
towards said enclosed space, of
which its internal pressure may increase. In order to save energy, the piston
may engage, but not seal to
the wall of the chamber - this will reduce the friction farce berween said
piston and said chamber wall.
The last way may be done by reducing the internal pressure of the container
during said part of the
stroke, by sucking Oct the fluid from the container That may be accomplished
by controlling means,
controlling the pressure in said enclosed space.
In the third aspect, the invention relates to a combination of a piston and a
chamber. wherein:
the piston is movable relative to said chamber wall at least from first to
second
longitudinal positions of said chamber.
It may be possible to move the piston from first to second longitudinal
positions, whithout
engaging the wall of the chamber. This may be done by reducing the pressure
inside die piston to a
minimum level, e.g. that the wall of the piston is stressfree and its
circumference is that of its production
size at a pressure when it was produced (e.g. the atmospheric pressure), so
that the piston can arrive at a
second longitudinal position withoutjamming. - - -
In the fourth and fifth aspects, the invention relates to a combination of a
piston and a chamber,
wherein
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the piston is comprising a piston rod, which is comprising said enclosed
space.
the piston is comprising engaging means outside said chamber-
The suspension of the piston rod may be special, e.g. according to those
bearing types shown
in W020091O25391, in order to guide the pistmt sharing said pan of the stroke,
whithout the guidance of
the piston itself, if the piston would not engage the wall of the chamber.
The piston rod may be extending from the piston in one longitudinal direction,
and guided by a
bearing at an end of the chamber. That means that the piston rod may
comprising the enclosed space,
and also comprising an engaging means, e.g. positioned outside the chamher.
The engaging means may
be pushing or pulling when the piston is moving from second to first
longimdinal positions. The other
way around would the engaging means not be able to push nor to pull. A force
outside the piston may be
driving the piston from first to second longitudinal positions. When the
piston may not be seatingly
moving from first to second longitudinal positions, a force on the piston rod
may be driving the piston,
when the piston is comprising the piston rod. This may be accomplished by said
engaging means.
tt may however also be possible that the piston is comprising a piston rod
which extends in two
longitudinal directors, and one piston rod may normally be a continuation of
the o[her. One or both
piston rusts may comprising engaging means, e.g. positioned outside the
chamber. When both piston rod
ends may extend onside the chamber, one bearing of the piston rod may be
fastened rigidly to the
climber, while the other may be floating in relation to the chamber. The
engaging means may be
pulling and pushing at the same time, when the piston is moving from second to
first longitudinal
positions. The other way around - the remm stroke - would the engaging means
not be able to push nor
to pull. A force outside the piston may be driving the piston from first to
second longitudinal positions.
When the piston may not be seatingly moving relative to the chamber fiom first
to second longitudinal
positions, a force on the piston rod may be driving he piston, when the piston
is comprising the piston
rod_ This may be accomplished by said engaging means.
In the sixth and seventh aspect, the invention relates to a combination of a
piston and a chamber, of
which the piston rod is connected to a crankshaft, wherein:
CA 02786315 2012-08-24
Io
a crank is adapted to translate the motion of the piston between
second and first longitudinal positions of the chamber into a rotation
of said crank.
the crank is translating As rotation into a movement of the piston from
first to second logitudinal positions of the piston.
The engaging means may be a crankshaft, which is connected to the piston by
said piston rod. In order
to be able to at least initiate the motion of the piston from first to second
longitudinal positions of the
chamber, the crankshaft should turn before said motion commences by said
piston, so that the impels of
the contra weigths of said crankshaft generated by the motion of the piston
from second to first
longitudinal positions can be transferred to the piston.
Another option is that the motion of the piston between first and second
longitudinal positions
maybe done by the motion of the crankshaft, initiated by e.g. another piston-
chamber combination, of
which the piston is simultaneously moving from second to first positions of
its chamber (at least two
cylinder, working together on the some crankshaft).
The initial motion of the piston may done be e.g. an electric motor, which
initiates and shortly
maintains the rotation of the crankshaft - a kind of starter motor - until the
crankshaft is turning by a
piston chamber combination.
In the seventh and eigth aspect, the invention relates to a combination of a
piston and a chamber, of
which the piston rod is connected to a crankshaft, wherein.
the crankshaft is comprising a second enclosed space.
the second enclosed space is communicating with a power source-
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The crankshaft may be hollow and comprising a second enclosed space. This
means that the
crankshaft anal and its contraweights are hollow, in such a way, that these
together form a channel
from a container type piston toward the end of the crankshaft axe]. With an O-
ring sealing may this
channel be communicating with a pressure source
It may also be positioned in the crankshaft inclusively the axis bearing of
said crankshaft, so that it
may be communicate with an external power source. -
Ina nineth aspect, the invention relates to a combination of a piston and a
chamber,
to wherein: -
said second enclosed space is communicating with the first enclosed space
in the piston rod during a period of the time when the piston is moving from
first to second
longitudinal positions of the chamber.
i5 During the part of the stroke from first to second longitudinal positions,
the piston
may be depressurized to a certain pressure level at which the piston was
produced, and this may be
done by connecting the first enclosed space in the piston to the second
enclosed spare in the
crankshaft the necessary period of time during the time when the piston is
moving from first to
second longitudinal positions. The pressure level under which the piston was
produced may not he
20 atmospheric pressure, but may be any pressure level. The higher the
pressure level is, the less energy
may be lost, when the first and second enclosed space are connecting to each
other.
In a tenth aspect, the invention relates to a combination of a piston and a
chamber, wherein
said crankshaft is comprising a third enclosed space, which is
25 communicating with the first enclosed space of the piston rod during a
period of the time when the
piston is moving from second to first longitudinal positions of the chamber.
This third enclosed space has the function to pressurize the piston again,
when its
movement changes direction from moving toward a final second longitudinal
position of the chamber
CA 02786315 2012-08-24
t2
towards a first longitudinal position of the chamber. The pressurization is
done by connecting the
third_enrdtaced~gace, wh;rh hac vnpressure..inselation_t0.the_Custenclosed~pnc
tthR--
enclosed space. Pressurization may be done as quickly as possible after the
motion of the piston has
changed direction. -
In an eleventh aspect, the invention relates to a combination of a piston and
a chamber, wherein'
said third enclosed space is communicating said second enclosed space during a
period
of the time when the piston is moving from second to first longitudinal
positions of the
chamber.
Ill
A shock absorber comprising:
a combination according to all earlier mentioned aspects,
means for engaging the piston from a position outside the chamber, wherein the
engaging means have an outer position where the piston is at the first
longitudinal position of the
15 chamber, and an inner position where the piston is at the second
longitudinal position.
A shock absorber may further comprising an enclosed space, which may
communicating with the
container. The enclosed space may have has a variable volume, or a constant
volume. The volume
may be adhjustabte.
20 A shock absorber may comprise the container and the enclosed space which
may forming an at least
substantially sealed cavity comprising a fluid, the fluid may be compressed
when the piston moves
from the first to the second longitudinal positions of the chamber.
A pump for pumping a fluid, the pump may comprising means for engaging a
second piston in a
25 second chamber from a position outside the chamber, a fluid entrance
connected to the second
chamber and comprising a valve means, and a fluid exit connected to the second
chamber-
A pump wherein the engaging tneaos may have an outer position where the piston
may be at the first
longitudinal position of the chamber, and an inner position where the piston
may be at the second
longitudinal position of the chamber.
CA 02786315 2012-08-24
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second longitudinal position of the chamber, and an inner position where the
piston imay be at the
first longitudinal position of the chamber.
The technology of the piston-chamber combinatoion may be used in a motor,
specifically in a car
motor - specifically the self-propelling actuator.
The piston may also move relatively with the taped wall, within a chamber,
which may be
cilindrical, or conical (not shown).
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CA 02786315 2012-08-24
K(11 395}6 SUMMARY OF THE INVENTION - feasibility study
The feasibility study for a `green' motor is as follows - please review Fig.
10B and Fig. llB
which gives a good helicopter view on the issue. This is a system, where the
output of the motor is
being generated by a new propulsion system, where an inflatable actuator
piston in a chamber with -
contineously differing cross-sectional area's, is moving by means of internal
pressure from a smallest
cross-sectional area to a bigger one, thereby decreasing internal pressure,
while during the return stroke
the fluid of said actuator piston is further depressurized, wherein said fluid
is being repressurized by a
cascade primping system using the energy efficient piston-chamber combination
according to
W02000/07tl227, of which at least one step is being energized by an external
green power source, e.g.
the sun, or preferably any other sustainable power source, or optionally a non-
sustainable power source.
Still more efficient and reliable solutions can be seen in Figs. 11G and 13F.
That system is complying to
the erarlier stated specifications.
TRANSLATIONAL POWER SOURCE for a `green' motor based on the principle of Fig.
I IA
The overall system solution regarding this invention is, that said `green'
motor as such may he
based on comparable construction elements as currently used in combustible
engines, but that the new
construction elements need to function much more efficiently than those of
current combustible motors,
and so much more, that the energy used, may be obtained from preferably a
`green' energy source, e.g.
like the sun, combustion of Hi generated preferably when the motor is running
by e.g. electrolyses, or
optionally by a lh refillable storage tank + fuel cell, and/or from a pressure
storage vessel, containing a
pressurized fluid, preferably of low pressure (e.g. approx. 10 Bar),
optionally of high pressure (e.g.
<300 Bar) Filled once and for all while the motor is produced and preferably
repressurized during
operation of said motor, optionally refilled when the motor is out of
operation, and/or a battery, charged
when the motor is produced, and preferably contineously recharged when the
motor is running, and/or
optionally recharged when the motor is not running, and from the system
itself, preferably because the
energy needed may be less than the available total energy which the system may
perform for the task of
generating motion, optionally from another power source
It
CA 02786315 2012-08-24
W020001070227 discloses a piston-chamber combination technology which can save
a
substantial amount of energy e.g. up to 65 % energy for a pump at 8 Bar (the
current working pressure
of car motors) - e.g. 10 Bar in a tube with an o17 mm (from a 60mm at first
longitudinal positions), at
second longitudinal piston positions, if the smallest cross-sectional area of
a chamber is positioned there
where the highest pressure occurs: at a second longitudinal position. The
other way around, by using
said technology in an actuator instead of a pump, is of even efficiency.
W02004/031583 discloses an
expandable piston type (e.g. ellipsoide sphere: small sphere big sphere) which
is not jamming in
mid chamber, when the non stressed production size of a piston has a
circumference, which is
approximately the size of the circumference of that part of said chamber which
has the smallest cross-
sectional area: this may be at a second longitudinal position. This piston
type shows special
characteristics, used as an actuator piston in said chamber, and these
characteristisc are claimed in this
invention* the actuator is self-propelling, if said piston is pressurized
through its enclosed space from a
pressure source outside said chamber, at said second longitudinal position,
and when there is no pressure
difference between both sides of said piston in said chamber, while there is
an angle net being zero
between the wall of the chamber and Use centre axis of said chamber - in a
working prototype is the
actuator piston expanding and rocketing with 260 N to first longitudinal
piston positions, where the
cross-sectional area is largest, in a chamber which has been designed having a
constant maximum
working force of 260 N (W020081025391, W02009/083274). This phenomenon may be
used in this
`green' motor, thereby exchanging motion based on energy derived from
combustible technics, however
still using a crankshaft. The energy used due to the expansion may be
approximately 5 Bars (e.g. from
10 Bar to 5 Bar overpressure, due to an increase of the piston's volume), e.g.
from ellipsoide sphere
by a constant volume of the enclosed space (W020091083274). This pressure drop
has to be re-gained
in the system, because in the return stroke, the actuator piston needs to
become unstressed at a second
longitudinal piston position, where it has its production size, thus with e.g.
0 bar internal overpressure.
The 5 Bar overpressure at first longitudinal piston positions can be re-used,
when the piston's enclosed
space is connected to another enclosed space, which may be positioned e.g.
within the crankshaft, and
which is through an e.g. two-stepped pumping process, increasing the pressure
from 5 Bar to 10 Bus
again. This may be done efficiently by using another aspect of the piston-
chamber combination
technology which is disclosed in W02000/070227, so that in the
repressurization process also a 65%
CA 02786315 2012-08-24
energy maybe saved: e.g. by using a piston based on e.g. claim 1 of
EP1179140131 or on Figs-5A- 511
of W02000/065235, of which further developments are additionally claimed in
this invention. From
these 65% energy reduction can still additional energy be saved, by connecting
the crankshaft of said
pump to the main crankshaft of said actuator piston: say, said additional
saving may be assumed to be
35%. Thus total savings are: 76,7 % (65 + 1/3 x 35%). Thus 23,3 % of the
energy should be gained
from another pump, e.g. identical with the last mentioned, but which now is
getting its energy from e.g.
an electric motor which receives its electricity from said battery charged
optionally by asolar cell
(which should not be bigger than a roof of a common car, or a solar cells,
incorporated in the paint of a
car), or optionally by a fuel cell, or preferably by an alternator, which may
gets its rotation from an axle
of the system of the motor itself or from an axle of a small Hi combustible
engine.
The energy necessary for letting that pump function is 35 % of the 23,3 %
which is 8,2 %
Neither heat may be generated by mid motor, nor noise, while the weight of
this motor may be
substantially (e.g. 60%) lower than that of current combustible motors, while
almost all additional
controlling devices which a combustible motor needs, such as controlling water
temperature for cooling
purposes, oil temperature and the exhaust system, may be unnessary, as well as
a petrol tank - with an
aluminum an/or plastic body, may the future car be half of the weight of
current cars - e.g. a VW Golf
Mark II weights 836 kg; while designed and produced according to this
invention may it weight approx.
425 kgs: with only the driver present is the TWR: 6,3!
A problem remaining may be driving during a long time in the dark of the
night, when solely a
solar cell may be used for recharging said battery. However, the light of
lamps of lamp posts in the
streets of a town may give enough light for the solar energy cell.
And, a gearbox may be necessary, because the rpm's of such a `green' motor may
be lower
than that of current combustible motors.
k
Xd
1961 amended 19611 added matter to the description - feasibility study jn
!1(,8
The feasibilty study until now did not incorporate quantitatively the lack of
beat generated by a
motor of this invention, in comparison with Otto Motor types.
CA 02786315 2012-08-24
When heat loss may be incorporated, than the motor types of this invention are
still
more interesting and convincing. Heat losses may give a current Otto Motor an
efficiency of 25%.
When it may be assumed in the first instance that said motor types of this
invention do not generate
heat at all (isothermal), than it may be possible to reduce the energy used to
pressurize the fluid from
5 Bar to say 10 Bar (10 Bar was already present in the pressure storage
vessel, when the motor was
produced) by approx. 65 %. The total efficiency of a motor type according to
this invention may then
come under 10%, namely 8,75%, by the self-propelling actuator piston, and this
is up to now may be
unprecedented (David IC Mackay, Sustainable Energy - without the hot air -
2009). When the pumps
for regenerating pressure, shown in this invention, again are using the piston-
chamber combination
types according this invention, than another 65% of energy may be saved. Thus
this may result in a
total energy use of 8,75 % x 0,875 = 7,6%, if we would disregard that heat is
being generated by the
pump. However, when a part of the energy used for pumping may come from
another energy source
(than from the total motor power), such as a battery, charged by e.g. solar
energy (photovoltaic)
and/or a fuel cell (e.g. a Hz), from a flywheel or from regerative braking
devices coupled to a
generator, than the total used energy still may end under 10%.
~// 15 ~ it I5- F- IS it
arlier has alre y been concluded that the configuration of a motor type
according to
Fig. ll~,and Fig.13F( may be the most efficient (simple construction, almost
isothermal
thermodynamics), and may additionally be the most reliable (no leaks), and of
which the
configuration of Fig. 13F is without the use of a crank generating rotation,
will the configuration of
l t"t
Fig. 13F be used in a quantitative assessment of a car motor.
We use a current VW Golf Mark B model RF, 1600cc, weight 836kg, with a 53 kW 1
71 pk gasoline motor, comprising 4 cylinders of each o 81mm, and a pressure of
9 Bar, and a stroke
of 77 mm as a benchmark for the invention. This gives a max. force of 1159 N
per cylinder, which
is approx. 116 kg per cylinder. A weigth reduction of approx. 50% may be
assumed, if all the
combustion parts would be taken out of the car body, and aluminium would be
used instead of steel
for said body. Thus necessary may be 58 kg per cylinder to drive an aluminium
body, up to 4
passengers and lugage.
CA 02786315 2012-08-24
The chamber of the pump shown in W020081025391 has a max. working force of
260N (26 kg), over approximately the whole stroke of 400mm from 2 - 10 Bar,
and with a diameter
of a 58mm - e17mm, respectively. Using an inflatable ellipsoide shaped piston
in this chamber, the
actuator is functioning very well in practise. Thus, two of these chambers,
now used as part of an
actuator could be equivalent with one cylinder of the gasoline motor of said
VW Golf Mark II, now
made of aluminium, and all parts related to combustion taken out.
In the motor according to this invention, will the pressure in the enclosed
space of an
actuator piston be changed from x Bar (stroke: 2n 1 ` longitudinal positions)
to approx. 0 bar
(stroke: 1st 2' longitudinal positions). The value of "x may be chosen as
small as possible, in
order to limit the energy use. Because using said special chamber type, the
size of the working force
is independant of the pressure value, it may be possible to limit the pressure
with using a pressure
window to 3,5 Bar at the highest level to approx. 0,5 Bar at the lowest level.
Said starting points may be taken over to the configuration of the pressure In
the sphere shaped piston,
positioned in a rotating chamber of Fig. 13F - however, the chamber may now be
still more simply
shaped as the one shown in Fig. 13F, as 31h Bar uses only a part (216,2nun of
the 400mm) of the stroke
in said specific chamber - the Force per actuator piston is max. 260N.
The change of the volume of said sphere may be quite big: from
Vi= 4/3 x 3,14 x 12,55' (m25.tmm; 1'i=0,35 N/nunz)= 8280 mm' to V,= 4/3 x 3,14
x 23,45' (e
46.9mm; P,=0,05 N/mm') = 54015 mm' - which is a V of 6,5 and a P = 7. The
angle of the
wall relative to the centre axis of said chamber is: L,=302,78 - 86,57=
216,21, r= 10,9: angle=
2,9 - this angle is good.
The energy used for the "virtual" compressing the volume of said actuator
piston at a first
longitudinal position (index 1) to the volume at a second longitudinal
position (index 2) for one
cylinder for one complete stroke L, is:
W;"._ _ -P5V,In(P5/P,)= 0,35 x 54015 x In 7= 0,35 x 54015 x 2,302585 x log 7 =
36788
Nrmn/channel/piston/revolution = 36,8 J/channel/piston/revolution, if there
would only be one
actuator piston per channel. Said motor according to this invention is not as
quick as said gasoline
motor (900 rev/m), regarding the number of strokes/minute - this is due to the
assumed slower
expanding and contracting of the actuator piston, which is made of reinforced
rubber. Let us assume
CA 02786315q"2012-08-24
2A1
the number of revolutions/minute is 60, thus 1 per second (15x slower than
said combustible motor).
The W= 36,8 J/channel/piston/s. There are 2 x 4 `comparable' chambers
(cylinders) - the power is
than 294,3 J/s/piston, which is 0,295 kW/piston. When using 5 pistons, one in
each of the 5 sub-
chambers of each of said 360 channels (Fig. 13F), than may the generated
power be: 5 x 0,295 kW
= 1,47 kW.
Check of the assumption 1 revolution per second: a combustible gasoline motor
amounting 53 kW, of
which it was stated earlier in this study, that it may save 92,4%: 7,6% may
only be used: 4,03 kW.
That may firstly complying to the above mentioned calculation, if the number
of revolutions per
second may approx. be (rounded off): 3 revolutions/sec.
Thus, a motor comprising 2x4 `comparable' chambers, each comprising 5 pistons
in 5 sub-chamber,
rotating at 3 revolutions per second (= 180 rev/min.), resulting in a power of
approx. 3 x 1,47 =
4,4 kW - this may be enough to drive a VW Golf Mark II with an aluminium body.
The literature (David IC Mackay, Sustainable Energy - without the hot air -
p.127, Fig.
20.20/20.21) reveals a small electric car using approx. 4,8 kW power to ran,
and which is coming
from 8x 6V batteries - that car could run 77 km on one batteries' charge, and
charging time is
several hours. If the energy is coming from batteries, which cannot be charged
during the drive of
said car, this may be an option, but not a preferred embodiment.
How much energy is necessary to get the actuator pistons pressurized and
depressurized, and, can
that be done while the car is driving?
It is necessary to get the pressure change in said actuator pistons of said
motor
energized. We use the principle hown in Fig. I IF and Fig. 13F.
The energy may come from the kinetic energy from said rotating chambers, where
e.g.
the piston of a classic pistonchamber combination is being moved by a
camshaft, which is
communicating with a main motor axle of said motor. If we use the data, which
have been used for
calculating the motor power, than the change in pressure of the inflatable
sphere piston may be done
by changing the volume of the enclosed space of said actuator piston, by
changing the volume
`under' the classic piston.
CA 02786315 2012-08-24
The volume change per piston per stroke needed by the actuator piston from a
second to a first
longitudinal position , thus from a small sphere shape (H 25,1 mm) with a
medium internal pressure
(3,5 Bar) to a bigger sphere shape (n 46,9 mm) with a low pressure (0,5 Bar),
with a constant
volume of the enclosed space is done by the internal pressure change of said
actuator piston. The
Force is 260N/stroke/piston, irrespective the internal force, thus with 8
chambers, each comprising 5
pistons, and with 3 revolutions per second, the generated power is: 4,4 kW.
In order to come from the first to the second longitudinal position the energy
needed is (Fig. 14A and
14B):
1. change the sphere shape (a 46,9mm; 0,5 Bar) of the actuator piston to its
production shape (e
25,1 mm; 0 Bar (overpressure)), by deflation of the actuator piston into the
enclosed measuring
space, which is now increasing volume - this may be cost no energy, if the
friction forces
between the pump piston and the wall of the enclose space are small enough,
2. to inflate the sphere (e 25,1 one, 0 Bar) to (0 25,1 mm, 3,5 Bar), by
decreasing the volume of
the enclosed space, where a pump piston is coming nearer the actuator piston -
the energy needed
is:
W:,,a, ,m = -P,V,1n(P,/P,)= -1(check this) x 4/3 x 3,14 x 12,55' x In 4,5*/1 =
-1 x 8280 x
2,302585 x log 4,5 = 12454 Nmm/channel/piston/revolution, and for 2x4
chambers, 5 actuator
pistons per chamber, 3 revolutions per second. = 12,5 x 8 x 5 x 3 Js= 1,5 kW.
(* P, absolute is 4,5 bar, if I', = 1 bar absolute).
Thus: generated brdtto power is 4,4 kW and needed power for getting the motor
run is at least
1,5 kW, thus approx. 2 kW necessary, besides eventual other losses.
In order to access the motor, if a pump complying to the above mentioned
should be present in a car,
we compare it to what is available: a present compressor has the following
specification 220V, 170
I/min, 2,2kW, 8 Bar, pressure storage vessel 100 1. We need the power, but at
a lower pressure, to
that this modifczted compressor is a bit quicker charging the pressure storage
vessel.
22
CA 02786315 2012-08-24
P = 2200 W for 8 Bar, hence for 31,4 bar may be needed using the same
repressuration time as for 8
Bar) only 3/8 x 2200 = 825 W. Even if a battery is a 24V battery, the current
will be 825/24 = 34,4
A - this is very much for a battery, and consequently would many batteries be
available, in the motor
configuration Figs. 11A,B,G and Figs. 12A, 13A, that the pump with reference
numbers 826 / 831
should be electrical. Charging these batteries would only be possible by an
external power source, so
that a car should be ineffective during many hours - the capacitator solution
(Fig. 15E) is still in its
research phase - this would not be a preferred embodiment, but an optional.
It may be better to avoid a conversion of power, and to use the motor
configuration of
Fig. 15C where the pmnp 826 / 831 is communicating with the axle of a
combustible motor, using
e.g. H, which has been generated by preferably electrolyses, and optionally by
a fuel cell. The last
mentioned process is powered by electricity from a battery which is charged by
an alternator, which
is communicating with said axle.
The 825 W needs to be generated by said combustible motor - this may be a 24ec
/ 66cc (VW Golf
Mark II has motor of 53kW, 1600ce, a 9(mm, 4 cylinder 825W is approx. 24ce,
90rnm one
cylinder or if 3x faster: 2,2kW is approx. 66cc, 90nun one cylinder) classic
motor, using the Otto
cycle, which may be compared with a big currently used moped motor. A moped
has been shown on
television for a couple of months ago, using a electrolyses of water, stared
in a tank (originally for
gasoline), and using the generated Hi for the combustion process - this is
feasible. For a car is this
size of external motor indeed an auxiliarly motor - all extra combustible
equipment, which we earlier
had thrown out of the VW Golf Mark H to gain lower weigth, needs to be
replaced by comparable
equipment of a moped motor, which is regrettably necessary - no pollution or
CO5 emission, and the
noise may be successfully reduced by proper noise reducing measurements, and
the weight is only an
assume 1/6 (= approx. 35 kg) of that for a car and a tank of 15 1 water = 15
kgs. - still may this
feasibility study hold.
END 1961Yt amended 19611 added matter to the description- feasibility study th
lq btB
23
CA 02786315 2012-08-24
IS
A further development may be that the inflatable piston is moving in a
specially
20 designed chamber, so that the generated force of the pistom has been
maximized, with a minimum of
expansion (= pressure drop). And, that the interrupted movement, or
`hesitation behaviour' (please see
page xx) of said piston may be compensated by an amended internal shape of
said chamber.
Controlling said motor according to said fast principle according to Fig. IA
is a new aspect as
25 well - for one actuator piston-chamber combination per crankshaft is this
as follows.
It is assumed that the pressure storage vessel may have been pressurized by an
external pressure source
once and for all, thus at the production of the motor. Said actuator piston
may start by means of an
electric starting motor, using the battery, which has been charged by the
solar cells, and/or by a
classic dynamo, which is turned around by the main axle of said motor. Said
starting motor is
CA 02786315 2012-08-24
initially turning the crankshaft, and as a consequence of that movement said
actuator piston is being
pressurized internally - the pressurization of the actuator piston will
thereafter take over the initiative
of the movement of said actuator piston, and consequently the initiation of
the turning of said
cipnkshaft. Said starting motor may then be decoupled from said crankshaft-
It may also be possible that the motor is starting by means of opening up the
pressure storage vessel
814, so that fluid 822 is pressurizing said actuator piston internally, which
is initiating the movement of
said piston - please see Fug-
1B-Speeding up said motor, that is to say, speeding up the rotation of said
crankshaft may be done
by raising the pressure inside said actuator piston, by means of opening up a
so-called reduction valve
between said pressure vessel and said actuator piston in the (lead) line
(829]. Slowing down the rotation
of said crankshaft may be done by reducing the pressure inside said actuator
piston, by closing down the
opening of said reduction valve.
to order to give the motor more power (torque on the main axle) nay be done,
by increasing
pressure for an existing configuration of actuator piston-chamber combination,
Or there may be more
than one actuator piston-chamber combination per axle. Stopping the motor may
be done by totally
closing said eduction valve in said (lead) line [829]- Said reduction valve
may he eomrnuncadng widr a
speeder.
The pressure management in more derail of said actuator piston may be
organized as follows.
Both in the wall of the crank of the crankshaft and at the cod of the piston
rod may be holes, which
communicate with a second and third enclosed space, and the enclosed space,
respectively. At a certain
point of time may these holes communicating with each other, so that the
enclosed space of the actuator
piston may be communicating with the second br the [bird enclosed space within
the crankshaft - while
_ communicating with the second enclosed space, the piston may then be
pressurized thnmgh its enclosed
space and may be moving from a second to a first longitudinal position in the
chamber. While
cormnunicating with the third enclosed space, deflation of the piston may
occur when the piston may be
moving from a first to a second longitudinal position. The main piston pump
(818) initiates the decrease
of pressure in the third enclosed space in the crankshaft and the decrease of
the pressure in the enclosed
CA 02786315 2012-08-24
space in the piston rod, due to the interrelated default positions of the
crankshaft of the pump, and of the
crankshaft of the actuator piston, respectively, which may be assembled on the
same axle
More in detail may the pressure management of said actuator piston working as
follows-
At the final second longitudinal position of the piston may the hole
More than one actuator piston-chamber combination in said motor may be present
on the
some axle. This concept however may not be helpfitl] complying to said
specifications. As it is with
current combustion motors, more than one piston-chamber combination per axle
may make the motor
running more smoothly. And, of course, the torque will be increased on said
axle.
.q I.
is
The crankshaft itself may be an inefficient way to generate rotational motion,
and moreover,
the stroke length of ibis type of piston-chamber combination may be larger
than that of e.g. a current
combustion motor - that is to say, that the r(otation)p(er)m(inute)'s of said
crankshaft may be
substantially lower than that of a current combustion motor. A gear may be
necessary, and the gearing
ratios may be different from that of current combustion motors. The gearbox
may reduce the efficiency
with say 25%, and said efficiency may be improved (by say 50%) by using low
friction bearings such as
Fluid Dynamic Bearings. As the motor may run the whole time, a clutch may be
needed. Thus the
% of energy needed fora car motor should come from e.g. green energy, e.g.
solar energy from
e.g. solar cells on the roof ! hood of the car / the paint of the whole body,
and that may be too much. Of
course could there be added some special batteries, if these arc being charged
with energy from wind
power or solar energy - this adds to the dead weight of a vehicle and
increases the WTR ratio - the last
mentioned would partially need a distribution stmcmre.Thus, this motor type
may not fully complying to
said specifications, when one would aim e.g. a 'green' car motor.
CA 02786315 2012-08-24
Thus in order to eofrtplyine to specifications a ennkshah mxyheavoidecl, ac
wrll ac a ge r
ROTATING POWER SOURCE FOR A 'GREEN' MOTOR based on the principle of Fig. 2A
This bring us to the point where said piston may be rotate instead of
translate - this new type of motor
may be a kind of a `green' Wankel Motor
A)
A still better use of energy may be obtained by a motor without a crankshaft,
using the same
principle as above mentioned, at least for the propulsion system. Besides the
foregoing mentioted, may
this decreased use of energy specifically be obtained in a chamber around a
circteround -rue line,
which may be concentrically pastioned around the main axle of said motor, by
reducing the distance
from a i" otnn-l position to a 2 ' rotational position of a piston in said
chamber to approximately the
eadius of said piston, so that she momr ahnost continuously may be powe ing
said mole.
At
A conical chamber, wherein a piston may function as a self-propelled actuator,
may be beaded
circularly in the longitudinal direction, and may be tilling 360' or a part of
it. There may be at least one
piston functioning in said chamber. The motor may comprising one of more
actuator piston-chamber
combinations, which may be using the same axel. In the center of the circular
motion of said actuator
piston and/or said chamber may be an axle, which may be connected to the
construction elements which
makes a car or another vehicle run, such as wheels e.g. a propeller.
There may be two ways to construct such a motor. One is, to have the centre
axis of the'
actuator piston rod moving in the plane where the centreaxis of said chamber
lies. Another possibility
may be that the centre axis of the actuator piston rod may be positioned
perpendicular the plane where
the centre axis of the chamber lies. In both cases may said actuator piston
moving or the chamber, or
both.
CA 02786315 2012-08-24
Running an actuator piston like the one which was used in the elongated
conical chamber - an
ellipsoide to sphere and vice versa formed piston (e.g. W02000/070227 - Figs.
9A,B,C) in a circularly
bend-chamber seems unlikely, as the chamber may be circularly bend in its
longitudinal direction, so that the bearings of the piston rod of said
actuator piston are missing.
Instead, a (smaller) sphere to (bigger) sphere and vice versa type actuator
piston may be used (e.g.
W02002/077457 Figs. 6A-B, 9A-C), which due to its symmetrical term enables a
less complex
constexction for the bearings of the piston rod. E.g. the piston rod may he
positioned through said
actuator piston perpendicular to the plane where the centre axis of said
circularly formed chamber lies.
Said actuator piston may be moving in said chamber, because of the fact that
said chamber is
identically shaped as the straight chamber which was used when using a
transitionally moving piston,
but now, circularly.
S-lowever, the size of the part of the wall of said piston which lies behind
the transitional centre
axis of said piston perpendicular the centre axis of said chamber, and a
direct line from the centre of the
piston to the place where chamber and piston engaging (or sealing or both), is
substantially smaller than
that of the ellipsoide sphere piston which is translating on the centre axis
of an elongate chamber.
That is why the assumed power which each actuator piston (sphere - spher) has,
may he lose than of a
ellipsoids sphere actuator piston. This calls for a motor, where more tlian
one actuator piston per
chamber is being used, Additional issue call for the some, because the
actuator piston is moving
intermptedly (please see later), and more Than one piston in the same 360
chamber, may create a
smooth motion. And, when said actuator piston(s) having expanded to its
maximum, a very short
moment occurs, that the pressure within said actuator piston is decreasing,
and this may also give a
'moment of hesitation' in the motion - in order that one actuator piston is
overcoming 'hesitotions' in the
motion of another acmator piston, said actuator pistons may be positionedon
different positions on the
centre .is of said chamber. As an example, if the 360 chamber has been
updividest in 4 identical
subchambers, the number of actuator pistons may he five, equally divided over
the 360'.
The major advantage of such a rotational motor may be, that the length of the
return stroke of
an actuator piston from a I" circular position to a 2nd circular position has
been substantially reduced in
comparison with the crankshaft option and may be at least the size of the
biggest radius of the piston at a
9
CA 02786315 2012-08-24
Out circular position, because the circular 1" position and the circular 20
position are in direct
--eonfimuatims.oCeacl>-o[Ler~n_the direction of rotation.
Thus the drop of pressure inside said actuator piston and the raise of
pressure immediately
thereafter may need to be managed.
There may be two fundamental ways to do change the inside pressure of the
actuator pistons. One option
is that each of the actuator pistons may be connected by a channel to a valve
which may be able to
increase I decrease the pressure in said actuator pistons. Said valves may be
computer steered, so that
The pressure inside each actuator piston is optimal to its position in said
chamber. Additionally may be
aceempliced that said computer is steering the pressure from a pressure
vessel, which is serving as a
0 pressure source, so that the distribution of the available pressure in each
of the actuator pistons may
optimize the use of the available fluid pressure for said actuator pistons. A
second option is e.g. by a
very short change in the volume of the enclosed space. This change may be done
by a movable piston
which is sealingly connected to the wall of e.g. an elongated chamber. Said
chamber may arty well be
of the kind having differing cross-sectional in the transitional direction.
Because of the speed of the
75 movement may this chamber be of a kind having a constant cireumphernnce, on
that the piston only is
bending during operation. But of course, chambers having differing sizes of
the transitional
circumpherenee may also be an Option. A piston moving within said chamber may
have a piston rod,
which may be communicating with a camdisk, which may be connected to the axle
on which the motor
is mounted- At the end of a piston rod may he a wheel, whicb is rotting over
said ranrdisk. Thus, as
20 such is this motor type not consuming fluid, only the contained energy
(pressure) of said fluid.
The 360 chamber may turn around an axle, of which centre axis may be crossing
the centre of
said chamber. Said chamber may be. part of a wheel, and the outetpart of said
wheel may have a notch,
in which a drive hell, which may be driving auxilliarly devices, such as a
electric generator.
Clearly is the type of motor where the chamber is rotating and the piston(s)
non-moving the less
complex solution of the two options of rotatable motors. Also is the generated
torque better, e.g. 5x in
said solution, because there are 5x more pistons per chamber of the same
dimensions.
- 10
CA 02786315 2012-08-24
The most reliable system may be a fixed piston in a rotating chamber. An
advantage may be, that the
-motor may be comgrising uoo o tftan_oneTi_nn~.e.g-5-pistens,-whit..-~: -be-
penhiened-ae-
different rotational positions, which may make the motor turning smoothly,
because the transition of a
piston from its 1" rotational position to its V rotational position may be
powered by e.g. 4 other pistons-
And the "hesitation behaviour" (please see toter) of a piston while moving
from a 2 to a 1' rotational
position may be also supported by e.g. the 4 other pistons, so that no
"hesitations" may being observed-
A gearbox may be unnessary, as the pressure rate of the Said inside the piston
will define the speed of
the main axle - this necessary pressure window may easily be obtained by the
construction of this
motor, while this pressure may easily be defined by a speeder Thus a gearbox
may be superfluously
and that adds to a further weight reduction of approx. 50 kg. The VW Golf Mark
11 conversion has now
been erchtimtally reduced to approx. 350 kg. The TWR is now approx. 5,6.
Controlling the rotational motor may be time in a similar way as the
controlling of the motor with
75 translating pistons (or even with translating chambers and non-moving
pistons, or even.when both are
moving - not shown).
Controlling means: putting iota function, starting up, speeding up, slowing
down, powering up,
stopping, and taking th-motor out of non.
Potting the motor into function may be done by en electrical on/off switch,
which is switching on the
electrical system, and another switch which is connecting the starter motor to
the electricity circuit, so
that it is connecting to the axle, and Nrning.
On the same axle as the moving piston or moving chamber is using, may there be
a starter motor, which
is using electricty from a starter battery, which itself is loaded by
electricity from a solar energy. The
starter motor may be corning said axle, and so initiate the rotation.
The pressure management may be done as follows.
A
Il
CA 02786315 2012-08-24
k- 1'u
In the motor where the piston is moving, needs this piston to be pressurizer],
and so that pressure is
changing at the transition point where the biggest circumpherence is changing
to the smallest. This may
be done electronically by means of a computer and injection jet. As the
pressurized fluid needs to be
sustained, said solution needs a new solution.
Otherwise, would it be possible to create a mechanical solution, as the change
of pressure is of a certain
frequenze: e.g. a camshaft, which is communicating with the drive shaft
through a time belt. The
camshaft may be pressing a flexible membrane which is communicating with said
fluid, of which the
pressure needs to be managed.
In order to make this solution less complex, may the chamber comprising one
instead of e.g. 4 sub-
chambers, so that the pressure needs to change only once.
is AA
in the motor where the chamber is moving, needs the e.g. 5 pistons to be
pressurized, and so that
pressure is changing at the transition point where the biggest circumpherence
is changing to the smallest.
This may be done electronically by means of a computer and injection jet. As
the pressurized fluid needs
to be sustained, said solution needs a new solution.
In the motor where the chamber is moving, need the inside pressure of e.g. 5
pistons be managed
differently from each other, but in the same order, and that pattern repeats
itself for every turn, so that
also here a camshaft solution may be possible: a camshaft which is
communicating with the drive shaft
through a time belt. The camdisk may be pressing a flexible membrane which is
communicating with
said fluid, of which the pressure needs to be managed per piston.
CA 02786315 2012-08-24
~~31
TRANSLATIONAL POWER SOURCE for a motor based on the principle of Fig-11F
B
A still more reliable system may be obtained by a new principle according to
Pigs- iF and fPP for Elie
i pressure management, namely by separating the fluid in the piston and the
enclosed space, from the
fluid in the repressurization stages - the change of pressure in the piston
may he ohtnin at by a change of
vnleme of the enclosed space of the piston. The impruved reliability may
relate n reducing the number
of transitions of pressurized fluid, which may leak. ]n this principle may
mainly the comroling devices
be using creepy for changing the volume of the enclosed space. This may very
well he done to that also
0 here energy is being reduced, by using again a piston (e.g. one for the
[unction of said piston, and
preferably one for the speecllpower - optionally a separate pisum for the
power management) which is
moving sealingly in a cylinder. said cylinder having contineonsty differing
transitional cross-sectional
area's and e.g. changing circnmlerences so that again a 65% reduction of the
energy used may be
obtained. Also for this priciple may the embodiment with a fixed piston in a
rotational chamber he the
beer option for reducing the use of energy. Constant circumferences may also
work, but the gained
reduction may be lower.
B
The change (and consumption) of pressure of a Said within an inflatable piston
may also he
20 done in an alternative way, alternative to the principle shown in Fig.(]A.
By temporary changing the
volume of the enclosed space of said piston, while an adjustment of said
volume may give a change in
the power (terq) of said motor, and this may be done serially of
simultaneously. The energy is coming
from .
2S This is still a more efficient way to use the available energy, and it may
increase the reliability
of said motor in relation to the priciple of that shown in Fig. CIA. There
will in this new principle be no
leakes between high pressure fluid when the piston is moving from 2"' to 1
longitudinal positions, and
low pressure fluid when the piston is moving vice versa in the joints, such as
crankshaft - big end
hearing, and the two parts of the connecting rod.
13
CA 02786315 2012-08-24
3Z
The energy used may be used to move a piston in a conical chamber which may be
optimized
no ieducing the woikng force on the piston rod pf sa_d , stoat, for chanting
the solnme-ofthe. enclosed-_-
space. Additionally'is the energy used may be used in a similar piston-chamber
combination as the one
used for said voNmih changing, for adjusting the volume of the enclosed space.
-
The move4pem of the volume changing piston may be done by using pressurized
liquid which is
moving a piston in In chamber from one point to another an vice versa by means
of ,-g- valves or other
kind of control dean pea, or by magnetic guidance. This is also valid for the
piston which is adjusting the
volume of the en fused space - the control of the movement of said- piston may
be done by
communicating wit a speeder, which is controlled by e.g. a person or a
computer.
t0
i
ROTATING POVT.R SOURCE FOR A MO'T'OR based on the priciple of Fig.13E
The char le (and consumption) of pressure of a fluid within an inflatable
piston may also be
is done in an ve way, alternative to the principle shown in Fig. 2A. By
temporary changing the
volume of the encl sed space of said piston, while an adjustment of said
volume may give a change in
the power (tort) of said motor, and this may be done serially or
simunaneousiy.
This prin
cipte is in rotating Owen sources still more efficient than for transitional
power source systems, because
the distance from I' to 2'"' rotational positions is almost oil - therefore
may the piston which is changing
the volume of the ,close space be guided by a cam disk, which may be mourned
on the axle, around
which- the motor p w r source is meting.
In fact this is the i sl efficient motor. /f- Sam/
m6hr1 Wt a enew~nn 4~ esa ~n'se a Wave wk e¾oh(
G/2rnl1w t WA=6L tT e -iA 1-U Vl-L
CA 02786315 2012-08-24
---F~--GAF-F~s ~t~ ,r~7-n. i t C~c/~J-~ . _ %7~ ~~ ~ ~ !a < a.~ -
;hn d ,~/~,.~ """7'~ t/I ~z mac. ;+/~ z r-.~`%~c ,~.J}n.- w/uz~
Ce Tw 7 ' ? w tt ~, f oc~ t s5-s fa av
S--,A S--,h'--
e--,4 d~ a Lsh e ioz a oGn~.x ru
j CL cJ`u~ G ~==.~. brtac~,,c~ r~Cri~;z~ b'1 lw Yhf 77~ e.~Cr~ r/J d~~,~IJ~(
-.rC<c/~~C G-rV~ -Scc,'-.`m,l~c Sc<~-`SCI -lz.~I.ts Q~.c o4c'~zGirs.' X
Ja.~ a~ ik('2 /n ih2w~ 67r*-P.fulr~c.~~ ZZc -'ac
lh. OS'Z~c hin, 6G..v, ~,inl6 fCL-~,-f~_~ ~~t prm''7vv~)
d"ll
~1"c. (~.C~rnn C{~r.~(.~,~-mot ~ J-e.,Y( C mm. d-tvt-mss
r't rx, Q >/~ ~J(~3`zh n ?a5. ~11f].c.~ i7 cC ~c,~,z _.'G.~G~I C/c>.~-g~2
~'l e'-~ ~7 ~ ¾ ~~ Cep O .~, s 'u ocoa shy --as
C~ys-S fisk~C bz uL ,7 ~a~~ZcC / ~afu 4",3
CA 02786315 2012-08-24
The various embodiments described above are provided by way of illustration
only and should not be
consorted to limit the invention. Those skilled in the art will readily
recogtado various modificatiom
changes, and combinations of elements which may be made to the present
invention without strictly
following the exemplary embodiments and applications illustrated and described
herein, and without
- departing from the true spirit and'scope of the present invention.
All piston types, specifically those which are containers with an elastically
deformable wall
may be sealingly connected to the chamber wall during its move between
longitudinal positions
engagingly connected or not connected to the wall of the chamber. Or may be
engagingly and sealingly
connected to the chamber wall. Additionally may there be no engaging between
said walls either,
possibly touching the walls each other, and this may happen e.g. in the
situation where the container is
moving from a first to a second longitudinal position in a chamber.
'the type.of connection (sealingly and/or engagingly and/or touching and/or no
connection) between said
walls may be accomplished by using the correct inside pressure inside said
container wall: high pressure
for sealingly connection, a lower pressure for engagingly connection and e.g.
atmospheric pressure for
no connection (production sized container) - thus, a container with an
enclosed space may be preferred,
because the enclosed space may be controlling the pressure inside the
container from a position outside
the piston.
Another option for an engagingly connection is than wall of the container,
which may have
reinforcements which are sticking out of the surface of said wall, so that
leaking may happen between
the wall of container and the wall of the chamber
19 09 B DESCRI IO OF THE D GS
In be fo owing referre embod- nts of the vention 11 be esctibed erenc to the
dra wing wherein:
CA 02786315 2012-08-24
CA 02786315 2012-08-24
X36
In the case of an actuator piston, which is connected to the main axle by a
crankshaft, and there are more than one actuator pistons present, all
connected to the same main
axle, the advantage may be that the turning of said main axle may be more
smoothly, if the
longitudinal position of said actuator pistons is different from each other,
to so that the "hesitation
moment" for each of tsaid actuator pistons, when moving from a second to a
first longitudinal
position, may occur on other points of time.
It may be necessary that all of said actuator pistons are engagingly or
sealingly (this
may be different from a longitudinal position to another longitidinal position
when moving in said
chamber) moving from a second to a first longitudinal position in a chamber
and vice versa,
which has the characteristics that the force on the piston rod - thus the
connection rod from the
actuator piston to the crankshaft - may be independent of the position which
the actuator piston
has (please see the description and drawings with reference 19620"), in order
to synchronize the
force of each of said actuator pistons to said main axle.
20
30
CA 02786315 2012-08-24 The feasibilty study until now did not incorporate
quantitatively the lack of heat
generated by a motor of this invention, in comparison with Otto Motor types.
When we incorporate heat loss, than the motors of this invention are still
more
interesting and convincing. Heat losses give a current Otto Motor an
efficiency of 25 %. When we
assume in the first instance that said motors of this invention do not
generate beat at all, than it is
possible to reduce the energy used to pressurize the fluid from 5 Bar to say
10 Bar (10 Bar was
already present in the pressure storage vessel, when the motor was produced)
by approx. 65 %
reduction. The total efficiency of a motor according to this invention will
then become under
%, namely 8,75 %, by the self propelling actuator piston, and this is up to
now unprecedented
David 7C Mackay, Sustainable Energy - without the hot air). When the pumps for
regenerating-
pressure, shown in this invention, again are using the piston-chamber
combination types
according this invention, than another 65% of energy is saved- 'thus this
would give a total
energy use of 8,75% x 0,875 = 7,6%, if we would disregard that heat is being
generated by the
pump. However, when a part of the energy used for pumping may come from
another source,
such as solar energy (photovoltaic), from a flywheel or from regerative
braking devices, than the
total used energy still may end under 10%.
CA 02786315 2012-08-24
1961k amended 19611 added matter to the description - feasibility study
The feasibilty study until now did not incorporate quantitatively the lack of
heat
generated by a motor of this invention, in comparison with Otto Motor types.
When heat loss may be incorporated, than the motor types of this invention are
still
more interesting and convincing. Heat losses may give a current Otto Motor an
efficiency of 25%.
When it may be assumed in the first instance that said motor types of this
invention do not generate
heat at all (isothermal), than it may be possible to reduce the energy used to
pressurize the fluid
from 5 Bar to say 10 Bar (10 Bar was already present in the pressure storage
vessel, when the motor
was produced) by approx. 65%. The total efficiency of a motor type according
to this invention may
then come under 10%, namely 8,75%, by the self-propelling actuator piston, and
this is up to now
may be unprecedented (David JC Mackay, Sustainable Energy - without the hot
air - 2009). When
the pumps for regenerating pressure, shown in this invention, again are using
the piston-chaniber
combination types according this invention, than another 65% of energy may be
saved. Thus this
may result in a total energy use of 8,75% x 0,875 - 7,6%, if we would
disregard that heat is being
generated by the pump. Ilowever, when a part of the energy used for pimping
may come from
another energy source (than from the total motor power), such as a battery,
charged by e.g. solar
energy (photovoltaic) and/or a fuel cell (e.g. a H2), from a flywheel or from
regerative braking
devices coupled to a generator, than the total used energy still may end under
10%.
Earlier has already been concluded that the configuration of a motor type
according to
Fig. 1IF and Fig.13F may be the most efficient (simple construction, almost
isothermal
thermodynamics), and may additionally be the most reliable (no leaks), and of
which the
configuration of Fig. 13F is without the use of a crank generating rotation,
will the configuration of
Fig. 13F be used in a quantitative assessment of a car motor.
We use a current VW Golf Mark II model RF, 1600ce, weight 836kg, with a 53 kW
/
71 pk gasoline motor, comprising 4 cylinders of each e 81mm, and a pressure of
9 Bar, and a stroke
of 77 mm as a benchmark for the invention. This gives a max. force of 1159 N
per cylinder, which
is approx. 116 kg per cylinder. A weigth reduction of approx. 50% may be
assumed, if all the
combustion parts would be taken out of the cur body, and aluminium would be
used instead of steel
for said body. Thus necessary may be 58 kg per cylinder to drive an aluminium
body, up to 4
passengers and lugage.
CA 02786315 2012-08-24
The chamber of the pump shown in W020081025391 has a max. working force of
260N (26 kg), over approximately the whole stroke of 400mm from 2 - 10 Bar,
and with a diameter
of o 58mm - e17mm, respectively. Using an inflatable ellipsoide shaped piston
in this chamber, the
actuator is functioning very well in practise. Thus, two of these chambers,
now used as part of an
actuator could be equivalent with one cylinder of the gasoline motor of said
VW Golf Mark IT, now
made of aluminium, and all parts related to combustion taken out.
In the motor according to this invention, will the pressure in the enclosed
space of an
actuator piston be changed from x Bar (stroke: 2 d -, 1" longitudinal
positions) to approx. 0 bar
(stroke: 1st -u 2"d longitudinal positions). The value of "x" may be chosen as
small as possible, in
order to limit the energy use. Because using said special chamber type, the
size of the working force
is independant of the pressure value, it may be possible to limit the pressure
with using a pressure
window to 3,5 Bar at the highest level to approx. 0,5 Bar at the lowest level.
Said starting points may be taken over to the configuration of the pressure in
the
sphere shaped piston, positioned in a rotating chamber of Fig. 13F - however,
the chamber may
now be still more simply shaped as the one shown in Fig. 13F, as 3Y Bar uses
only a part
(216,2mm of the 400mm) of the stroke in said specific chamber - the Force per
actuator piston is
max. 260N.
'the change of the volume of said sphere may be quite big: from
Va= 4/3 x 3,14 x 12,553 (o25.l=; P2=0,35 N/mm )= 8280 mm3 to V1= 4/3 x 3,14 x
23,453 (o
46.9nun; P3=0,05 N/mmc) = 54015 mm3 - which is a AV of 6,5 and a AP = 7. The
angle of the wall
relative to the centre axis of said chamber is: Lt=302,78 - 86,57= 216,21, sIr-
10,9: angle= 2,9 -
this angle is good.
The energy used for the "virtual" compressing the volume of said actuator
piston at a fast
longitudinal position (index 1) to the volume at a second longitudinal
position (index 2) for one
cylinder for one complete stroke Lr is:
Wi,u ml = -P3V1In(P2/Pt)= 0,35 x 54015 x In 7= 0.35 x 54015 x 2,302585 x log 7
= 36788
Nnun/channel/piston/revolution = 36,8 J/channel/piston/revolution, if there
would only be one
actuator piston per channel. Said motor according to this invention is not as
quick as said gasoline
motor (900 rev/m), regarding the number of strokes/minute - this is due to the
assumed slower
expanding and contracting of the actuator piston, which is made of reinforced
rubber. Let as assume
the number of revolutions/minute is 60, thus I per second (15x slower than
said combustible
motor). The W= 36,8 J/channellpiston/s. There are 2 x 4 `comparable' chambers
(cylinders) - the
ko
CA 02786315 2012-08-24
power is than 294,3 J/s/piston, which is 0,295 kW/piston. When using 5
pistons, one in each of the
sub-chambers of each of said 360 channels (Fig. 13F), than may the generated
power be: 5 x
0,295 kW = 1,47 kW.
Check of the assumption 1 revolution per second: a combustible gasoline motor
amounting 53 kW,
5 of which it was stated earlier in this study, that it may save 92,4%: 7,6%
may only be used: 4,03
kW. That may firstly complying to the above mentioned calculation, if the
number of revolutions
per second may approx, be (rounded off): 3 revolutions/sec.
Thus, a motor comprising 2x4 `comparable' chambers, each comprising 5 pistons
in 5 sub-chamber,
rotating at 3 revolutions per second (= 180 rev/min.), resulting in a power of
approx. 3 x 1,47 - 4,4
kW - this may be enough to drive a VW Golf Mark 11 with an aluminium body.
The literature (David JC Mackay, Sustainable Energy - without the hot air -
p.127, Fig.
20.20/20.21) reveals a small electric car using approx. 4,8 kW power to run,
and which is coming
from 8x 6V batteries - that car could run 77 km on one batteries' charge, and
charging time is
several hours. If the energy is coming from batteries, which cannot be charged
during the drive of
said car, this may be an option, but not a preferred embodiment.
How much energy is necessary to get the actuator pistons pressurized and
depressurized, and, can
that be done while the car is driving?
It is necessary to get the pressure change in said actuator pistons of said
motor
energized. We use the principle hown in Fig. I IF and Fig. 13F.
The energy may come from the kinetic energy from said rotating chambers, where
e.g.
the piston of a classic piston-chamber combination is being moved by a
camshaft, which is
communicating with a main motor axle of said motor. If we use the data, which
have been used for
calculating the motor power, than the change in pressure of the inflatable
sphere piston may be done
by changing the volume of the enclosed space of said actuator piston, by
changing the volume
`under' the classic piston.
The volume change per piston per stroke needed by the actuator piston from a
second to a first
longitudinal position, thus from a small sphere shape (o 25,1 nun) with a
medium internal pressure
(3,5 Bar) to a bigger sphere shape (e 46,9 mm) with a low pressure (0.5 Bar),
with a constant
volume of the enclosed space is done by the internal pressure change of said
actuator piston. The
1-I
CA 02786315 2012-08-24
Force is 260N/stroke/piston, irrespective the internal force, thus with 8
chambers, each comprising
pistons, and with 3 revolutions per second, the generated power is: 4,4 kW.
In order to come from the first to the second longitudinal position the energy
needed is (Fig. 14A
5 and 14B):
1. change the sphere shape (e 46,9mm; 0,5 Bar) of the actuator piston to its
production shape (o
25,1 mm; 0 Bar (overpressure)), by deflation of the actuator piston into the
enclosed measuring
space, which is now increasing volume - this may be cost no energy, if the
friction forces
between the pump piston and the wall of the enclose space are small enough,
2. to inflate the sphere (o 25,1 mm, 0 Bar) to to 25,1 mm, 3,5 Bar), by
decreasing the volume of
the enclosed space, where a pump piston is coming nearer the actuator piston -
the energy
needed is:
W;,oac,,,,a _ -P,Vrln(P7/P,)- -1(cheek this) x 4/3 x 3,14 x 12,553 x In 4,5*/l
= -t x 8280 x
2,302585 x log 4,5 - 12454 Nmm/channel/piston/revolution, and for 2x4
chambers, 5 actuator
pistons per chamber, 3 revolutions per second. = 12,5 x 8 x 5 x 3 Js= 1,5 kW.
(* Pz absolute is 4,5 but, if P, = 1 bar absolute)-
Thus: generated brutto power is 4,4 kW and needed power for getting the motor
run is at least
1,5 kW, thus approx. 2 kW necessary, besides eventual other losses.
In order to access the motor, if a pump complying to the above mentioned
should be present in a
car, we compare it to what is available: a present compressor has the
following specification 220V,
170 1/min, 2,2kW, 8 Bar, pressure storage vessel 100 1. We need the power, but
at a lower pressure,
so that this modifeated compressor is a bit quicker charging the pressure
storage vessel.
P = 2200 W for 8 Bar, hence for 3 `/, but may be needed using the same
repressuration time as for 8
Bar) only 3/8 x 2200 = 825 W. Even if a battery is a 24V battery, the current
will be 825/24 - 34,4
A - this is very much for a battery, and consequently would many batteries be
available, in the
motor configuration Figs. 11A,B,G and Figs. 12A, 13A, that the pump with
reference numbers 826
/ 831 should be electrical. Charging these batteries would only be possible by
an external power
source, so that a car should be ineffective during many hours - the
capacitator solution (Fig. 15E) is
still in its research phase - this would not be a preferred embodiment, but an
optional.
q2
CA 02786315 2012-08-24
It may be better to avoid a conversion of power, and to use the motor
configuration of
Fig. 15C where the pump 826 / 831 is communicating with the axle of a
combustible motor, using
e.g. H2, which has been generated by preferably electrolyses, and optionally
by a fuel cell. The last
mentioned process is powered by electricity from a battery which is charged by
an alternator, which
is communicating with said axle.
The 825 W needs to be generated by said combustible motor - this may be a 24ce
/ 66cc (VW Golf
Mark It has motor of 53kW, 1600cc, e 90mm, 4 cylinder -r 825W is approx. 24ce,
90mm one
cylinder or if 3x faster: 2,2kW is approx. 66cc, 90mm one cylinder) classic
motor, using the Otto
cycle, which may be compared with a big currently used moped motor. A moped
has been shown
on television for a couple of months ago, using a electrolyses of water,
stored in a tank (originally
for gasoline), and using the generated H2 for the combustion process - this is
feasible. For a car is
this size of external motor indeed an auxiliarly motor - all extra combustible
equipment, which we
earlier had thrown out of the VW Golf Mark II to gain lower weigth, needs to
be replaced by
comparable equipment of a moped motor, which is regrettably necessary - no
pollution or CO2
emission, and the noise may be successfully reduced by proper noise reducing
measurements, and
the weight is only an assume 1/6 (= approx. 35 kg) of that for a car and a
tank of 15 1 water = 15
kgs. - still may this feasibility study hold.
CA 02786315 2012-08-24
The motor based on a crankshaft solution (Figs. 11A-D and 11F) with an
elongate
chamber and a piston which is connected to said crankshaft by a piston rod/
connection rod, may
preferably be used as a main motor of a transport vehicle, e.g_ a car. Said
wheels or propellors
may be connected to the central main motor by drive shafts and a distibution
device such as a
cardan_. Optionally may said motor type be used as a decentrally positioned
motor, which may be
directly connected to each of the propulsion devices, such as wheels or
propellors.
The motor based on a chamber which is positioned around a circleround centre
axis
and a piston which is increasing and decreasing its size (Figs. 12A-C, 13A-G),
may preferably be
used as a decentrally positioned motor in a transport vehicle, e.g. a car.
Each of said motors may
be directly connected to each of the propulsion devices. Optionally as a
central motor, which may
be connected to said propulsion devices by driveshafls.
The control of said motors may preferably be done by a computer, specifically
when
each motor is directly connected to one of more than one propulsion devices
which a transport
vehicle is using.
A flywheel which may preferably be connected to a main central motor, and
optionally decentrally positioned to each of the propulsion devise. A flywheel
may be used for
keeping the motion smoothly - the classic solution - or to regaining energy
for acceleration, after
braking (and simultaneously storing the kinetic braking energy) of a transport
vehicle - or to give
energy to one of the pumps (e.g. references 818, 821,821', 826, 826' in Figs.
11A,B,C, F,
12A,C, 13 A,B,E,F) which are communicating with a pressure storage vessel
(e.g. references
814, 839, 890, 889). All or a few of said types of flywheels may be present in
a transport vehicle,
which is comprising a motor according to this invention.
Another aspect of the regaining energy while braking may be pumps which are
directly connected to a main axe], which maybe a central driveshaft (e.g.
references 821, 821').
which may pump the fluid to a much higher pressure and communicate the
resulting high pressure
fluid to a pressure storage vessel (e.g. references 814, 839, 890, 889)-
CA 02786315 2012-08-24
1961 optimal configuration of chambers for actuators (h I q Is 18
The geometry of chambers to be optimally used in co-operation with an actuator
piston may be different from those, which are aiming an optimal use of a pump,
because the
conditions for the use in said actuator and said pump may be different
For example the actuator piston needs to give a maximum force, by using as
less energy as
possible, while moving at an appropriate speed. And, for an actuator piston
which is
communicating with a crank, the sub-conditions may be different from the sub-
conditions of e.g.
an actuator piston which is communicating with a rotating chamber: e.g. the
point of time where
the maximum force is'being needed.
In order to use the actuator piston as a self-propelled piston, it is
necessary that an
elongate chamber is of a type where the wall of said chamber is widening
outwards when moving
from a second to a first longitudinal position. Thus, the angle of the wall in
relation to the centre
axis of said chamber, 'from a second to a first longitudinal position needs to
be positive. This
angle may be fixing the speed of the actuator piston. And of course need the
transitions from one
point of the wall to another in the longitudinal direction be smooth, so as to
limit friction between
said actuator piston and said wall of the chamber.
The inflatable actuator piston itself needs to have an internal pressure in
order to be able to load
the wall of the chamber. In order for said actuator piston to be able to move
needs the centre of
the flexible wall be closer to a fast longitudinal position than the
circumference which is
engagingly connected to the wall of the elongate chamber. The larger this
distance is, the higher
the speed of said actuator piston in said chamber.
The reaction farce of the wall of the chamber on said actuator piston is
fixing the force which
with the piston is pushing itself off the wall of the chamber in the direction
of a first longitudinal
position. Thus also the force on the piston rod, if at least one cap of the
actuator piston, best
nearest a second longitudinal position, is assembled on said piston rod.
In section 19620 of this patent application is a chamber shown (e.g. Fig.21A),
which, when used in a pump, reduces the working force on the piston rod with
approx. 65 % at 8-
10 Bar of the pumped fluid - this is excellent for pumping purposes. This
reduction should be
seen in comparison with the force needed in a straight cylinder, and comes
from a comparison of
CA 02786315 2012-08-24
a classic high pressure bicycle pump, and an advanced bicycle pump where the
chamber has the
shape of Fig. 21A. In said chamber is the maximum force approximately
independant of the
pressure of the fluid in said chamber, thus approximately constant (e.g. from
2 Bar, when the
maximum force has been reached) during a pumping stroke-
An identical chamber used in an actuator, comprising an actuator piston, may
have the advantage
that the force is approximately constant during the stroke from a second to a
first longitudinal
position - the price to be paid may than be that the working force may only be
approximately 113
in relation to the working force when the maximum pressure has been reached in
a straight
cylinder having a certain diameter (same comparison source as mentioned
above). The size of the
force may not be appropriate for the purpose of an actuator piston, while
additionally the force,
being constant, may not be appropriate either in relation to the use with a
crank.
The same may be valid if the chamber is circleround (`circular') instead of
elongate.
In the particular solution where an actuator piston is non-moving, and
positioned in a rotational
moving chamber may such a chamber type as mentioned above be used. If more
than one piston
is used, e.g. 5 pistons (e.g. Fig.10B), than such a chamber may be necessary,
when each piston is
at a different circular position in each sub-chamber, thus different pressure,
the force derived by
each piston may be the same for all pistons, so that none of said pistons is
pushing others - the
total force is 5x that of when only one piston would have been used. A gear
may than he
necessary to obtain the required torque, and speed, depending on the purpose.
Other optimal configurations of for actuator chambers may be possible.
The parameters for an elongate chamber of which the actuator piston is
connected to a crank, may
be:
= relative short length L of the chamber, so as to obtain a relative short
stroke length,
the force F(p,d,g) may vary during the stroke from a 2nd to I" longitudinal
positions, so that
the maximum force is obtained when the actuator piston is almost reaching the
extremity of
first longitudinal positions [where F= the force from the piston rod; p= the
pressure inside
the actuator piston; d= the diameter of the chamber at a certain longitudinal
position; R= the
friction coefficient between the wall of the chamber and the flexible wall of
the actuator
piston],
CA 02786315 2012-08-24
the friction force F( ) during the entire return stroke is zero, which is
obtained by lightly
sucking out the overpressure of said actuator piston [F( ) = the friction
force between the wall
of the chamber and the flexible wall of the actuator piston],
= the velocity v( F) should be optimised with the length L of said chamber
[where v=speed of
the actuator piston relative to the chamber; =angle between the wall of the
chamber and the
cdentre axis of said chamber; F= force from the piston rod],
= the energy used is as less as possible - thus: the pressure drop (V) when
the actuatore piston
is moving from a 2n' to a 1" longitudinal position, while changing its volume,
while the
enclosed space temporarely has been closed, needs to be as less as possible.
The parameters for a chamber of which its wall is positioned around a
circleround centre axis, of
which its center is positioned on the centre of the main motor axle, where
said chamber is
rotating, and where more than one actuator piston is present and non-moving,
and being engaging
said chamber wall, may be, additionally to said chamber of Fig. 21A, having a
circleround
transversal cross-section:
= the circumference of chamber wall, irrespective the distance to the centre
of rotation, needs to
be identical - this may affect the shape of the transversal cross-section of
said chamber
= the friction force needs to be optimally small, e.g. by using enhanced
tibricators like
Superlube which has a much smaller friction coefficient than other libricant,
and which is
functioning well with rubber and metal, like steel or aluminium_
It may however be necessary to produce an optimal configuration of the piston
as well to achieve
the effect of that the circumference of chamber wall, irrespective the
distance to the centre of
rotation, needs to be identical, the circumference of chamber wall,
irrespective the distance to the
centre of rotation, needs to be identical -
CA 02786315 2012-08-24
1961 thermodynamical issues 5n 110
When the fluid in the system (elongate chambers with a an actuator piston
communicating with a crankshaft - chambers which may be symmetrically arranged
around a
circieround centre axis, which may be either communicating with a crankshaft,
or with the main
axle of a motor) is compressed, heat may very well be produced.
The storage of a fluid in a pressure storage vessel may have been arranged
while the
device, in which the motor is being used, was produced. While the motor runs,
a smaller portion
of beat may be generated in said storage vessel, when fluid of a higher
pressure from the last
pump of the pressurization cascade enters the fluid of said vessel, which may
have a lower
pressure (Figs. ltA-C, 12A-C, 13A-B).
The pressurization of the fluid which comes from the third enclosed space of a
motor type which uses a crank, which is assembled on the main axle of said
motor, generates a
much bigger portion of heat in the first pump of the pressurization cascade,
which may receive its
energy from the main axle. And another portion of approximately the same
magnitude of beat
may be generated with a pump which may gets its energy from the other energy
source(s)
(preferably any sustainable energy source(s) such as solar cells, a fuel cell,
electric batteries
which have been loaded by solar energy or optionally a classic energy source,
such as electric
batteries, which are being loaded by a generator which is communicating with a
combustion
engine) (Figs- I IAC, 12A).
In the actuator piston takes both pressurization in the enclosed space + the
cavity
within the actuator piston body from the second enclosed space, and expansion
to the third
enclosed space place. As the pressurization may be a bit more than the
expansion, the actuator
piston may get a higher temperature than its temperature when the motor
started (Figs. 11A-C,
11F, 12AC, 13A-E).
Thus this system is generating heat, which e.g. may be used for heating the
cabin
of a car, or to heat the third enclosed space, where expansion takes place
(adiabatic). Because this
is positioned in the crankshaft, it will not be easy to be done. Thus this may
be more or less a
diabatic situation.
Better of course is it to compensate the production of heat, there where it is
being
produced: the isothermal situation. In case the change of the pressure inside
the actuator piston is
being controlled by a piston which is moving in a chamber of a bi-directional
pump - which is in
CA 02786315 2012-08-24
fact an enclosed space of said actuator piston, both compression and
pressurization will take place
in said chamber by changing its volume, as that heat and cooling may
balancing: this may be the
case with the combination of a non-moving actuator piston and a moving
(rotating) cha,ber (Fig,
13F-G). Again, now with thermodynamic's aspect, is this the most efficient
motor principle,
because the (theoretical) efficiency may be near 100%.
CA 02786315 2012-08-24
1961 amended 19615 energy sources working together with the motor "n t^] 618
The motor may be working together with any other energy source, preferably
sustainable, optionally non-sustainable. Such energy source may be necessary
to feed the
approximately 7.5 % of the motor, which may be the limit of the efficiency
improvement in
relation to a classic motor burning fossile fuel, e.g. by using the Otto
cyclus.
Sustainable energy sources like e.g. the sun, potential energy from water and
wave
power and other sources, which do not result in emissions of undesirable
chemicals such as CO,
CO, NO etc., when the energy has been generated. -
For a motor according the invention may the energy source(s) preferably be
e.g.
electricity, a capacitator (= electricity stored in a very big condensator) or
electric batteries of
any type, charged by solar power through e.g. photo voltaic solar cells with
or without focus
means (mirrors), or by fuel cells e.g. using Hz, or air compressed by
potential hydroenergy etc.
An H. fuel cell may be `charged' with Hz, which may have been derived from
electrolyses of
H20, which may be stored in a vessel - the electricity may come from a special
battery, capable
of giving contineously energy (no starter battery) - this battery may be
charged by an alternator,
communicating with an axle of said motor and/or from photo voltaic solar
cells. The Hi may also
be stored in a special vessel, and may directly be inserted in the fuel cell.
Optional energy sources may be electricity, a capacitator or electric
batteries of any
type, loaded by an electric generator which is turning around on the basis of
steam, generated by
a fossile fueled burner, or a compressor driven by a motor, burning fossile
fuel etc.
A motor according the invention may have one energy source or a combination of
energy sources, preferably sustainable, optionally sustainable and non-
sustainable.
When the motor is used as a motor in a transport device, such as ships,
trains, cars
or aeroplanes, which has limited possibilities to connect to big energy
sources, the batteries may
be temporary charged by an external energy source, e.g. through an electric
cable- Filling up of
other energy containing materials, e.g. He may be done by hoses etc. Thus
charging the energy
bearing material positioned in said device by a temporary suitable connecting
to said external
energy source(s).
It may preferably be that said devices be able to move over such a strategic
distance,
where it is self-supporting without a longduring external fill up from an
external available power
CA 02786315 2012-08-24
source (e.g. electrical). A strategic distance may have several definitions,
e.g. for a commuting
car, 2x 50 km commuting + 40 km random per day may be enough without a refill,
and e.g. a
car used for traveling longer distances may need to travel 500 km without a
refill, or even twice
that distance. The last mentioned may be the limit for what humans may perform
per day.
Preferably may a movable power source (e.g. a battery, a fuel cell, an
electrolyses
of HO resulting in available H, for combustion purposes, pressurized fluid or
other possibilities
not mentioned here) which have been mounted in said transport device be self-
supporting for at
least one day. It may preferably also be possible to travel at night. Said
power source may
preferably not add very much to the extra dead weight (increasing the RAT),
specifically
important for cars, although this may not be decisive for the efficiency.
There are several battery types, and the newest are high power, are efficient,
but
add much to the extra weight and space. It takes a long time to charge these,
while an rapid
exchange of batteries is not feasible, as it demands an infrastructure, while
one may not be able to
separate new from old batteries. A charging from a and/or a solar cell may not
be enough for
the use of energy (see the feasibility study). It is necessary to have a plug,
and a connection to the
electricity network, which is an available infra-structure.
In order to reduce the charging time to 1-2 minutes, the `battery' based on
loading a condensator
of the size of a suitcase, and release controlled the electricy again to the
motor system may very
well he the solution for all the problems mentioned above while using a
battery. It is still under
development in the USA.
A fuel cell may not be cheap, not very efficient to generate electricity, but
adds not
very much to the extra weigth, and it is at noisy - this contrary the
traditional method when a
combustible (fossile) motor is communicating with a alternator - the e.g.
necessary H, may be a
security hazard, and storage of H, may be difficult, due to leaking from
vessels, which for other
matter are leak free. It may also need a distribution infrastructure, although
there are already
home based electrolyses systems on the market, which with electrolyses
produces I-h for own use.
However, after having seen in 2009 a moped, with a combustible motor (<50ec),
using H. from
instant electrolyses of water, said water being contained in the tank where
normally gasoline was
stored, it may be possible to do this for this motor according to this
invention as well. The
electricity for the electrolyses may come from a battery which is designed to
be used for
CA 02786315 2012-08-24
equipment (constant use), and which may be charged by an alternator, using the
rotational kinetic
energy from said motor, while electricity is additionally charged by e.g. a
solar cell.
The electricity generated by a fuel cell, e.g. using Ha, may be used to charge
said battery, of
which generated electricity may be used for the motor factions. An alternator
may be
communicating with the main axle of said motor, and additionally charge a
battery, e.g. said
constant use battery and a possible present start motor battery for a possible
present start motor.
Solar cells may add to charge said batteries. The electricity generated by a
fuel cell, e.g. using
Hi, may be connected directly to the motor functions, bypassing said
batter(y)(ies).
Another possibility may be that e.g. H2 is being used for combustible purposes
-
e.g. a motor comprising a classic piston-straight cylinder combination with a
crankshaft, turning
an axle which is communicating with an alternator, said alternator being
charging a battery. The
alternator may also be directly connected by wires with the other motor
functions. The power of
said combustible motor may be complying to the complement need for power, thus
what the
motor according this invention cannot generate. The power of said combustible
motor may be
very small in comparison with current combustible motors when used for 100%
for the motor
functions, which makes it feasible that e.g. the eleteolyses process for
generating Hz may be made
movable, e.g. to be used in a car.
What may be needed for the current invention is that a bi-directional pump,
which is
changing the volume of the enclosed space of e.g. the non-moving sphere
piston, positioned in a
rotating chamber may need electricity, if e.g. an electric motor may be used
for turning around an
axle which is communicating with a crank, on which the piston rod of said pump
has been
assembled. Said axle may be the main axle of said combustible motor using e.g.
Hz as fuel.
In another configuration, where said pump is used for a represmration of a
fluid,
which is used to control an actuator, which is controlling said pump, it may
have the same
configuration as in the overall solution mention above.
Another configuration may be used without using electricity for changing the
volume
of said enclosed space, when said pump has been exchanged by a camshaft -
electricity may than
only be necessary for a starter motor, and that may come from a starter
battery, which may be
charged by an alternator driven by the main axle of said motor, and/or by
solar cells. A camshaft
CA 02786315 2012-08-24
X52
solution may preferably be using more than one piston, optionally one piston.
A small pump may
be necessary for speeding up, which means a higher pressure in the actuator
piston, driven by the
main axle or by an electric motor, which gets its energy from a battery,
designed for constant
use.
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- CA 02786315 2012-08-24
invention may be constmcted with lighter weight than those based on the
classic pistoe-cylinder
combination.
For at the motor may fu etion in the darts, a complemen addition to the solar
cells
may be necessary. This may be e.g. sustainable power source. a fuel cell, e.g.
of a Elz type
which reacts with the 07 of the atmosphere, and giving electricity and HsO.
This fact cell may need
a relative sma11 storage vessel, which may be of reduced pressure. That is to
say, that the
distribution system for 02 may beat hone, or that the distribution system may
be not very dense.
In the motor type where an enclosed space is commmicnting with a represswnti-
cascade of
pumps, rise electricity may be used to give energy to elect is motor, which is
driving the piston
pump through another crankshaft - this may be One as a complement to the
energy or the solar
cells, e.g. when it is darts, or this may be done at any time.
Additionally may a generator been added to this motor type, which may he
driven by list main axle,
and which may load the nccumrdatnr.
In the motor type where the fluid in the enclosed space has been separated
tinm rise repressaration
cascade, possibly more electric energy may be needed, for the eoatro) of
valves. This nny make the
necessity of another sustainable power source, e.g. a fuel cell as described
above, than the solar
cells more likely.
It may also be used for an external cascade system, which has not yet been
added to the drawings
Fig. IIF and Fig. 13F, which may be needed for repuessuration of the pressure
vessel I Do), Bad
889, respectively. This may be done bye cascade of pumps, of which at best one
is comnonieatiug
with the main note, and at least one with an external power source. The pumps
may commincote
with a pressure vessel. F' eP,,. S6t.~.. h'os,. s ~ F') = t7 F --7 , is --p
o.I,e bt
lad' S`1
19617 gearbox - clutch ; n I i b'$
The motor according this invention may have a certain maximum for the number
of revolutions per
minute (rpm), which is limited by the change of shape and/or pressure at both
turning points
(first- and second longitudinal positions) when the piston is running in an
elongate chamber, or
when running in a circular chamber the change point from the first- to the
second circular point. The
flexibility of the inflatable piston is the key: its wall, which e.g. may be
made of rubber - thus the
hardness of the rubber - and the reinforcement layer, and how many
reinforcement layers are being
used, and, if used more than one layer is being used, the in between angle of
the reinforcement
layers - please see chapter 19650.
The motor according this invention is a two-stroke motor when a piston is
running in an elongate
chamber: one half revolution = power stroke, and the other half is the return
stroke. When we
compare it in the feasibility study with a four-stroke 4 cylinder 1595 cc VW
Golf Mark II petrol
motor, which has an idle speed of 700-800 rpm, and a maximum of 2500 (check)
rpm, the
comparable speeds of the motor according this invention maybe half of the
above mentioned, in
order to generate the some power, with the configuration according the
feasibility study. 'I his
reduced speed would suit the motor according this invention.
A reduced speed would limit the impels of the main motor axle, when a clutch
is starting to engage
with the flywheel. In the feasibility study has we figured out the
configuration of the motor, when
having a comparable torque per kg weight of the car, in relation to the above
mentioned Golf Mark
II - the 50% reduction of net weight of the car according to this invention,
cannot be taken into
account now, if we keep said configuration.
If a gearbox (manual, autmatic - e.g. the Van Doome's Variomatic or a common
automatic
gearbox with a fluid), is being used, the ratio's and the number of gears may
be different from those
in cars currently used. The last mentioned has to do with the specific
characteristics (limitation of
the fimctional window in terms of rpm of teh main motor axle) of a combustion
motor, which is not
present as the main part of the motor according the invention. The last
mentioned would, if a
gearbox would be necessary, preferably have an automatic gearbox, optionally a
manual gearbox.
Quantitative considerations may be as follows:
- wheel diameter: a 0,65m (VW Golf Mark II),
- motor idle speed: 350 - 400 rpm -motor driving speed: 2x idle speed.
Thus:
CA 02786315 2012-08-24
x'55
60 km/h: motor: 750 rpm CA 02786315 2012-08-24
wheels: 490 rpm thus: gear ratio: 1:1,5 down
90 km/h: motor: 1000 rpm
wheels: 735 rpm thus: gear ratio: 1:1,35 down
120 km/h: motor: 1250 rpm
wheels: 980 rpm thus: gear ratio: 1:1,28 down
140 km/h: motor: 1500 rpm
wheels: 1143 rpm thus: gear ratio: 1:1,31 down
Conclusions:
. If no reverse traction was necessary, a gearbox may be unnecessary, and by
that another
reduction of weigth could be obtained.
The rpm. seems still too high for the change of shape of the inflatable
piston, and if that has
been proved to be correct, a gearbox may be necessary - if so, the relatively
slow turning motor
may be needed to gear up its rpm., in order to be able to couple the motor to
the wheels by a
clutch; in order to be able to use these rpm. for normally sized wheels, it
may be necessary to
gear down again.
30
t 5G
CA 02786315 2012-08-24
19617 motorsonnd in til,iH
The sound pitch of the power part of the motor according this invention is of
very little magnitude
due to the lack of explosions, and that may make a big difference with the
common well-know,
engine sound of petrol motors based on the Otto Motor design (please see
Classiccars, issue no.
402, pages 86-89, February 2007, "Why engines sound so good" for prior art).
Instead, there may
be a sound of lubricated (e.g. Super Lube) friction of an inflatable rubber
piston body on metal or
plastic from the chamber - the sound may be of low frequency.
Only in the elongate chamber design will be a frequency of pitches of sounds
(from second to fast
longitudinal positions) / silence (from first to second longitudinal
positions), while there will be
contineously sounds in the circular chamber designs - as these also are
friction sounds, the sound
may be of low frequency.
Because the motor according this invention is a two-stroke motor (remember: a
green one!) while
most of the car motors today are four-stroke motors, the revolutions per
minute in the motor
according this invention may be half of that in a motor according the Otto
design, in order to
achieve the same or comparable power. Also this lowers the number of
revolutions per minute
which may add the sound to be of low frequency.
Additionally is there sound from a pump (compressor) which is generating the
pressure for
repressuretion of the pressure vessel. When a pump is a piston-chamber type
according this
invention, it may give some noise from valves and noise from the release of
fluid from the chamber
to the pressure vessel, and the intake of depressurized fluid - according the
type of motor
repressuration according to Figs. ........................
Current air compressors based on a piston moving in an elongate chamber sound
absolutely ungly.
These sounds may come from the fact that the speed of the air may be over the
speed of sound, so
that shock waves are the source of the ugglyness.
In the design according this invention will preferably the speed of the fluid
he lower than the speed
of sound, optionally will a schock wave from an over air speed wave be damped,
e.g. by contra
wave designs (such as Audi did in its race cars, which were almost without
noise, even the motor
was a combustibel motor type).
5~ S CA 02786315 2012-08-24
In the repressuration type according Figs ..................... there are no
valves, and only extra piston
chamber combinations, for deriving the pressure change. This motor type is
besides being the most
efficient, additionally the most quiet of all motor types according this
invention.
The generating of electric power for (re)loading a battery for powering the
pumps, which may re-
pressurize the presure vessel, which may be serving the pressure for the main
motor part, may need
an Otto Motor of approx. 60 cc (comparable to a moped motor) on preferably H2
as power fluid,
optionally petrol/diesel or any other combustible fluid (please see the
feasibility study). The sound
of such a moped motor is normally ugly, but may be sounding acceptable, if
sound dampened
enough.
Thus, the total sound of the motor according this invention is not zero, such
as is the case with an
electric motor, but a low pitching low frequency sound. This enables the car
to be identified by
sound as being a car, which is better is this aspect than a car with only an
electric motor running at
low speeds.
The low frequency may be altered if it is concluded from a working prototype
that the low
frequency is that of the
CA 02786315 2012-08-24
19620 SUMMARY OF THE INVEN17ON .
In the first aspect, the invention relates to a combination of a piston and-a
chamber, wherein:
said chamber comprising a wall of a cross-sectional border which is parallel
to the centre axis of said chamber.
[said chamber comprising a second chamber, which is communicating
with said first chamber through a channel comprising a longitudinal
cross-sectional section of which the wall is concave shaped, the wall
of said second chamber is parallel to the centre axis of said chamber.]
The conical chamber of e.g. an advanced bicycle pump may be updivided into
longitudinal cross-sectional sections of which its common borders are detined
by an over
pressure (e.g. over the atmospheric pressure) rating such as e.g. 1 Bar, 2 Bar
..... 10 Bar
which a piston may produce, while moving from a first to a second longitudinal
position of
said chamber. Said chamber comprising convex and concave shaped sections of
longitudinal
cross-sectional sections, said sections are updivided from earls other by
conunon-borders,
the resulting heigth of the walls of said longitudinal cross-sectional
sections are decreasing
by an increasing overpressure rate, the transversal length of the cross-
sectional common
borders is determined by the maximum work force, which is chosen constant for
said
common borders, at least near a second longitudinal position.
Another factor which is decisive for the proper shape of the longitudinal
cross-
section of said chamber, regarding proper sealing of the piston to the wall of
the chamber,
in a bottom position (a 2" position) of the piston, is that, there must be
enough space to
have the piston at that position and allowing it to move, e.g. when the
chamber has been
designed for lowering working force: the smallest longitudinal cross-sectional
area at the
point of the highest pressure: e.g. WO/2008/025391, where the smallest part of
the
chamber was o 17nna.
The longitudinal cross-sectional sections may have convex and/or concave
sides.
The part of the chamber where convex shapes end and where a concave wall part
is
beginning, and which is matching a cone shaped bottom part, is used in a
bicycle floor
pump for the purpose to keep the convex / concave shaped part of the chamber
on a certain
ergonomics] height, so that pumping is comfortable for the user
(WO/2008/025391).
CA 02786315 2012-08-24
A spring-force operated piston, e.g. a flexible expandable inflatable
container
piston (e.g. EP 1 384 004 01) may begin to. move by itself from a second
longitudinal
fararren. to a firer lnngitidinaLpositi~s id rhamh h elhe_anec-eecjaaat asna
a*,d
circumference of a second longitudinal postion is smaller than the cross-
sectional area and
circumference of a first longitudinal position, if a sealing pressure exists
from the piston to
the wall of convex / concave chamber walls, and if the longitudinal component
of the
friction force between the piston and the wall of the chamber is lower than
the longitudinal
component of the sealing force. In order for the piston rod to maintain its
position
controlled by a user of e.g. a bicycle pump, it may be necessary that the wall
of the
chamber which is in contact with said piston, is parallel to the central axis
of the chamber.
This parallelliry provides a sealing force without a longitudinal component,
and so remains
the piston which is sealing to the wall of the chamber in a position only
there, where the
user wants it to be. E.g. EP 1 179 140 BI shows chambers, where in the top
(first
longitudinal positions) and the bottom (second longitudoinal positions) of the
chamber a
part of the inner wall of said chamber is parallel to the central axis: thus
there where the
piston and is positioned when the pump is either not in use or where the
piston rod is
changing its direction, the last mentioned which also occurs in the top of the
chamber, by a
user, when the pump is in use. No reasoning was disclosed for the parallelliry
in EP 1 179
140 El
For said piston type to move from second to first longitudinal positions in
said
chamber is possible when said piston is engagingly movable or when said piston
is sealingly
movable in said chamber.
In the second aspect, the invention relates to a combination of a piston and a
chamber,
wherein:
said chamber has an exit between a convex wall and a concave wall,
said exit is communicating with a hose:
The longitudinal cross-sectional sections may have convex and/or concave
sides.
The part of the chamber where convex shapes end and where a concave wall part
may
begin, and which may matching a cone shaped bottom part, is used in a bicyle
floor pump
for the purpose to keep the convex /concave shaped part of the chamber on a
certain
ergonomics] height, so that pumping is comfortable for the user
(WO/2008/025391).
If said bottom part is hollow, it may be used it ht tree ways.
CA 02786315 2012-08-24
61~
An option is to keep this part open, and add an exit to said chamber at its
second
longitudinal position- Said exit may preferably communicate directly with a
hose.
Optionally said exit comprises a check valve, where said check -valve is
communicating with an expansion chamber, which is built in the bottom part of
said
chamber. The problem is, that such expansion chamber may be only nessessary,
for higher
pressures, and is than delaying the speed of the pump at lower pressures,
because the
volume of said expansion chamber is to be inflated as well, irrespectively the
pressure-
Such a solution may be nessesary if a piston would jam in a concave shaped
transition from
convex shaped wall parts to a further longitudinal position of the chamber, dr
the piston
would be too big to travel to a further longitudinal position.
In the third aspect, the invention relates to a combination of a piston and a
chamber, wherein:
said concave shaped walls are positioned at least between two common borders.
Preferably may said hollow pan be used as an additional pumping volume of said
chamber,
and the piston should be able to move toward and in said bottom pan without
jamming.
Necessary is than a smooth transition from convex shaped wall of cross-
sectional sections,
said transition comprising a concave shaped wall- Depending on the heigth of
the cross-
sectional sections - thus the pressure rate - these concave shaped walls may
be positioned at
least between more than two common borders, the last mentioned at high
pressures.
30
If there is not enough space near a second longitudinal position for the
piston to
move, one can chose to use that , there must be enough space to have the
piston at that
position and allowing it to more,
CA 02786315 2012-08-24
In the third aspect, the invention relates to a combination of a piston and a
chamber, wherein:
- said second chamber comprising a third chamber, communicating
through a check valve with said second chamber.
Tlms, there may be a point on the wall of said chamber where counted from a
first
longitudinal position, the convex shape of the sides of the longitudinal cross-
sectional area's
have to transfer to that part of the chamber in the bottom, where the wall of
the chamber
wall is parallel to the central axis. In order to do that smoothly, the
transition needs to be
from convex to concave - thus the shape of a side of the longitudinal cross-
section at the
transition needs to be concave in the direction from a first to a second
longitudinal position.
If the piston has a sealing which takes a certain longimdinale length, so much
that
the sealing cannot comply to the transition from convex shaped sides of the
longitidinal
cross-section to a concave shape, then a solution may be to close the chamber
there and
create an exit by a non-return valve, and use the rest of the chamber as an
expansion vessel
This may be usefiall for a proper pumping at high pressures.
The positions of said common borders are in both cases (the bottora pan used
as additional
pumping space vs. used as expansion vessel) on different lengths from a first
longitudinal
position, while their in-between distances are different - the stroke volume
of a pump with
an expansion vessel is less that that of a pump which is using the bottom part
as part of the
stroke volume.
In a-fourth aspect, the invention relates to to a combination of a piston and
a chamber,
wherein:
said chamber is elivated by a fourth chamber which is open, said chamber has
an exit, which -
end in said fourth chamber.
6~.
CA 02786315 2012-08-24
The fourth chamber is just the basic chamber with its chacteristic shape, and
nothing more.
. _._._-_Said_ebambecmay]rane_anexit_which_isarrippe]]..
In a fifth aspect, the invention relates to a combination of a piston and a
chamber, wherein:
said exit is communicating with a hose.
In order to optimize the pumping speed, the hose of a bicycle pump may be
expandable upon
a certain pressure, so that an expansion vessel is created there. That means
that the pump is
pumping very efficiently at low pressures, where the hose is not creating an
expansion vessel
- such a pressure vessel creates more volume to the volume of the tyre alone,
to be pumped.
Most of the pumping is done for low pressure tyres. The expansion of the hose
may be
limited by a reinforcement of the hose, and the expansion may be done only on
a part of the
hose-
wtxtrn h~ ~~ haV is ~ to
77'
-jS~t a( - bv2 t'lid
1 h-v {2;.S,,,
ii
CA 02786315 2012-08-24
Alt
1961f - added matter to the description of 19620 9 108 -
Using the chamber from Fig. 21A, which is used in an advanced bicycle pump,
the amount of
energy used may be reduced by approx. 65 % at 8-10 Bars pressure, in relation
to current high
pressure bicycle pumps. This has been calculated as follows:
The chamber of Fig. 21A has been designed, so that max. force is 260 N, at any
pressure,
specifically the higher pressures, thus also at 8 or 10 Bars.
Current high pressure pumps are comprising a straight cylinder with an
internal diameter of o 27
mm, so that the working force at 8 Bar is: F = p x O = 0,8 x 0,25 x 3,14 x 272
= 458 N. At 10
Bar this is: 572 N
The reduction at 8 Bar is: 458-260/458 = 198/458, so that the reduction is:
43%, and at 10 Bar:
54%. At 12 Bar: 687-272*/687 results in 60%, while 14 Bar gives: 801-
318**/801= 66% and 16
Bar: 916-363/916 = 60,3%.
The efficiency of said advanced bicycle pump is much higher than the current
high pressure
bicycle pumps, and that has influenced the choice of the 260N as a maximum
force. However, the
design has been made that the pump may have a higher pressure rate than l0
Bar, when the e
l7rmn straight cylinder part is being used as well, besides the conical part
of the chamber: F at 12
Bar: 1,2 x 0,25 x 3,14 x 172 = 272N*; F at 14 Bar: 318N**, 16 bar. 363N***.
Conclusion: the stated 65 % at 8-10 Bar should have been 54% - however, as the
chosen
maximum force of F = 260N influences the result, it may be a good to
recalculate the chamber
which as optimized for a bicycle pump, but now specifcially for the use in a
motor.
CA 02786315 2012-08-24
19617 - added matter for 19620 elongate conical chamber design ,'v 6 B
The chambers of Figs. 21A,21B, 22-25 (incl.) of EP Patent Application No.
100754027 (08-09-
2010) have been designed, based on the following mathematical considerations.
The shape of an elongate conical chamber of a pump, having a centre axis, is a
line connecting
certain dots (x-coordinate: along said centre axis, y-coordinate:
perpendicular on said centre axis)
outside said centre axis. Said chamber having different cross-sectional
area's, and a first and a
second longitudinal position, the first longitudinal position having a bigger
cross-sectional area than
that of a second longitudinal position, wherein between a piston is moving,
said piston is sealingly
connected to the wall of said chamber, having a production size corresponding
with the
circumference of said second longitudinal position, said piston having a
certain pre-determined
maximum working force due to said shape of teh chamber. The position of said
dots relative to said
centre axis is determined as follows.
When said piston is moving in an elongate conical chamber, from said first to
said second
longitudinal position, is the rest volume V. , which is defined as the volume
of said chamber at a
position L, , L, measured from the overpressure side of said piston to e.g. a
farthest away second
longitudinal position (0-point), where there is an overpressure P, , the
overpressure P. is counted in
relation to a standard pressure, e.g. the atmospheric pressure, used in this
calculation:
V, = 3,14.[0,00046. S,' +(1,118-0,00139.L). S,z + (900-2,236.L +
0,00139.L2).S,]
where:
V, is the rest volume at Px z Bar over standard pressure, where V. - Vo /
(z+l).
Vo = is the total volume of said conical chamber, where S = L = the total
length of said conical
chamber.
S, = a step in the iterative calculation process.
The longitudinal positions where P. = z Bar (z ) occurs within a certain
predefined pressure
window (e.g. 1 - 10 Bar overpressure), can now be calculated iteratively (in
order to overcome
calculations of 30 degree equations, when no computer software is available),
with the step S, which
may be a part (e.g. 1/1000) of the total length L of said conical chamber,
counted along said centre
axis: The S, is found from said equation, and gives the x-coordinate of said
dot, as S,.L.
G
CA 02786315 2012-08-24
If said chamber is comprising non-conical parts (as can be seen in e.g.
Figs.21A,B), than only the
projected length of conical wall parts on said centre axis need to be used in
the calculation of L and
L.
The y-coordinate of said dot is found as follows.
If a certain maximum working force F... has been chosen, than the position of
said dots at a certain
longitudinal position 1, at the centre axis, from a chosen 0-point, can be
derived as follows:
Dc= iFx,,/0,008.P, (PcinBar,Dinmm,Finkgl)
The y-coordinate of said dot from said centre axis at said longitudinal
position S,.L is D,/2, if a
symmetrical chamber design in the transversal direction has been chosen, as is
in said Figures.
The shape of the chamber wall is than a line through all the points found. In
practise is it possible to
smoothen ('peditise') said line, if it is drawn as a polyline, so that a
contineous shape of a chamber
wall results.
k66
CA 02786315 2012-08-24
19630 circular chamber design 5(,(- w A Ry Of 441 L in! VIWF, 0 (
The circular chamber shown in Fig.13C and 14D, where a chamber maybe moving
and the piston(s) do(es) non-moving, has been updivided into e.g. four
identical sub-chambers.
These chambers have been constructed in such a way that that the effect of
each may be that the
circular force of each piston, having a different position in each of the
circular subchambers, on the
chamber wall may be identical. This, to avoid unnessary friction, which would
decrease efficiency,
and add to wear of the pistons. The chamber may have a constant circulars.
force, thus a constant
torque. The size may only be depending on the pressure.
As such is it not necessary to updivide a circular chamber into more than one
chambers, in order to comprise more than one piston- However, the angle of the
wall of siad sub-
chambers is bigger than that of one chamber, having the same circle as centre
axis. That the force
of each chamber is bigger, than if only one chamber was used for several
pistons.
The chamber shown in Fig. 12B, where the piston may be moving and the chamber
may not, may have in fact the same basic design as the one mentioned above for
Figs. 13C and 14D.
The piston may have a constant circular force on said chamber wall.
Said sub-chambers have been constructed, so that the chamber is comprising two
circle sections in the circular section. Each of the circle sections have its
own centerpoint, which are
tying in opposite quadrants, around and at an identical distance of the center
point of the circular
centre axis of the (sub)chamber. Said circle sections arc lying around a
centre axis of the chamber.
which may be a circle.
SM-PVTI
In a final version, we exneet a cross-sectional section of such a chamber, in
comparison with that of the elongate chamber of Figs. 21A/B where there are
(virtual) common
border lines (9,11,13,15,17,19,21,23,2527) parallel to each other and
perpendicular to the centre
axis (3) of said elongate chamber (1), that a common border line in a
longitudinal cross-section of
the circular chamber is converging with a line drawn from the farthest
boundary of said chamber in
the cross-section to the centre point of the centre axis of said circular
chamber (e.g. the two arrowed
lines in Fig.27C with two center points) - but not is known where the exact
centre point is, and
whether or not the centre point of the farthest circular chamber line of said
cross-section is identical
with the centre point of the nearest circular chamber line of said cross-
section (in Figs. 27A-C we
assumed two centre points), in view of the requirement, that the maximum force
of the actuator in
CA 02786315 2012-08-24
said chamber on said chamber wall is independant of the position of said
actuator in said chamber,
and thus independant of the inside pressure of the actuator.
SM-PVT2
A chamber (with the above mentioned characteristics) is engagingly andlor
sealingly
moving over said sphere shaped piston (Fig.IOH with said attempted
configuration of the chamber),
which is positioned in said chamber. By moving the chamber over said piston a
comparable
problem arizes, as exists with the front wheels of a car, turning around a
comer-both front wheels
are not positioned at the same distance to the rotation center(s?), and in
order to get the car around
the corner, the wheels need to have independant axles, and neither the angles
of said wheels in
relation to said direction are not the same at the same time, nor the speed of
said wheels, Thus, the
reaction forces from the chamber on a contact area of the piston are not
equally divided over the
circumference of said contact line, which should (?) be identical with said
common border lines (of
an elongate chamber).
Thus, in that case may the engagingly/sealingly connection to the wall of said
piston not be a circle
line, but more a combination of a circle point (on the boundery of the cross-
section nearest to the
center of the circular chamber) to a circle section (on the farthest boundary
of said cross-section
from the center of the circular chamber), and in between said point and
section sections of different
sizes and possibly also shape(s). This may not be a big hazard, as the
connection to the wall of said
chamber only needs to be engagingly, in order to generate motion of said
chamber. Due to the
several sizes of a circumference, said contact may become from sealingly
(nearest the centre of the
circle round centre axis of said chamber) to engagingly (farthest to from the
centre of the circle
round centre axis of said chamber), and in between all kinds of combinations
of sealingly- and
engagingly contacts. This affects the size of the friction between the piston
and the chamber wall,
and that the direction in which the relative motion may be generated - in this
assumed
configuration should said direction be that of the shape of the chamber - is
it in our attempted
configuration (Figs 27A-C).
In order to reduce the friction may the sphere piston be rotatable around its
piston rod - thus around
the centre axis of the piston rod, which maybe parallel to an axis through a
centre point of said
chamber, perpendicular the cross-sectional section of said chamber.
CA 02786315 2012-08-24
ACTUATOR PISTON AND CHAMBER GEOMETRY
Configurations of piston and piston chambers are considered: Cir-
cular conic tubes containing a constant area, variable volume, flex-
ible actuator, piston with wall contact. Chambers are constructed
as Fermi tubes. Explicit calculations of volumes and contact areas
are appended in a roughly commented Maple worksheet. The actu-
ator force distribution is indicated. Figures are eomew}tat extreme
for the sake of illustrating the importance of the geometry.
1. Fermi tube construction
The central base circle (around which the chamber is'bent') is parametrized
by 'unit speed', has radius R and center at the origin (0, 0, 0) in a fixed
(x, y, z)-coordinate system. See blue circle in figeres,7; A etc. The
vector function for the base circle is standard: 32Q', 32 N
(1.1) y(u) = R (cos(u/R), sin(u/R), 0)
Along this base circle we will consider only the turning angle interval
u E [0, L] for which the piston has contact with the chamber wall.
In each orthogonal plane (see figures 1 and 2) to the base circle for
u E [0, L] we define a circle, which will eventually trace out the full
chamber and thence also that part of the piston which has chastber-
wall contact. These circles have radii p(u) which depend on the base
circle parameter u E [0,L[; and they all have their respective centers
on the base circle.
The family of circles trace out a tube surface, a so-called Fermi tube,
around the base circle.
We will assume that the function p(u) is linear in u so that the
corresponding Fermi surface may be called conic, see corresponding
32F,324aw13209ures . The conic effect (which will eventually drive the
piston inside the chamber) can be obtained by any other increasing
function of u. The linear radial function is then the following (this is
applied for specific values of o: and ,Q in the Maple appendix and used
for illustrations in this report):
6O
CA 02786315 2012-08-24
2 PISTON AND CHAMBER
(1.2) P(u)=n u+(3 .
The parametrized Fermi tube surface with radius function p(u) which
is 'bent' around the base circle is than given by the vector function:
(1.3) r(u, v) = y(u) + p(u) (cos(v) 0 (u) + sin(e) ea(u)) ,
where r, (u) and as (u) are orthogonal unit vectors which span the or-
thogonal plane to the base circle as shown in figure 1:
er(sa)=(cos(u/R),sn(u/R}, 0) ,
(1.4) ez(n)=(0,0,1)
The parametrized Fermi tube solid with radius function p(u) which
is likewise 'bent' around the base circle is than
(1.5) F(u, e,w)='5(u)+w p(u) (cor(n) er(u)+ein(v) ez(u))
Note that the surface is obtained from the corresponding solid simply
by setting w = 1
(1.6) r(u, v) = F(u, v, l)
The volume of the Fermi tube solid (corresponding to the turning
angle interval (0, L]) is determined by
1
(1.7) Vol= I _f' f~J(u,v,w)dudvdw
where the Jacobi function integrand is given by the partial derivatives
of F as follows:
(1.8) J(u, v, w) _ I (r~õ x F) F. I .
The area of the Fermi tube surface is (corresponding to the turning
angle interval [0, L])
/( (L
(1.9) Area J(u, v) du dv
where now the Jacobi function integrand is:
(1.10) J(u, v) - ~r;,x r.4
The Maple output appendix contains an example of the calculation
of the respective total area and total volume calculated from the cho-
sen values of the constants defining the geometry in the particular case
considered and shown. This is fully general and can be numerically
evaluated with my other choice of geometric descriptor values.
The total area and total volume includes the values from the end
caps which we now discuss.
f9'3 "i 0
CA 02786315 2012-08-24
PISTON AND CHAMBER 3
2. THE END CAPS
We assume that the end caps are spherical. This is not absolutely
needed. What we used is a circular fit to the tube part of the chamber
in both ends and a handle on the enclosed volume and total surface
area of the piston. Both are obtained most easily - for the present
model considerations - by spherical end caps, see figures A and II
32D 32.E
In fact the sperical assumption is not completely realistic either:
Given a perfectly elastic piston material it will at all times have
constant mean curvature wherever it has no wall contact, i.e. in this
setting it will (tend to) have the some spherical radius at both ends.
This condition is not implemented in the present discussion.
With a physically precise description of the flexible piston material
it is possible to estimate the actual shape of the end caps, the volume
they enclose, and thence at each instance of time the internal pressure
inside the piston.
Spherical caps have simple geometric expressions for their area and
'enclosed' volume, i.e. the volume cut off from a solid sphere when
cutting off the cap by a planar cut. Here we will therefore continue
with this Ausalz of spherical caps.
The area of the cap with height h and base radius a is (see figure 3):
(2.1) A(h,p)=o (a5+h5) .
The volume of the cap with height h and base radius a is
(2.2) V(h,p)-6. x h' (3as+h3) .
For completeness we display also the radius of the virtual sphere
from which the respective end caps are taken for u = 0 and u = L
respectively:
(2.3) '(u) - P(u) V 1 + (P'(u))z
In the tube geometry the values of a and h are determined only by
the radius function p(u) and its derivative d(u) at the u end-values
u = 0 and It = L respectively; the bear circle radius plays no role!
a = P(u)
(24) h p(u) (,/I-+ P'(.))
Thus the end cap areas and volumes are determined solely by the
respective values of p and p' when the spherical Ansatz is assumed to
CA 02786315 2012-08-24
4 PISTON AND CHAMBER
hold.
Since the end cap(s) are supported or attached to a shaft, say a rigid
version of the base circle, this attachment and the induced coupling of
forces there between shaft and piston will alter the spherical geometry
of the piston end(s). Given a precise description of the attachment and
of the piston material it could be possible to estimate the geometry of
the resulting deformed end caps. This will not be considered here.
3. MOVING THE PISTON AND SHAFT ATTACHMENT
Most important is the area and the geometry of the precise contact
between the piston and the chamber wall. It is via this contact that the
driving force on the piston is activated. In the present model the wall
contact is modeled by a Fermi tube mound a given base circle; volume
(pressure) and area (forces at the wall) are calculated accordingly.
The actual sliding force along the wall of the chamber is obtained by
geometrically symmetric (around that direction as axis) double projec-
tion of the gray total force on the chamber segment shown in figures
Q {d_321'1 Ci nsf-~li '4 4 12l asr betew.Hence theresulting sliding force
ispro-
portional to the longitudinal length of the segment and to the internal
pressure of the piston; pressure = force per area.
Depending on the friction model (friction between chamber well and
piston) and depending on the material properties (elasticity etc) of the
piston, this resulting force will drive the segment in the longitudinal
direction. Since the force at each segment is proportional to the longi-
tudinal length of the segment and hence proportional to the distance
of the segment from the center of the base circle, it will tend to (to
first order and again very much depending on the physical descriptors
alluded to above) orchestrate the resulting motion of the free piston
surface as a rotation around the center of the base circle-
If the piston is attached to a shaft along the base circle in the cham-
her, the force described can likewise be applied to pull or push the
attached circular shaft into circular motion around the center of the
base circle.
CA 02786315 2012-08-24
19640 SUMMARY OF THE INVENTION
EP I179140B1 shows on Figs. 5A-5H (incl.) a piston (Figs. 105A-105H of this
patent application), which is comprising six support means 43, which are
rotatably fastened
around an axle 44 to a piston rod 45. The other ends of said support means are
assembled on an
impervious flexible sheet, positioned between a flexible O-ring, which is
sealitsgly connected to
the wall of a piston-chamber combination, where the chamber is conical. Said 0-
ring is squeezed
to the wall by said support means, due to pulling springs which at one side
have been assembled
on said piston rod, and at the other end on said support means near said O-
ring, so as to spread
said support means from the piston rod to the wall of the chamber.
Additionally a spiral spring,
which is circleround laid on the impervious sheet, having its center on the
centre axis of said
chamber, and pressing said 0-ring to the wall of said chamber, there where
said support means
are not supporting directly said 0-ring. This was a main solution as a
solution principle.
The not yet solved aspect of this construction is that said impervious
flexible sheet is
free hanging and it may be pushed inwards (change shape) the piston (Fig. 5G,
5H) when
pressurized by a fluid under said sheet. Another not yet fully developed
aspect is a proper
assembling of the O-ring to said support means. And, a proper asseembling of
said support means
to a means which is keeping the O-ring in place between the assembling points
of said support
means to said O-ring.
There may be two prefered solutions for avoiding the change of shape of the
impervious flexible sheet. Other solutions may be possible, but have not been
not shown.
One is that said impervious flexible sheet may be assembled at the end of the
piston
rod, e.g. by a screw. Another solution may be, just to vulcanize said sheet on
and around the
piston rod. This fastening of said sheet to the piston rod may substantially
reduce (but hot avoid)
the change of shape of said sheet, when pressurized. And, additionally, a
shape change of said
sheet may additonally be reduced by a proper reinforcement of said sheet.
First of all, the sheet
may need to have a production size having a circumference which is
approximately that of the
circumference of the chamber wall at a second longitudinal position. In order
to seal said sheet to -
the wall of the chamber, when the piston is moving to a second longitudinal
position, said sheet
may need in the first instance to be spreaded, when firstly moving the piston
from said second
longitudinal position to a first longitudinal position. The pulling springs on
said support means
may be pulling a bit more than the pulling forces in said impervious sheet,
pulling it back to its
CA 02786315 2012-08-24
production size, when the piston is not at a second longitudinal position. A
third force may be
pulling the O-ring from the wall, and that happens when said sheet would bend
upwards when
pressurized. In order to substantially prevent that, the reinforcement may
comprise concentric
reinforments, which may have been made of flexible material in its length, or,
if made of non-
flexible material as a spiral, having the centre axis of the piston rod as
centrum. Other
reinforcement possibilities may be possible, but are not shown. The use of
said reinforcement
patterns mean that the sheet may be widened in 21), in a transversal plane,
perpendicular the
centre axis of said chamber, and only a bit in the direction of the centre
axis of said chamber.
Preferably is the reinforcment layer of said sheet positioned closest to the
high pressure side of
said sheet, and anodrer layer without reinfocements may be vulcanized on the
first mentioned
layer. The production thickness of each layer may be so thick, that the
decreased thickness at a
fast longitudinal position may be enough for a loegduring proper functioning
of said piston.
Also the O-ring may have a production size where its external circumference is
approximately the size of the circumference of said chamber at a second
longitudinal position.
Also here should the production diameter of said 0-ring be big enough to
compensate for the
decrease of thickness when the piston has been moved to a first longitudinal
position.
The impervious sheet may be vulcanised on / in said 0-ring, so as to achieve a
proper sealing, when the 0-ring is sealingly connected to the wall of the
chamber.
The lying spring may be vulcanized on both said O-ring, the ends of said
support
means and on the impervious sheet. This keep the whole together.
Having assembled the impervious flexible sheet onto the piston rod, the
widening of
said sheet may substantially be caused by the pulling forces of the springs on
said support means,
and by the rotation forces of said support means. There may be a balance of
forces of the internal
pull forces of the impervious flexible sheet , 0-ring and the pushing forces
of the lying spiral
spring and the pushing forces of said support means, and the reaction forces
of the wall to the 0-
ring, so that allways the O-ring may be pressed onto the wall of the chamber
for achieving a
sealingly connection. The lying spiral spring shown in the Figures of said
prior art, which mainly
should keep the 0-ring in place between the support means ends, would possibly
not give enough
force to do that job. Instead, an elastic metal rod may keep the O-ring better
in place. Both ends
CA 02786315 2012-08-24
of said rod may be sliding between two adjacent support means, while two rods
may stied along
each other through a support means-
10
20
30
CA 02786315 2012-08-24 - -
19650 SUMMARY OF THE INVENTION
EP 1 179 140 B1 discloses an elasticallyl deformable means, which has been
stiffened by stiff members, which are rotatably fastened to a common member,
such as a piston
3 rod, in case a piston may be made of said elastically deformable means. The
elastically
deformable means may have a tranversal cross-section of that of a trapezium.
When moving in
the chamber from a first longitidinal position to a second longitudinal
position, wherein the wall
of said chamber eta second longitudinal position is parallel to the centre
axis of said chamber, the
trapezium becomes more and more a rectangular. Said stiffereners may rotate to
an angle where
the stifferers are approx. positioned parallel to said centre axis, when the
piston is moving from a
first to second longitudinal position.
A foam may expand from a second longitudinal position in a elongate chamber to
a
bigger shape at a first longitudinal posirtimt. But it may be done in a
different way than expanding
an inflatable container which is comprising a flexible wall, with a production
size so that the
circumference is approximately the circumference of the wall of the chamber at
a second
longitudinal position (please see e.g. EP 1 384 004 Bl). When it is moved to a
first longitudinal
position, and it may need to be engagingly connected to the wall of said
chamber, the thickness of
the wall of said container may be decreased ("balloon effect").
A motor wherein a pump having a piston engagingly and/or sealingly movable in
a chamber,
wherein
in the elastically deformable means is made of Polyurethane-foam,
- the P13-foam is comprising a Polyurethene Memory foam and a Polyurethane
foam.
- the Polyurethane foam is comprising a major part is Polyurethane Memory
foam, and a minor
part Polyurethane foam.
An elastically deformable means may be made of a foam. Specifically good
characteristics for harsh circumstances as e.g. a moving piston in a chamber
of a pump may be
Polyuretban Foam.
CA 02786315 2012-08-24
The growing in size of a foam when moving from a second to a first
longitudinal
position may be done by enlarging the cells wherein the fluid is positioned,
which may be present
in said chamber. That may be possible, when the cells are open, that is to
say, that the inside of
said cells may be communicating with the atmosphere around said foam, in siad
chamber. Thus
. the foam at a second longitudinal position needs to be under pressure so as
to be able to decrease
the size of the open cells in the foam, and, at a second longitudinal position
needs the foam be
under pressure, in order to be able to expand itself, when moved to a first
longitudinal position.
The foam, thus the material of the walls of the open cells may than needed
being very elastically.
Such a material may be a Polyurethane (shortly `PU') foam, and a very flexible
type of PU foam
may be the so-called Memory Foam.
Materials which are very flexible may however not withstand very well big
pressure
by itself, such what a piston needs to be capable of. In order to gain a
better resistance to
pressure, a kind of a sandwhich may be made, which may be made of e.g. a two
layer PU, of
which one layer is made of less flexible PU foam than PU Memory Foam, and a
layer of PU
Memory Foam - the two layers may be glued to each other. If there is no space
for layers and/or
a sandwhich may be difficult to be produced, a mixture of a PU foam and a PU
Memory Foam
may be the solution. The percentage of a normal PU Foam may be a minor part of
the total
mixture.
A motor wherein said pump having said piston wherein
the support members are bendable,
said support members have been pre-determined bending force,
said members being locked in a holder, which is connected to the piston rod,
and being
rotatable around said bend of said stiffener in said holder,
said end is being under pressure of an adjustable member,
said longer end of siad stiffener having an increased tPk mess.
Said Memory Foam material is quickly regaining its original size when
released,
after having been depressed, at normal working temperatures, such as 10 - 100`
C. At lower
temperatures such as around the freezing point, it takes longer time, an that
may be too loong, in
CA 02786315 2012-08 -24`]~''
order to comply to the demand of engagingly and/or sealingly connected to teh
wall of the
chamber. It may be necessary that said stiffeners are being made of a sprung
material, so that
when the piston is moving from a second to a first longitudinal position, said
stiffeners may be
pressing the foam outwards. A pre determined bending force may be necesasary,
and that may be
done by e.g. the endof said stiffener, being bended a much shorter length than
the total length of
said stiffener, thereby the angle being capable of locking the end of said
stiffener in a holder -
said holder may be connected to the piston rod. The pre-determined bending
force may be
obtained by an adjustable member, which presses the short end of said
stiffeners - it may be a
rotatable member, which can be locked in a certain position.
When moving from a first to a second longitudinal position said foam may be
being
pressed inward by the wall of said chamber, and said foam may need to be in
such a shape, that
no lateral forces are present, so that the cast foam, which glues to said
stiffeners (which may he
preferably made of Polyurethane), has become unstuck, so that its function is
lost.
In order to avoid that said stiffeners are becoming intuck another measure is
to
increase the thickness of the long end of said stiffeners, close to where
pressure is obtained from
the fluid ender the piston in said chamber.
A motor wherein said pump having said piston wherein
- said flexible impervious layer has an unstressed production size with a
circumference which is
approximately the same as the circumference of the wall of the chamber at a
second longitudinal
position.
A foam piston with open cells is engaingly connected to the wall of said
chamber. In
order to make it sealingly connectable to said chamber wall it is necessary to
add an impervious
layer, such as a nature rubber type. This may need to comply to approximately
the same sizes of
a circumference as an inflatable container type piston. That may need the size
of said layer
buying a circumference of that of the chamber wall at a second longitudinal
position, unstressed -
thus needs the assembling be around a foam under pressure. When moving from a
second to a
first longitudinal position, the foam and thus said stiffeners) need to press
the layer-into the shape
CA 02786315 2012-08-24
(trapez) of the foam when being positioned at a first longitudinal position.
When returning to said
second longitudinal position, said layer may be shrinking into the approx.
rectangular shape of
said foam at a second longitudinal position: it needs to be flexible. The
impervious layer may
need to be able to communicate with the fluid of the non-pressure side of said
piston in order to
be able the open cells to communicate (`breath'), when moving from second to
first longitudinal
positions and vice versa.
to
20
30
CA 02786315 2012-08-24
19650-1 improved suspension of foam piston for e.g. pumping purposes
W02000/070227 discloses a foam piston which has the problem that the foam
cannot
not properly be mounted on the piston rod, specifically during the return
stroke. The reason is that
the PU foam cannot be fastened very well to the steel of the piston rod.
Another difficulty is the
release of the ready piston from the mould. due to the fact that the angles of
the several rows of
reinforcement pins are increasing outwards from the piston rod side. A further
difficulty is that PU
foam is not very well fastening on a metal reinforment pin, even the surface
of the last mentioned
has been made rough. The improved suspension of the foam piston is the subject
matter of this
section of the patent application.
The piston disclosed in the section 19650 of this patent application is very
robust for professional
use. For the use in e.g. a bicycle pump a less robust, still reliable
construction may be needed,
where also repair may be simply and straight forward.
The solution is according to the characteristic part of the independant claim.
The use of metal pins may be maintained, when e.g. the pins have received a
surface
coating of an appropriate material, e.g. PU when the foam of the piston also
is made of PU, before
the foam piston has been moulded around said pins - than the pins will fasten
enough to the foam,
to avoid stripping off the foam of said piston. The metal pins may be made of
a steel type which can
be magnetized. If the holder plate, to which the pins are designed to transfer
the compression force
from the high pressure side of the piston to the piston rod, is being
magnetized, said pins may be
sticking into small holes of about a deepness to said surface, approximately
the size of the diameter
of said pins. Said holes may have a geometrical design, so that said pins may
be able to rotate in
said holes. Said pins will be fastened to said holder plate, as soon as these
have come near enough
to each other, so that the magnetic force can do it's work. Said holder plate
may have s small
thickness, and may be glued to the piston rod, directly or indirectly on a
holder, which is assembled
on a piston rod.
Another still more improved version of the pins may be that these have been
made e.g.
by injection moulding of e.g. PU-plastic, which will stick perfectly to the
same type of foam (e..g
PU foam) of the piston. Here is the extra possibility to avoiding stripping
the PU foam off the pins,
by making many small reduction of the diameters of said pins. The suspension
of the pins may be
done as follows. The pins may have a sphere shaped end which can be smoothly
pressed in a holder
plate, having a sphere cavity, so that said sphere end may rotate in said
sphere cavity. The pins may
CA 02786315 2012-08-24
have a certain pre-loading, so that the foam will be widened when the piston
is moving from a 2 a to
a 10 longitudinal position of the chamber, specifically at lower temperatures.
This may be done by
giving the sphere end of said pins a small lever arm, which is sticking in a
plate of flexible material,
e.g. rubber. The production angle is than the widest angle of said piston,
thus when the piston is at a
1 longitudinal position of the chamber.
CA 02786315 2012-08-24
19660 SUMMARY OF THE INVENTION
BPI 179140 BI shows an inflatab{e contaieorpiston type, while EP 1304004 BI
shows that
this piston type should have an sastresed production size wherein its
circumference at the second
longitudinal position of an elongate chamber, should have a circumference
which is approximately the same
as the one of the chamber, so as to avoid that the piston is jamming when
moving from a first to a second
longitudinal position.
The piston is expanding when moved from a second to a first longitudinal
position. EP 1384
004 BI shows that a reinforcement for such a desired behaviour may be a layer
where the reinforcement
strengs are laying parallel besides each other in an unstressed production
model, and these strengs are
connecting the two end parts, of which one is mounted on the piston rod, while
the other ican glide of the
piston rod - the rubber is directly vulcanized on both ends. The reinforcemnet
layer is the inner layer, while
another, thicker layer than the layer with reeinforcement strengs, is
protechting said reinforcement layer.
Both layers are being vulcanized on each other, and at the end parts, there
may he another extra layer on top
of the two. The function of the second layer is additionally to avoid that the
reinforcement strengs arc
`sticking' out of the outer layer, thereby making a sealingly contact with the
wall of the chamber impossible
-however, for an engagingly contact is this just fine. Hacving the second
layer on top of the reinforcement
layer is working fine in practise, and it has shown be possible to expand near
the 330%, e.g. in a chamber of
a pump (please see 19620) where the force on the piston rod is constant, from
an a17 mm (2ntl longitudinal
position) to an a 59 mm (1" longitudinal position). With two reirrforemrst
layers on top of each other with a
,cry small angle for overlapping each other, and on top the above mentioned
`second' layer makes the
container more strong, but expansions possible are much less 330%.
The types of rubber of the layers rubber may be different, but should be
counpubbal ao, that
these can be vulcanized an each other, without getting lose fm each other
under normal working
conditions.
It was observed that when the ellipsoids shaped container type piston was
expanding
completely to its sphere shape, the chance of breaking apart was very present -
that is why the design may be
changed so that the length of the piston as unstressed production model be
increased, by keeping the other
variables, such as the chamber design unchanged-thus, the sphere shape maynot
be reached and neither an
expansion to 330%, only an ellipsoide which has almost become the shape of a
sphere - this makes the
piston reliable, even with one layer with reinforcements.
The shape of the container in an unstressed production state may also be that
the wall of the
container is not parallel with the centre axis, but parallel to the wall of
the chamber because the wall of the
CA 02786315 2012-08-24
a7gL
chamber at a second longitudinal position is not parallel to the centre axis.
Just the wa11 of the chamber is
free of the wall of the container in said nnstiessed production state.
15
25
35
a3
CA 02786315 2012-08-24
19660-1.2 Update on the functioning of actuator piston
The actuator piston is comprising a container, said container is comprising
awall around a cavity,
said cavity may be inflatable and pressurized by a fluid and/or may comprise a
foam, said container
is moving from 2"a to is` longitudinal positions of the chamber, when
pressurized, in a chamber
having cross-sections of different cross-sectional areas and different
circmnferential lengths at the
first and second longitudinal positions, and at least substantially
continuously different cross-
sectional areas and circumferential lengths at intermediate longitudinal
positions between the first
and second longitudinal positions, the cross-sectional area and
circmnferential length at said second
longitudinal position being smaller than the cross-sectional area and
circmnferential length at said
fast longitudinal position, due to sliding of the wall of said container of
said actuator piston on the
wall of said chamber.
This may also be the case for chambers having cross-sections of different
cross-sectional areas and
equal circumferential lengths at the first and second longitudinal positions,
and at an intermediate
longitudinal position.
Said wall of the piston may preferably having a symmetrical shape in the
longitudinal direction of
the chamber between the end cabs (the movable and the non-movable), around a
transversal central
axis, wherein each symmetrical half part having longitudinal cross-sections of
different cross-
sectional areas and different circumferential lengths at least substantially
continuously different
cross-sectional areas and circumferential lengths at intermediate longitudinal
positions between said
transversal centre axis and an end cab.
This may also be the case when said circumferential lengths are equal.
Having a reinforcement layer in the wall of said container of actuator piston
makes the outside of
said wall smooth, and preferably convex shaped, when pressurized from within
the cavity of said
container. This provides a small contact area with the wall of said chamber.
The expansion forces of
the wall of said container are directed perpendicular the surface of the wall
of said chamber. The
expansion forces maybe much larger than the pressure inside the cavity of the
actuator piston,
depending on the t/R ratio (R= transversal radius of a longitudinal cross-
sectional section, l = wall
thickness of the actuator piston), specifically when t/R<<<,
SCI
CA 02786315 2012-08-24
When said actuator piston is being positioned in a wall of a chamber having am
positive angle with
the centre axis of said chamber in the direction from a 2"d to a 1"
longitudinal position, an
asymmetry arises in the reaction forces from the wall of said chamber, because
there will be no
reaction forces on chamber positions nearest a 1" longitudinal position of the
chamber on the
ultimate position nearest a 1" longitudinal position part of the contact area
(wall chamber -
contaiber), and the consequences are that the wall of said container at these
positions will bend
towards the wall of said chamber, until the reaction foces of the wall equal
the expansion forces of
the wall of said container - the wall of said conatiner of the actuator piston
is rolling over the wall
of said chamber, This rolling is adding to the contact height of the contact
area of the wall of said
container and the wall of said chamber, where so the frictional forces
increase. Said expansion of
the wall of container of the actuator piston is causing a small pressure drop
inside the wall of said
container, when the volume of the enclosed space remaims constant, said
pressure drop causes that
the expansion forces of the wall of said piston are decreasing, that also the
friction forces, A
movement of said actuator piston towards a I" longitudinal position may occur
(sliding). This may
reduce said contact height, because the portion of said wall of the container
nearest a 2"A
longitudinal position may reduce its circumference, and thus also that of the
contact area nearest a
2"' longitudinal position.
Due to the lubrication between the wall of said chamber and the wall of said
container, the
propulsion forces are still bigger than said friction forces, and the actuator
piston will slide to a new
chamber position newer a first longitudinal position, until said asymmetri of
forces occurs again,
whereafter the cycle may start again.
It is the ability to increase (- rolling) a contact heigth in a longitudinal
cross-section of the engaging
wall of the container and the wall of the chamber, thereby malting the height
in immediate
continuation of the existing height larger, that is the main reason of the
behavouir of the actuator
piston.
The means to do so are: ~ e.P, (t_h
= when present, a bendable reinforcement layer of which the direction of
reinforcement is in
longitudinal direction approx. parallel to the centre axis of the chamber,
CA 02786315 2012-08-24
= none of almost no reinforcement in the transversal direction,
= preferably a symmetrical wall of the container around a transversal
symmetrical axis,
= a smooth surface of the wall of the actuator piston, at least on and
contineously until nearby its
contact area with the wall of the chamber,
than,
the wall of the container will under internal pressure bend out from an
ultimate circumference of the
contact area nearest a first longitudinal position, between the wall of the
chamber and the wall of
the container, and reaching the wall of the chamber, thereaby increasing the
contact surface area,
and
the wall of the container near a second longitudinal position will thereafter
under said bending
retract from the wall of the chamber,
whereafter the contact surface area area between the wall of the container and
the wall of the
chamber again is decreasing.
The actuator piston will stop running towards a 1" longitudinal position, when
there may be not
sufficient internal pressure to press the wall of the container of the
actuator piston towards the wall
of the chamber, so that a circumferential leak occurs. This may happen e.g. in
case of a chamber
shown in section 19620 of this patent application, when the common border of 1
Bar overpressure
exists in the chamber - this is earlier in the description disclosed as the
"hesitation behaviour".
In practise a behaviour is seen that a container of an actuator piston, of
which the movable cab is
positioned nearest a 1" longitudinal position, is moving stepwardsly, when the
pressure inside the
cavity of the actuator piston is quite low.
The reason may be that the expansion of the wall of said actuator piston, when
moving from 2n to
10 longitudinal positions, is additionally forcing the contact area of the
wall of said actuator piston
to the wall of the chamber nearest to the 1" longitudinal position, besides
the expansion of the wall
of the container due to the internal pressure, thus also increasing the
friction force.
In case the non-movable cab is positioned nearest a 1" longitudinal position,
thus `ahead' of the
container in the direction of the movement, even the pressure is low, the
movement is smoothly.
The reason maybe that the extra force of the expansion of the wall of the
container may add to the
reduced expansion force, and not exceeding the friction force.
8G
CA 02786315 2012-08-24
Thus: the wall of the piston is made of a flexible reinforced material, when
pressurized by a
pressure source through the enclosed space, which is resulting in a smooth
outer surface of said
piston wall, and by that, providing a height of the contact area
circumferentially in a longitudinal
cross-section of said piston, between said piston wall and the wall of the
chamber, said height is
changing in size during the movement of the piston at intermediate
longitudinal positions between
the second and first longitudinal positions.
This sliding may done over several different contact area's of the wall of
said actuator piston, with
the wall of said chamber. This is possible, because the wallof said container
is convex shaped,
flexible, while the several different area's are positioned in continuation of
each other.
CA 02786315 2012-08-24
19660-2 inflatable piston - strength and stiffness
The inflatable piston of the type where an ellipsoide at a 2nd longitudinal
position of a
chamber is becoming a enlarged ellipsoide / (almost) sphere, can, regarding
strength and stiffness,
be compared to a cylindrical vessel with a small wall thickness, which is
under internal pressure.
The Hoop stress on is expanding the wall of the cylinder. The size of said
Hoop stress
nH tis in general approximately l Ox the size of the internal pressure in said
cylinder'. This is the
reason why a the actuator piston already at a low internal pressure is
rocketing from a 2n to a 1"
longitudinal positions in a cylinder according section 19620 of this patent
aplication.
The size of the Hoop stress as depends on the longitudinal position of the
piston, the
size of the chamber and on the number of reinforcement layers - for one
reinforcement layer, and a
- 2nd longitudinal position / e l7mm: is approx. 3x the internal pressure in
the piston,
- 1" longitudinal position / o 58mm: is approx. 3,8x the internal pressure in
the piston.
The inflatable piston of the type where a sphere at a 2nd longitudinal
position of a
chamber is becoming an enlarged sphere, can, regarding strength and stiffness,
be compared with a
sphere vessel, with a small thickness, which is under internal pressure.
The spherical stress ass which applies, can be compared with the longitudinal
stress at
of a cylindrical cylinder, which is half of the size of the Hoop stress an .
This means that a sphere
piston in a circular chamber may give half the propulsion force of that of an
ellipsoide. Thus, more
than one sphere piston may be available in a circular chamber, in order to
reduce the size of a
motor, while having a comparable torque.
Thus: the stress which expands the wall of the actuator piston is depending on
the
thickness t of the wall of the actuator piston, in relation the the
transversal radius R of the actuator
piston, is C, _ [1-t/R] times the pressure in the actuator piston. Cx may be
different form one
longitudinal pisition of the actuator piston to another, as R may depend on
the transversal radius of
the chamber. This may be saving energy, and how much is depending on the slope
of the wall of the
= pRS p= internal pressure, R- 'h diameter of the cylinder, t= wall thickness
of the cylinder.
' Strength and Stiffness of Engineering Systems, Frederick A Leckie, Dominigae
I. Dalbello, Springer, 2009
ISBN: 978-0-337-49473-9
s = pR12t p- internal pressure, R- 'h diameter of the sphere, t= wall
thickness of the sphere.
88
CA 02786315 2012-08-24
chamber, because the propulsion force of an actuator piston is the expansion
force of the wall of the
actuator x the sin of the angle between the wall of the chamber with its
longitudinal centre axis.
The bigger said angle is the bigger is the propulsion force.
As an example: we find out the magnitude of a motor, as a replacement fora
petrol
motor for a Golf MK II, which has 081 mm cylinders, stroke length 77,4 mm, and
which is
operating between 9-10 Bar.
The slope of the chamber is chosen: a - I OS, thus sin IOo = 0,174, while we
keep a cylinder e -
81 mm, at a 1 longitudinal position- this gives 0 53,7mm at a 2nd
longitudinal position, and a wall
thickness of the actuator piston: 3.5mm - pressure at a 2nd LP = 10 Bar, at a
1" LP - 2,25 Bar.
C, = R/t [I - t/R ] = 10,6 -a our = 24 N/mmc -a F smpmsmn, = 2125 N
C2-R/t [I -t/R]= 6,7 -a am =67N/mmr *Fr,~põis;mr= 3933N
Conclusion: it is possible to use a motor according to this invention, which
has approximately the
size of a current petrol motor.
CA 02786315 2012-08-24
19689-2 - Pump Piston comprising a container
The aim of this section is to develop a container type piston, which may be
used in a
pump, while using the principle disclosed of W02002/077457, where the
emcunrfereaee of said
piston is having a production size of that of the circumference of the 2nd
longitudinal position. That
means that an inflatable container type piston is to be inflated from a 2nd
longitudinal position for
moving to a 1st longitudinal position and back without jamming. However, it is
the experience that
the travel: rolling - sliding - rolling etc. from a 2"d to a 1" longitudinal
position is done solely by
means of the internal pressure of said piston, having a contineous outside
wall of said piston, a
contact area with the wall of said chamber which is positioned under the
transversal centre line of
said piston, and a movable cab closest to the 1" longitudinal position, while
the non-movable cab is
closest to the 2' longitudinal position.
The experience is that the self propelling ability is out of function, when
the wall of
said chamber is parallel to the centre axis of said chamber. Thus, in order to
use the piston in a
pump, the selfpropelling motion should the "rolling" of the wall of said
piston over the wall of the
chamber should be avoided. This may be done by discontinuation of the outside
wall of said piston.
The creation of a self-propelling actuator piston, a "rolling-sliding-rolling
etc. of the
wall of said piston over the wall of said conical chamber" should be avoided,
as it generates a
propulsion force in the opposite direction of the pumping force. In order to
do so, the contact arm
between the wall of said chamber and the wall of said piston may be restricted
("dis-contineous") to
a certain area of the wall of said piston, and that may be done at least in
two ways:
the contact area may be a separate part of the wall of said piston, so that it
expands more
that the rest of the wall of said piston,
= the part of said piston closest to the second longitudinal position may have
a smaller
circumference of a transversal cross-section than that of said contact area.
R
CA 02786315 2012-08-24
The hoop stress in the wall of a inflatable container type piston (please we
sections
19660, 207 and 653 of this patent application) is causing the expansion of the
circumference of said
wall, and is the source of the actuator piston to become self-propelling by
internal overpressure.
Thus has said hoop stress a big impact on the sealing ability of said piston
to a chamber wall, and
thus at the same time is the ability to jam big, when said piston is pushed
from a 1" to a 2"
longitudinal position. Due to the specific R/t ratio (big radius in comparison
to a small wall
thickness (which is the layer which is having the reinforcement layer(s)), is
the hoop stress much
higher than the pressure inside. A first thought may be that "thus" may the
pressure of the gaseous
medium inside said piston be low, in relation to the pressure of a medium in
the chamber, wherein
said piston is situated, and which is compressed by said piston. However, the
piston has to seal at
any pressure of the medium to be pumped.
As at the same time, it has shown to be impossible to push by hand an inflated
(with a
compressible medium such as 0f) piston (according those shown in said
sections), in a chamber
shown in section 19597 of this patent application, said piston is comprising a
compressible medium
having 1-1 % bar (absolute) overpressure (over atmospheric pressure) at a
first longitudinal position,
from said first longitudinal position to a second longitudinal position, said
medium to expand the
wall of said piston may preferably be:
= different from that of a compressible medium such as a gas - e.g. a foam
would than be
better, even it may contain a fluid in its holes, when the foam having an open
structure -
it would be preferable that the foam has an open structure - said foam should
preferably
be at atmospheric pressure at a first longitudinal position, optionally at a
low over
pressure (e.g. I Bar). The foam, and preferably not said medium should be
expanding
the wall of said piston, optionally may there be a combination of said two
factors,
= and/or different from a medium which is compressible, such as a non-
compressible
medium (e.g. a liquid such as water),
= and communicating with an enclosed space, e.g. a hollow piston rod, in which
the
medium, which will be pressed out of said foam, thus from said container, when
said
foam is compressed by the wall of said piston, when said piston is moving from
a that
to a second longitudinal position, to said enclosed space (e.g. W02010/094317
or
CA 02786315 2012-08-24
sections 207 and/or 653), in order to avoid a steep rise of the internal
pressure, and
thereby a possible jamming.
An alternative solution for avoiding the creating a self-propelling actuator
piston,
when using an inflatable piston, is that the piston may have a wall without of
with a reinforced part,
whereby said the reinforcement may be minimal, only avoiding any exhurbitant
svallowing up of
the wall of the piston when inflated, and a foam, preferably an open cell
foam. The open cells may
be containg a fluid, preferably a gaseous medium, optionally a liquid Or a
combination of a liquid
and a gaseous medium. Said foam may be inserted into the piston when the
piston is in its first
longitudinal position, and the wall of said piston is engagingly and/or
sealingly connected to the
wall of the chamber, so that it is filling up the biggest volume of said
piston, when the wall of said
piston is in tension, with a smaller wall thickness than that when produced
(in the second
longitudinal position). The foam may be able to be compressible to an high
order (e.g. 5:1 when
using the piston of sections 19660 and /or 19680), so that the piston may be
filled with a denser
foam when being at a second longitudinal position, where almost all of the
open cells have been
closed - when moving from a first to a second longitudinal position the medium
inside said foam
may then be removed from said piston, e.g. to a piston rod. In order to avoid
the building up of high
pressure inside said piston rod, may the piston rod have a movable piston,
which is reducing the
volume of the medium in the open cells (when not being at a second
longitudinal position). This
high pressure world be causing of the piston becoming an actuator piston, and
jamming when
moving from a first to a second longitudinal position. The result may be a
piston which is changing
size (and may additionally be changing shape), with just a sufficient sealing
force to the wall of the
chamber during the pump stroke, without moving itself, and without jamming The
wall of said
piston made of a flexible material, e.g. rubber, makes said piston a reliable
piston for a pump.
The production of said container piston comprising a foam would be as follows:
the wall of said
container piston is produced when it is at a 2d longitudinal position.
Thereafter a fluid is injected
into the cavity of said container, when it is at a l" longitudinal position -
the movable cab is
moving towards the other cab, and the wall of the container is bowed. Then the
position of the
movable cap is being fixed, whereafter the fluid is released from the cavity.
The foam blend is now
injected, and the cavity of said continuer is closed. After hardening, is the
fixture of the movable
cap removed. Then a shrinkage may occur of the wall of said container, due to
the nature of said
~2
CA 02786315 2012-08-24
foam, comprising open cells. This shrinkage may be compensated by a very small
increasing of the
pressure of the medium in said open cells, hr by having another cavity within
a impervious flexible
wall, positioned within the center of said foam, said cavity may be inflated,
and which then presses
the foam towards the well of mid container piston, in order to get the wall to
its originally planned
position.
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43
20'7 SUMMARY OF THE INVENTION
-In-general; a-nevrdesigtrfor~eornbieatien eF-n-ebamber-and--a-piston-for-eg--
a-prinrymttsl-
ensure that the force to be applied to operate the-pomp during the entire
pumping operation is low
enough to be felt as being comfortable by the user, that the length of a
stroke is suitable, especially for
women and teenagers, that the pumping time is not prolonged, and that the pump
has a minimum of
components reliable and almost free of maintenance time.
In a first aspect, the invention relates to a combination of a piston and a
chamber, wherein:
the chamber defines an elongate chamber having a longitudinal axis,
- the chamber having, at a first longitudinal position thereof, a first cross-
sectional area thereof
and, at a second longitudinal position thereof, a second cross-sectional area,
the second moss-sectional
area being 95 % or less of the first cross-sectional area, the change in cross-
section of the chamber being
at least substantially continuous between the first and second longitudinal
positions,
the piston being adapted to adapt itself to the cross-section of the chamber
when moving from the first to
the second longitudinal position of the chamber.
In the present context, the cross-sections are preferably taken
perpendicularly to the longitudinal axis.
Also, due to the fact that in order for the piston to be able to seal against
the inner wall of the
chamber during movement between the first and second longitudinal positions,
the variation of the cross-
section of the chamber is preferably at least substantially continuous - that
is, without abrupt changes in
a longitudinal cross section of the inner wall.
In the present context, the cross-sectional area of the chamber is the cross-
sectional atea of the
inner space thereof in the cross-section selected.
Thus, as will become clear in the following, the fact that the area of the
inner chamber changes
brings about the possibility of actually tailoring the combination to a number
of situations.
In a preferred embodiment, the combination is used as a pump, whereby the
movement of the
piston will compress air and output this through a valve into e.g. a lyre. The
area of the piston and the
pressure on the other side of the valve will determine the force required in
order to provide a flow of air
through the valve, Thus, an adaptation of the force required may take place.
Also, he volume of air
provided will depend on the area of the piston. However, in order to compress
the air, the first
CA 02786315 2012-08-24
CA 02786315 2012-08-24
translation of the piston will be relatively easy (the pressure is relatively
low), whereby this may be
perfomrd with a large_azea_"C6us^totallyra:largeramnnr,r of ;;r maTla poa
ded.at_a-gi,piessuie-
during a single stroke of a certain length.
Naturally, the actual reduction of the area may depend on the intended use of
the combination
as well as the force in question.
Preferably, the second cross-sectional area is 95-15%, such as 95-70% of the
first cross-
sectional area. In certain situations, the second cross-sectional area is
approximately 50% of the first
cross-sectional area.
A number of different technologies may be used in order to realise this
combination. These
technologies are described further in relation to the subsequent aspects of
the invention.
One such technology is one wherein the piston comprises:
a plurality of at least substantially stiff support members rotatably fastened
to a common -
on-bet,
75 - elastically deformable means, supported by the supporting members, for
sealing against an
inner wall of the chamber,
the support members being rotatable between 10v and 40" relative to the
longitudinal axis.
2D In that situation, the common member may be attached to a handle for use by
an operator, and
wherein the support members extend, in the chamber, in a direction relatively
away from the handle.
Preferably, the support members are rotatable so as to be at least
approximately parallel to the
longitudinal axis.
Also, the combination may further comprise means for biasing the support
members against an
25 inner wa11 of the chamber -
Another technology is one wherein the piston comprises an elastically
deformable container
comprising a deformable material.
CA 02786315 2012-08-24
In that situation, the deformable material may be a fluid or a mixture of
fluids, such as water,
t _, a_nrllnrg~tn f flm
Also, in a cross section through the longitudinal direction, the container may
have a first shape
at the first longitudinal direction and a second shape at the second
longitudinal direction, the first shape
being different from the second shape.
Then, at least part of the deformable material may be compressible and wherein
the first shape
has an area being larger than an area of the second shape.
Alternatively, the deformable material may be at least substantially
incompressible
The piston may comprise an enclosed space communicating widr the deformabte
container, the
enclosed space having a variable volume. The volume may be varied by an
operator, and it may
comprise a spring-biased piston.
Yet another technology is one , wherein the first cross-sectional shape is
different from the
second cross-sectional shape, the change in cross-sectional shape of the
chamber being at least
substantially continuous between the first and second longitudinal positions.
In that situation, the first cross-sectional area may be at least 5%,
preferably at least 10%, such
as at teas 20%, preferably at least 30%, such as at least 40%, preferably at
least 50%, such as at least
60%, preferably at least 70%, such as at least 80, such as at least 90% larger
than the second cross-
sectional area.
- Also, the first moss-sectional shape may be at least substantially circular
and wherein the
second cross-sectional shape is elongate, such as oval, having a first
dimension being at least 2, such as
at least 3, preferably at least 4 times a dimension at an angle to the first
dimension.
In addition, the first cross-sectional shape may be at least substantially
circular and wherein the
second cross-sectional shape comprises two or more at least substantially
elongate, such as lobe-shaped,
parts.
Also, in the cross-section at the first longitudinal position, a first
circumference of the chamber
may be 80-120%, such as 85-115%, preferably 90-110, such as 95-IOS, preferably
98-102% of a
second circumference of the chamber in the cross-section at the second
longitudinal direction.
Preferably, the first and second circumferences are at least substantially
identical.
An optional or additipnal techno]oey is n e whe* " tt+e_;' r n n poises;
an elastically deformable material being adapted to adapt itself to the moss-
section of the
chamber When moving from the first to the second longitudinal position of the
chamber, and
- a coiled flat spring having a central axis at least substantially along the
longitudinal axis, the spring
being positioned adjacently to the elastically deformable material so as to
support the elastically
deformable material in the longitudinal direction.
In that situation, the piston may further comprise a number of flat supporting
means positioned
between the elastically deformable material and the spring, the supporting
means being rotatable along
an interface between the spring and the elastically deformable material.
The supporting means may be adapted to rotate from a first position to a
second position
where, in the first position. an outer boundary thereof may be comprised
within the first cross-sectional
area and where, in. the second position, an outer boundary thereof may be
comprised within the second
cross-sectional area.
In a second aspect, the invention relates to a combination of a piston and a
chamber, wherein:
the chamber defines an elongate chamber having a longitudinal axis,
the chamber having, at a first longitudinal position thereof, a first cross-
sectional area thereof
and, at a second longitudinal position thereof, a second cross-sectional area,
the first cross-sectional area
being larger than the second cross-sectional area, the change in cross-section
of the chamber being at
least substantially continuous between the first and second longitudinal
positions,
the piston being adapted to adapt itself to the cross-section of the chamber
when moving from the first to
the second longitudinal position of the chamber,
the piston comprising: -
- CA 02786315 2012-08-24
a plurality of at least substantially stiff support members rotatably fastened
to a commas
membt
elastically deformable means, supported by the supporting members, for sealing
against an
inner wall of the chamber
the support members being rotatable between 10 and 400 relative to the
longimdinal axis.
Preferably, the support members are rotatable so as to be at least
approximately parallel to the
longitudinal axis.
Thus, the manner in which the piston is able to adapt to different areas
and/or shapes is one
wherein the piston comprises e number of rotatably fastened means holding a
sealing means. One
preferred embodiment is one wherein the piston has the overall shape of an
umbrella.
Preferably, the consort member is attached to a handle For use by an operator,
such as when
the combination is used as a pump, and wherein the support members extend, in
the chamber, in a
direction relatively away from the handle. This has the advantage that
increasing the pressure by forcing
the handle into the chamber, will simply force the supporting means and the
sealing creams against the
wall of the chamber - thus increasing the sealing
In order to ensure sealing also after a stroke, the combination preferably
comprises means for
biasing the support members against an inner wall of the chamber.
In a third aspect, the invention relates to a combination of a piston and a
chamber, wherein:
the chamber defines an elongate chamber having a longitudinal axis,
- the chamber having, at a first longitudinal position thereof, a first cross-
sectional area [hereof
and, at a second longitudinal position thereof, a second cross-sectional area,
the tits[ cross-sectional area
being larger than the second cross-sectional area, the change in cross-section
of the chamber being at
least substantially continuous between the first and second longitudinal
positions,
CA 02786315 2012-08-24
the piston being adapted to adapt itself to the cross-section of the chamber
when moving from the first to
...the second longitudinal position of [he chamber
the piston comprising an elastically deformable container comprising a
deformable material-
That, by providing an elastically deformable container, changes in area and/or
shape may be
provided. Naturally, this container should be sufficiently fastened to the
piston in order for it to follow
the remainder of the piston when The piston is moved in the chamber.
The deformable material may be a fluid or a mixture of fluids, such as water,
steam, and/or
gas, or foam. This material, or a part thereof, may be compressible, such as
gas or a mixture of water
and gas, or it may be at least substantially incompressible.
When the cross-sectional area changes, the volume of the container may change.
Thus, in a
cross-section through the longimdinal direction, the container may have a
first shape at the first
longitudinal direction and a second shape at the second longitudinal
direction, the first shape being
different from the second shape. In our situation, at least part of the
deformable material is compressible
and the first shape has an area being larger than an area of the second shape.
In that simation, the overall
volume of the container changes, whereby the fluid should be compressible.
Alternatively or optionally,
piston may comprise a second enclosed space communicating with the deformable
container, the
enclosed space having a variable volume. In that manner, that enclosed space
may take up fluid when
the deformable container changes volume- The volume of the second container
may be varied by an
operator. In that manner, the overall pressure or maximum/minimum pressure of
the container may be
altered. Also, the second enclosed space may comprise a spring-biased piston.
It may he preferred to provide means for defining the voume of the enclosed
space so that a
pressure of fluid in the enclosed space relates to a pressure of fluid between
the piston and the second
longitudinal position of the container. In this manner, the pressure of The
deformable container may be
varied in order to obtain a suitable scaling.
A simple manner would he to have the defining means adapted to define the
pressure in the
enclosed space at least substantially identical to the pressure between the
piston and the second
CA 02786315 2012-08-24
CA 02786315 2012-08-24
longitudinal position of the.container. In this situation, a simple piston
between the two pressures may be
piwvided(inouleue-notloose-uypafthr_ luid ; a th defnnnable-centainer)
In fact, the use of this piston may define any relation between the pressures
in that the enclosed
space in which the piston translates may taper in the same manner as the main
chamber or the
combination.
In order to withstand both the friction against the chamber wall and the
shape/dimension
changes, the container may comprise an elastically deformable material
comprising enforcement means,
such as a fibre enforcement.
In order to achieve and maintain a appropriate seating between the container
and the chamber
wall, it is preferred that an internal pressure, such as a pressure generated
by a fluid in the conutiner, is
higher than the highest pressure of the surrounding atmosphere during
translation of the piston from the
first longitudinal position to the second longitudinal position or vice versa.
In yet another aspect, the invention relates to a combination of a piston and
a chamber,
wherein:
the chamber defines an elongate chamber having a Iongimdinal axis,
the chamber having, at a first longitudinal position thereof, a first cuss-
sectional shape and
area thereof and, at a second longitudinal position thereof, a second cross-
sectional shape and area, the
first cross-sectional shape being different from the second cross-sectional
shape, the change in cross-
sectional shape of the chamber being at least substantially continuous between
the first and second
longitudinal positions,
- the piston being adapted to adapt itself to the cross-section of the chamber
when. moving from
the first to the second longitudinal position of the chamber.
This very interesting aspect is based on the fact that different shapes of
e.g. a geometrical figure have
varying relations between the circumference and the area thereof- Also,
changing between two shapes
may take place in a continuous manner so that the chamber may have one cross-
sectional shape at one
lnng+ adinal--pesihou-ihsasof--and-analhnc_at-a-second-Iongimdirtal-posiEiau -
whillo-maintaining-thn__
preferred smooth variations of the surface in the chamber.
In the present context, the shape of a cross-section is the overall shape
thereof - notwithstanding
the size thereof. Two circles have the same shape even though one has a
diameter different from that of
the other.
Preferably, the first cross-sectional area is at least 5%, preferably at least
10%, such as at least
20%, preferably at least 30%, such as at least 40%, preferably at least 50%,
such as at least 60%,
preferably at least 70%, such as at least 80, such as at least 90% larger than
the second cross-sectional
area. -
In a preferred embodiment. the first cross-sectional shape is at least
substantially circular and
wherein the second cross-sectional shape is elongate, such as oval, having a
fist dimension being at
least 2, web as at least 3, preferably at least 4 times a dimension at an
angle to the first dimension.
In another preferred embodiment, the first cross-sectional shape is at least
substantially circular
is and wherein the second cross-sectional shape comprises two or more at least
substantially elongate, such
as lobe-shaped, pans.
When, in the cross section at the first longimdinal position, a first
circumference of the
chamber is 80-120%, such as 85-115%, preferably 90-110. such as 95-105,
preferably 98-102% of a
second circumference of the chamber in the cross-section at the second
longitudinal direction, a number
of advantages are seen. Problems may arise when attempting to seal against a
wall having varying
dimensions due to the fact that the sealing material should both provide a
sufficient sealing and change
its dimensions. If, as is the situation in the preferred embodiment, the
circumference changes only to a
small degree, the sealing may be controlled more easily. Preferably, the first
and second circumferences
are at least substantially identical so that the sealing material is only bent
and not stretched to any _
significant degree.
Alternatively, the circumference may be desired to change slightly in that
when bending or
deforming a sealing material, e.g. a bending will cause one side thereof to be
compressed and another
stretched. Overall, it is desired to provide the desired shape with a
circumference at least close to that
which the sealing material would automatically "choose
CA 02786315 2012-08-24
CA 02786315 2012-08-24
One type of piston, which may be used in this type of combination, is the one
comprising:
a larality of at ]east substantially stiff sunnor[ members rRtatabN f steed m
member,
- elastically deformable means, supported by the supporting members, for
sealing against an
inner wall of the chamber.
Another type of piston is the one comprising an elastically deformable
container comprising a
deformable material.
to Another aspect of the invention relates to a combination of a piston and a
chamber, wherein:
the chamber defines en elongate chamber having a longitudinal axis,
- the chamber having, at a first longitudinal position thereof. a first cross-
sectional area thereof
and, at a second longitudinal position thereof, a second cross-sectional area,
the first cross-secrional area
being larger than the second cross-sectional area, the change in cross-section
of the chamber being at
least substantially conrimmus between the first and second longitudinal
positions, the piston comprising:
an elastically deformable material being adapted to adapt itself to the cross-
section of the
chamber when moving from the first to the second longitudinal position of the
chamber, and
- a coiled flat spring having a central axis' at least substantially along the
longitudinal axis, the spring
being positioned adjacently to the elastically deformable material so as to
support the elastically
deformable material in the longitudinal direction.
This embodiment solves the potential problem of merely providing a large mass
of a resilient
material as a piston. 'I he fact that the material is resilient will provide
the problem of deformation of the
piston and, if the pressure increases, lack of selling due to the resiliency
of the material. This is
especially a problem if the dimension changes required are large.
CA 02786315 2012-08-24
In the present aspect, the resilient material is supported by a helical flat
spring. A helical spring
is able to lie expanded a d com, eced ' rderln fnllnw lbcrareanLihe-chamber-.n
aile-thÃ-flat-strnnnart~
of the material of the spring will ensure that the spring is not deformed by
the pressure.
In order to e.g. increase the area of engagement between the spring and the
deformable
-5 material, the piston may further comprise a number of flat supporting means
positioned between the
elastically deformable material and the spring, the supporting means being
rotatable along an interface
between the spring and the elastically deformable material.
Preferably, the supporting means are adapted to rotate from a first position
to a second position
where, in the first position, an outer boundary thereof may be comprised
within the first cross-sectional
area and where, in the second position, an outer boundary thereof may be
comprised within the second
cross-sectional area -
Another aspect of the invention is one relating to a combination of a piston
and a chamber,
wherein:
the chamber defines no elongate chamber having a longitudinal axis.
- the piston being movable in the chamber fi-om a fast longitudinal position
to a second
longitudinal position, - -
- the chamber having an elastically deformable inner wall along at least part
of the inner chamber
.all between the first and second longitudinal positions,
- the chamber having, at a first longitudinal position thereof when the piston
is positioned at that
position, a first cross-sectional area thereof and, at a second longitudinal
position thereof when the
piston is positioned at that position, a second cross-sectional area, the
first cross-sectional area being
larger than the second cross-sectional area, the change in cross-section of
the chamber being at least
substantially continuous between the first and second longitudinal positions
when the piston is moved
between the first and second longitudinal positions.
1O
CA 0278631522012-08-24
iY1 '~/ G~f bGO J l t"'
Thus alternatively to the combinations where the isg, tad adapts lolhe- - -ono
changemof-
the chamber, this aspect relates to a chamber having adapting capabilities.
Naturally, the piston may bemade of an at least substantially incompressible
material - or a
combination may be made of the adapting chamber and an adapting piston - such
as a piston according
to the above aspects.
Preferably, the piston has, in it cross section along the longitudinal axis, a
shape tapering in a
direction from to the second longitudinal positions.
A preferred manner of providing an adapting chamber is to have the chamber
comprise:
- an enter supporting s[rucmre enclosing the inner wall and
a fluid held by a space defined by the outer supporting structure and the
inner wall.
In that manner, the choice of fluid or a combination of fluids may help
defining the properties of the
chamber, such as the sealing between the wall and the piston as well as the
force required etc.
It is clear that depending on from where the combination is seer, on of the
piston and the
chamber may be stationary and the other moving - or both may be moving. This
has no impact on the
function of the combination.
Naturally, the present combination may be used for a -,.be, of purposes in
that it primarily
focuses on a novel manner of providing an additional manner of tailoring
translation of a piston to the
fume required/taken up. In fact, the area/shape of the cross-section may be
varied along the length of
the chamber in order to adapt the combination for specific purposes and/or
forces. One purpose is to
provide a pump for use by women or teenagers - a pump that nevertheless should
be able to provide a
certain pressure. In that situation, an ergonomically improved pump may be
required by determining the
force which the person may provide at which position of the piston - and
thereby provide a chamber
with a suitable cross-sectional area/shape-
Another use of the combination would be for a shock absorber where die
area/shape would
determine what translation a certain shock (force) would require. Also, an
actuator may be provided
CA 02786315 2012-08-24
where the amount of fluid introduced into the chamber will provide differing
translation of the piston
depending_onlheactuaLpositioncothe-piston-pxior4o. he-iuwoducing.nf- he-guid.
In fact, the nature of the piston, the relative positions of the first and-the
second longitudinal
- positions and the arrangement of any valves connected to the chamber may
provide pumps, motors,
actuators, shock absorbers etc. with different pressure characteristics and
different force characteristics.
If the piston pump is a handpump for tire inflation purposes it can have an
integrated connector
according to those disclosed in PCTIDK96100055 (including the US Continuation
in Part of 18 April
1997), PCTIDK97/00223 and/or PCT/DK98/e0507. The connectors can have an
integrated pressure
gauge of any type. In a piston pump according to the invention used as e.g. a
floor pump or 'caipump'
to far inflation purposes a pressure gauge arrangement can be integrated in
this pump.
Certain piston types as e.g. those of Fig. 4A-F, 7A-E,71, 12A-C may he
combined with any
type of chamber.
The combination of certain mechanical pistons as e.g. the one shown in Fig. 3A-
C, and
and of certain composite pistons as e.g. the one shown in Pig 6D-F and
chambers having a constant
circumferical length of the convex type as e.g. the one shown in Fig. 7L may
be a good combination.
The combination of composite pistons as e.g. those shown in Fig. 9-12 may he
used well with
chambers of a convex type, irrespective of a possible change in the
circumferical length.
Pistons of the 'embrella type' shown in this application have their open side
at the side where
the pressure of the medium in the chamber is loading the 'embrella' at the
open side. It may also very
well possible that the 'embrella' is working upside down.
The inflatable pistons with a skin with a fiber architecture which has been
shown have an
overpressure in the piston in relation to the pressure in the chamber. It is
however also possible to have
an equal or lower pressure in the piston than in the chamber - the fibers are
than under pressure instead
of under tension. The resulting shape may be different than those which are
shown in the drawings. In
that case, any loading regulating means may have to be tuned differently, and
the fibers may have to be
supported. The load regulating means showed in e.g. Fig. 9D or 12B may then be
constructed so that
the movement of the piston of the means gives a suction in the piston, e.g. by
an elongation of the piston
rod, so that the pistons are now at the other side of the holes in the piston
rod. The change in the form
of the piston is than different and a collaps may be obtained- This may reduce
the life-time.
z~s
Through these embodiments, reliable and inexpensive pumps optimized for manual
operation,
vg: usuvezsal w -pumpsto-be-ep atÃd-by-women-and-tÃenagers; Ean-be-ebtiined-
The-shapoftbe--
walls of the pressurerizing chamber Qongitudinal and/or transversal cross-
section) and/or piston means
of the pumps shown are examples and may be changed depending on the pump
design specification. The
invention can also be used with all kinds of pumps, e.g. multiple-stage piston
pumps as well as with
dual-function pumps, piston pumps driven by a motor, pumps where e.g. only the
chamber or piston is
moving as well as types where both the chamber and the piston are moving
simultaneously. Any kind of
medium may be pumped in the piston pumps. Those pumps may be used for all
kinds of applications,
e.g. in pneumatic and/or hydraulic applications. And, the invention is also
applicable for pumps which
are not manually operated. The reduction of the applied force means a
substantial reduction of
investments for equipment and a substantial reduction of energy during
operation. The chambers may be
produced e.g, by injection moulding, from taper swaged tubes etc.
Ina piston pump a medium is suued into a chamber which may thereafter be
closed by a valve
arrangement. The medium is compressed by the movement of the chamber and/or
the piston and a -1-
may release this compressed medium from the chamber- In an actuator a medium
may be pressed into a
chamber through a valve arrangement and the piston and/or the chamber is
moving, initiating the
movement of an attached devise. In shock absorbers the chamber may be
completely closed, wherein the
chamber a compressable medium can be compressed by the movement of the chamber
and/or the piston.
In the case of a non-compressable medium is inside the chamber, e.g. the
piston may be equiped with
several small channels which give a dynamic friction, so that the movement is
slowed down.
Further, the invention can also be used in propulsion applications where a
medium may be used
to move a piston and/or a chamber, which can turn around an axis as e.g. in a
motor. The above
combinations are applicable on all above mentioned applications-
Thus, the invention also relates to a pump for pumping a fluid, the pump
comprising:
a combination according to any of the above aspects,
means for engaging the piston from a position outside the chamber,
a fluid entrance connected to the chamber and comprising a valve means, and -
a fluid exit connected to the chamber.
CA 02786315 2012-08-24
CA 02786315 2012-08-24
In orte.situatinn the~ngaging~eans~na}Lasean-outetposition_wtlere_[he_pisto~is-
in-itsfitst-
longitudinal position, and an inner position where the piston is in its second
longitudinal position. A
pump of this type is preferred when a pressurised fluid is desired-
In another situation, the engaging means may have an outer position where the
piston is in its
second longitudinal position, and an inner position where the piston is in its
first longitudinal position. A
pump of this type is preferred when no substantial pressure is desired but
merely transport of the fluid.
In. the situation where the pump is adapted for standing on the floor and the
piston/engaging
means to.compress fluid, such as air, by being forced downwards, the largest
force may, ergonomically,
be provided at the lowest position of the piston/engaging means/handle. Thus,
in the first situation, this
.,,as that the highest pressure is provided there- In the second situation,
this merely means that the
largest area and thereby the largest volume is seen at the lowest position-
However, due to the fact that a
pressure exceeding that in the e.g_ tyre is required in order to open the
valve of the tyre, the smallest
cross-sectional area may be desired shortly before the lowest position of the
engaging means in order for
is the resulting pressure to open the valve and a larger cross-sectional area
to. force more fluid into the tyre
(See Fig. 2B).
Also, the invention relates to a shock absorber comprising;
- a combination according to any of the combination aspects,
means for engaging the piston from a position outside the chamber, wherein the
engaging
means have an outer position where the piston is in its first longitudinal
position, and an inner position
where the piston is in its second longitudinal position.
The absorber may further comprise a fluid entrance connected to the chamber
and comprising a
valve means.
Also, the. absorber may comprise a fluid exit connected to the chamber and
comprising a valve
means.
1o7
.It may be preferred that the chamber and the piston forms an at least
substantially sealed cavity
.comprising a fluid, the fluid being compressed when the piston moves from the
first to the second
longitudinal positions- -
Normally, the absorber would comprise means for biasing the piston toward the
first
longitudinal position.
Finally, the. invention also relates to an actuator comprising:
a combination according to any of the combination aspects,
means for engaging the piston from a position outside the chamber, -
to - means for introducing fluid into the chamber in order to displace the
piston between the first
and the second longitudinal positions.
The actuator may comprise a fluid entrance connected to the chamber and
comprising a valve
means.
1 S Also, a fluid exit connected to the chamber and comprising a valve means
may be provided.
Additionally, the actuator may comprise means for biasing the piston toward
the first or second
longitudinal position.
CA 02786315 2012-08-24
l B
The various embodiments described above ate provided by way of illustration
only and should not be
construed to limit the invention. Those skilled in the art will
readilyr.coenize Various modafipations,_
changes, and combinations of elements which may be made to the present
invention without strictly
-following the exemplary embodiments and applications illustrated and
described herein, and without
- departing from the than spirit and scope of the present invention.
All piston types, specifically those which are containers wilts an elastically
deformable wall
may be sealingly connected to the chamber wall during it move between
]ongimdinal positions
engagingly connected or not connected to the wall of the chamber. Or may be
engagingly and sealingly
connected- to the chamber wall. Additionally may there be no engaging between
said walls either,
possibly touching the walls each other, and this may happen e.g. in the
situation where the container is
moving from a first to a second longitudinal position in a chamber
The type. of connection (sealingly and/or engagingly and/or touching and/or no
connection) between said
walls may be accomplished by using the correct inside pressure inside said
container wall: high pressure
for sealingly connection, a lower pressure for engagingly connection and e.g.
atmospheric pressure for
no connection (production sized container) - thus, a container with an
enclosed space may be preferred,
because the enclosed space may be controlling the pressure inside the
container from a position outside
the piston.
Another option for an engagingly connection is don wall of the container,
which may have
reinforcements which are sticking out of the surface of said will, so that
leaking may happen between
the wall of container and the wall of the chamber.
19 09 B DESCRIP IO OF THE D GS
In e but Owing, referre embed* sass of the invention ill be necri; i erme to
the
dra iu wherein:
CA 02786315 2012-08-24
leg
sa- J
CA 02786315 2012-08-24
207 SPECIFICALLY PREFERRED EMBODIMENTS
According to an embodiment of the invention, there is provided a combination
of a
piston and a chamber, wherein: the chamber defines an elongate chamber having
a
longitudinal axis, the chamber having, at a first longitudinal position
thereof, a first
cross-sectional area thereof and, at a second longitudinal position thereof, a
second
cross-sectional area, the second cross-sectional area being 95% or less of the
first
cross-sectional area, the change in cross-section of the chamber being at
least
substantially continuous between the first and second longitudinal positions,
the
piston being adapted to adapt itself to the cross-section of the chamber when
moving
to from the first to the second longitudinal position of the chamber.
Preferably the second cross-secti onal area is between 95% and 15% of the
first cross-
sectional area.
Preferably, the second cross-sectional area is 95-70% of the first cross-
sectional area.
Preferably, the second cross-sectional area is approximately 50% of the first
cross-
sectional area.
Preferably the piston comprises: a plurality of at least substantially stiff
support
members rototably fastened to a common member, elastically deformable means,
supported by the supporting members, for sealing against an inner wall of the
chamber the support members being rotatable between Ioo and 40o relative to
the
longitudinal axis.
According to an embodiment of the invention there is also provided a
combination
where the support members arc rotatable so as to be at least approximately
parallel to
the longitudinal axis.
Preferably the common member is attached to a handle for use by an operator,
wherein the support members extend, in the chamber, in a direction relatively
away
from the handle.
Preferably the combination further comprises means for biasing the support
r 2 y ~ 10
CA 02786315 2012-08-24
members against an inner wall of the chamber.
Preferably the piston comprises an elastically deformable canlainer comprising
a
deformable material.
Preferably the deformable material is a fluid or a mixture of fluids, such as
water, steam, and/or gas, or a foam.
Preferably, in a cross-section through the longitudinal direction, Use
container has a
l0 first shape at the first longitudinal direction and a second shape at the
second
longitudinal direction, the first shape being different from the second shape.
Preferably at least part of the deformable material is compressible and
wherein the
first shape has an area being larger than an area of the second shape.
Preferably the deformable material is at least substantially incompressible.
Preferably the piston comprises a chamber communicating with the deformable
container, the chamber having a variable volume.
Preferably the volume may be varied by an operator.
Preferably the chamber comprises a spring-biased piston.
Preferably the combination further comprises means for defining the volume of
the
chamber so that a pressure of fluid in the chamber relates to a pressure of
fluid
between the piston and the second longitudinal position of the container.
Preferably the defining means are adapted to define the pressure in the
chamber at
least substantially identical to the pressure between the piston and the
second
longitudinal position of the container.
Preferably the first cross-sectional shape is different from the second cross-
sectional
shape, the change in cross-sectional shape of the chamber being at least
substantially
CA 02786315 2012-08-24
continuous between the first and second longitudinal positions.
Preferably the first cross-sectional area is at least 5%, preferably at least
10%, such
as at least 20%, preferably at least 30%, such as at least 40%, preferably at
least
50%, such as at least 60%, preferably at least 70%, such as at least 80%, such
as at
least 90% larger than the second crass-sectional area.
Preferably the first cross-sectional shape is at least substantially circular
and wherein
the second cross-sectional shape is elongate, such as oval, having a first
dimension
to being at least 2, such as at least 3, preferably at least 4times a
dimension at an angle
to the first dimension.
Preferably the first cross-sectional shape is at least substantially circular
and wherein
the second cross-sectional shape comprises two or more at least substantially
elongate, such as lobe-shaped, parts.
Preferably, in the cross-section at the first longitudinal position, a first
circumference
of the chamber is 80-120%, such as 85-115%, preferably 90-110, such as 95-105,
preferably 98-102% of a second circumference of the chamber in the cross-
section at
the second longitudinal direction.
Preferably the first and second circumferences are at least substantially
identical.
Preferably the piston comprises: an elastically deformable material being
adapted to
adapt itself to the cross-section of the chamber when moving from the first to
the
second longitudinal position of the chamber, and a coiled flat spring having a
central
axis at least substantially along the longitudinal axis, the spring being
positioned
adjacently to the elastically deformable material so as to support the
elastically
deformable material in the longitudinal direction.
Preferably the piston further comprises a number of flat supporting means
positioned
between the elastically deformable material and the spring, the supporting
means
being rotatable along an interface between the spring and the elastically
deformable
material.
sg- 21112,
Preferably the supporting means are adapted to rotate from a first position to
a
second position where, in the first position, an outer boundary thereof may be
comprised within the first cross-sectional area and where, in the second
position, an
outer boundary thereof may be comprised within the second cross-sectional
area.
According to an embodiment of the invention, there is provided a combination
of a
piston and a chamber, wherein: the chamber defines an elongate chamber having
a
longitudinal axis, the chamber having, at a first longitudinal position
thereof, a first
cross-sectional area thereof and, at a second longitudinal position thereof, a
second
cross-sectional area, the first cross-sectional area being larger than the
second cross-
sectional area, the change in cross-section of the chamber being at least
substantially
continuous between the first and second longitudinal positions, the piston
being
adapted to adapt itself to the cross-section of the chamber when moving from
the
first to the second longitudinal position of the chamber, the piston
comprising: a
plurality of at least substantially stiff support members rotatably fastened
to a
common member, elastically deformable means, supported by the supporting
members, for sealing against an inner well of the chamber the support members
being rotatable between 10` and 40 relative to the longitudinal axis.
According to an embodiment, there is provided a combination where the support
members are rotatable so as to be at least approximately parallel to the
longitudinal
axis.
Preferably the common member is attached to a handle for use by an operator,
and
wherein the support members extend, in the chamber, in a direction relatively
away
from the handle.
Preferably, the combination further comprises means for biasing the support
members against an inner wall of the chamber A combination of a piston and a
chamber, wherein: the chamber defines an elongate ehanrber having a
longitudinal
axis, the chamber having, at a first longitudinal position thereof, a fast
cross-
sectional area thereof and, at a second longitudinal position thereof, a
second cross-
sectional area, the first cross-sectional area being larger than the second
cross-
CA 02786315 2012-08-24
2 ~1 2 ! 13
CA 02786315 2012-08-24
sectional area, the change in cross-section of the chamber being at least
substantially
continuous between the first and second longitudinal positions, the piston
being
adapted to adapt itself to the cross-section of the chamber when moving from
the
first to the second longitudinal position of the chamber the piston comprising
an
elastically deformable container comprising a deformablc material.
Preferably the deformable material is a fluid or a mixture of fluids, such as
water,
steam, and/or gas, or a foam.
to Preferably, in a crass-section through the longitudinal direction, the
container has a
first shape at the first longitudinal direction and a second shape at the
second
longitudinal direction, the first shape being different from the second shape.
Preferably at least part of the deformable material is compressible and
wherein the
first shape has an area being larger than an area of the second shape_
Preferably the deformable material is at least substantially incompressible.
Preferably the piston comprises a chamber communicating with the deformable
container, the chamber having a variable volume.
Preferably the volume may be varied by an operator.
Preferably the chamber comprises a spring-biased piston.
Preferably, the combination further comprises means for defining the volume of
the
chamber so that a pressure of fluid in the chamber relates to a pressure of
fluid
between the piston and the second longitudinal position of the container
Preferably the defining means are adapted to define the pressure in the
chamber at
least substantially identical to the pressure between the piston and the
second
longitudinal position of the container.
Preferably the container comprises an elastically deformable material
comprising
CA 02786315 2012-08-24
enforcement means.
Preferably the enforcement means comprise fibres.
Preferably the foam or fluid is adapted to provide, within the container, a
pressure
higher than the highest pressure of the surrounding atmosphere during
translation of
the piston from the first longitudinal position to the second longitudinal
position or
vice versa.
Preferably, the chamber defines an elongate chamber having a longitudinal
axis, the
chamber having, at a first longitudinal position thereof, a first cross-
sectional shape
and area thereof and, at a second longitudinal position thereof, a second
cross-
sectional shape and area, the first cross-sectional shape being different from
the
second cross-sectional shape, the change in cross-sectional shape of the
chamber
being at least substantially continuous between the first and second
longitudinal
positions, the piston being adapted to adapt itself to the cross-section of
the chamber
when moving from the first to the second longitudinal position of the chamber.
Preferably the first cross-sectional area is at least 5%, preferably at least
10%, such
as at least 20%, preferably at least 30%, such as at least 40%, preferably at
least
50%, such as at least 60%, preferably at least 70%, such as at least 80, such
as at
least 90% larger than the second cross-sectional area.
Preferably the first cross-sectional shape is at least substantially circular
and wherein
the second cross-sectional shape is elongate, such as oval, having a first
dimension
being at least 2, such as at least 3, preferably at least 4 times a dimension
at an angle
to the first dimension.
Preferably the first cross-sectional shape is at least substantially circular
and wherein
the second cross-sectional shape comprises two or more at least substantially
elongate, such as lobe-shaped, parts.
Preferably, in the cross-section at the first longitudinal position, a first
circumference
of the chamber is 80-120%, such as 85-115%, preferably 90-110, such as 95-105,
'- 2' (15
CA 02786315 2012-08-24
preferably 98? 102% of a second circumference of the chamber in the cross-
section at
the second longitudinal direction-
Preferably the first and second circumferences are at least substantially
identical.
Preferably the piston comprises: a plurality of at least substantially stiff
support
members rotatably fastened to a common member, elastically defonnable means,
supported by the supporting members, for sealing against an inner wall of the
chamber.
Preferably the piston comprises: an elastically deformable container
comprising
a deformabte material.
According to another embodiment of the invention, there is provided a
combination
of a piston and a chamber, wherein: the chamber defines an elongate chamber
having
a longitudinal axis, the chamber having, at a first longitudinal position
thereof, a first
cross-sectional area thereof and, at a second longitudinal position thereof, a
second
cross-sectional area, the first cross-sectional area being larger than the
second cross-
sectional area, the change in cross-section of the chamber being at least
substantially
continuous between the first and second longitudinal positions, the piston
comprising: an elastically defoemable material being adapted to adapt itself
to the
cross-section of the chamber when moving from the first to the second
longitudinal
position of the chamber, and - a coiled flat spring having a central axis at
least
substantially along the longitudinal axis, the spring being positioned
adjacently to the
elastically deformable material so as to support the elastically deformable
material in
the longitudinal direction.
Preferably the piston further comprises a number of flat supporting means
positioned
between the elastically deformable material and the spring, the supporting
means
being rotatable along an interface between the spring and the elastically
deformable
material.
Preferably the supporting means are adapted to rotate from a first position to
a
second position where, in the first position, an enter boundary thereof may be
CA 02786315 2012-08-24
comprised within the first cross-sectional area and where, in the second
position, an
outer boundary thereof may be comprised within the second cross-sectional
area.
According to an embodiment of the invention there is provided a combination of
a
piston and a chamber, wherein: the chamber defines an elongate chamber having
a
longitudinal axis, the piston being movable in the chamber from a first
longitudinal
position to a second longitudinal position, the chamber having an elastically
deformable inner wall along at least part of the timer chamber wall between
the fast
and second longitudinal positions, the chamber having, at a first longitudinal
position
thereof when the piston is positioned at that position, a first cross-
sectional area
thereof and, at a second longitudinal position thereof when the piston is
positioned at
that position, a second cross-sectional area, the first cross-sectional area
being larger
than the second cross-sectional area, the change in cross-section of the
chamber
being at least substantially continuous between the first and second
longitudinal
1,5 positions when the piston is moved between the first and second
longitudinal
positions.
Preferably the piston is made of an at least substantially incompressible
material.
Preferably the piston has, in a cross section along the longitudinal axis, a
shape
tapering in a direction from to the second longitudinal positions
Pwferahty the chamber comprises: an outer supporting structure enclosing the
inner
wall and a fluid held by a space defined by the outer supporting structure and
the
inner wall. -
According to an embodiment of the invention, there is provided a pmnp for
pumping
a fluid, the pump comprising: a combination according to any of the preceding
claims, means for engaging the piston from a position outside the chamber, a
fluid
entrance connected to the chamber and comprising a valve means, and a fluid
exit
connected to the chamber.
Preferably the engaging means have an outer position where the piston is in
its first
", 2-5~t I I T
CA 02786315 2012-08-24
longitudinal position, and an inner position where-the piston is in its second
longitudinal position.
Preferably the engaging means have an outer position where the piston is in
its
second longitudinal position, and an inner position where the piston is in its
first
longitudinal position.
According to an embodiment of the invention, there is provided a shock
absorber
comprising: a combination as described above, means for engaging the piston
from a
position outside the chamber, wherein the engaging means have an outer
position
where the piston is in its first longitudinal position, and an inner position
where the
piston is in its second longitudinal position.
Preferably the shock absorber further comprises a fluid entrance connected to
the
is chamber and comprising a valve means.
Preferably the shock absorber further comprises a fluid exit connected to the
chamber and comprising a valve means.
Preferably the chamber and the piston firms an at least substantially sealed
cavity
comprising a fluid, the fluid being compressed when the piston moves from the
first
to the second longitudinal positions.
Preferably the shock absorber further comprises means for biasing the piston
toward
the first longitudinal position.
According to an embodiment of the invention there is also provided an actuator
comprising: a combination as described above, means for engaging the piston
from a
position outside the chamber, means for introducing fluid into the chamber in
order
to displace the piston between the first and the second longitudinal
positions.
Preferably the actuator further comprises a fluid entrance connected to the
chamber
and comprising a valve means.
CA 02786315 2012-08-24
Preferably the actuator farther comprises a fluid exit connected to the-
chamber and
comprising a valve means.
Preferably the actuator farther comprises means for biasing the piston toward
the
first or second longitudinal position.
Preferably the introducing means comprise means for introducing pressurised
fluid
into the chamber.
Preferably the introducing means are adapted to introduce a combustible fluid,
such
as gasoline or diesel, into the chamber, and wherein the actuator further
comprises
means for combusting the combustible fluid.
Preferably the actuator according further comprises a crank adapted to
translate the
is translation of the piston into a rotation of the crank
CA 02786315 2012-08-24
~- tl 1
.S hOd,-oa- - 1+~~- - I Spec.', r 2sz) 0fhsL .e,,,, boal,.^n..<,,M
I~cc,oecc,tr. hn c.,, za, 6DOC;n,.e.~F d. YJws,'S P---A
.1: A piston-chamber combination comprising an elongate chamber
5(70) which is bounded by an inner chamber wall (71,73,75) and
comprising a piston means (7(5,76',163) in said chamber, the
piston means comprising sealing means to be sealingly movable
relative to said chamber at least between first and second
longitudinal positions of said chamber, said chamber having
10cross-sections of different cross-sectional areas at the first
and second longitudinal positions of said chamber and at least
substantialy continuously differing cross-sectional areas at
intermediate longitudinal positions between the first and
second longitudinal positions thereof, the cross-sectional area
15at the first longitudinal position being larger than the cross-
sectional area at the second longitudinal position, said piston
means being designed to adapt itself and said sealing means to
said different cross-sectional areas of said chamber during the
relative movements of said piston means from the first
201ongitudinal position through said intermediate longitudinal
positions to the second longitudinal position of said chamber,
W.,n
ebaaar* the cross-sections of the different
cross-sectional areas have different cross-sectional shapes,
the change in cross-sectional shape of the chamber (162) being
25continuous between the first and second longitudinal positions
of the chamber (162), wherein the piston means (163) is further
designed to adapt itself and the sealing means to the different
cross-sectional shapes, and wherein a first circumferential
length of the cross-sectional shape of the chamber (162) at the
30first longitudinal position thereof amounts to 80-1200 of a
second circumferential length of the cross-sectional shape of
the chamber (162) at the second longitudinal position thereof.
120
CA 02786315 2012-08-24
A-eenabina din the cross-
sectional shape of the chamber (162) at the first longitudinal
position thereof is at least substantially circular and wherein
the cross-sectional shape of the chamber (162) at the second
5longitudinal position thereof is elongate, such as oval, having
a first dimension being at least 2, such as at least 3,
preferably at least 4 times a dimension at an angle to the
first dimension.
rU'v-z`W7 15
10X. F.-eamb'na-t ~,on-a d' o to clai 1 0 2 h the cross-
sectional shape of the chamber (162) at the first longitudinal
position thereof is at least substantially circular and wherein
the cross-sectional shape of the chamber (162) at the second
longitudinal position thereof comprises two or more at least
15substantially elongate, such as lobe-shaped, parts.
__ _ _ ___iu .,tee-n a
first circumferential length of the cross-sectional shape of
the cylinder (162) at the first longitudinal position thereof
20amounts to 85-115%, preferably 90-110, such as 95-105,
preferably 98-102%, of a second circumferential length of the
cross-sectional shape of the chamber (162) at the second
longitudinal position thereof.
Plt eiah1`l 113
255..5 eemb n~tiae arc 3,_,e n the first and
second circumferential lengths are at least substantially
identical.
I~'1y,10.bL~ .'~
6-. ae-,irg Ty..- the
30cross-sectional area of said chamber at the second longitudinal
position thereof is 95% or less of the cross-sectional area of
said chamber (162)at the first longitudinal position thereof.
PzI~ f201
CA 02786315 2012-08-24
^ the cross-
sectional area of said chamber (162) at the second longitudinal
position thereof is between 95% and 15% of the cross-sectional
area of said chamber (162)at the first longitudinal position
5thereof.
~Za ~p tnhly '_1 _^ =-. _.- the cross-
sectional area of said chamber (162) at the second longitudinal
position thereof is 95-70% of the cross-sectional area of said
l0chamber (162) at the first longitudinal position thereof.
Pu~z~bl~ rs
the cross-
sectional area of said chamber (162) at the second longitudinal
position thereof is approximately 500 of the cross-sectional
15area of said chamber (162) at the first longitudinal position
thereof.
CCs7a mj to ah to b,OlL..e,,~ sQ Yl~ Ih~:c~~,"e-~, Ylc3n i7 c(gv pi5Ve¾
10-. A pump for pumping a fluid, the pump comprising:
a combination according to any of the preceding claims,
20 means for engaging the piston means (76, 163) from a
position outside the chamber (162),
a fluid entrance connected to the chamber and comprising a
valve means, and a fluid exit connected to the chamber
(162).
25 Pte.b l,a~
1 . 2--psmp--meeorel4-sg-%w c-.~ai n n the engaging means
have an outer position where the piston means (76, 163) is at
the first longitudinal position of the chamber, and an inner
position where the piston means (76, 163) is at the second
30longitudinal position of the chamber (162).
^ the engaging means
have an outer position where the piston means (76, 163) is at
the second longitudinal position of the chamber, and an inner
X22
CA 02786315 2012-08-24
position where the piston means is at the first longitudinal
position of the chamber (162).
ICJ "CO z54-, 2- ew. k' s4 ~j-% ;w~~f~'en 7 ,p
.2.3-. A shoe absorber comprising:
a combination according to any of claims 1 to 9,
means for engaging the piston means (76, 163) from a
position outside the chamber, wherein the engaging means have
an outer position where the piston means is at the first
longitudinal position of the chamber (162), and an inner
10position where the piston means is at the second longitudinal
position.
~/~zab~J ~-- 89~c~cdihsibe.~ l/h'~~~
r-bcr ecc ding to ci further comprising
a fluid entrance connected to the chamber (162) and comprising
15a valve means.
ft
pv~ ~h a Gr oC c f r 3A, J G kr , $
75_ "- - - --- -~A further
comprising a fluid exit connected to the chamber (162) and
comprising a valve means.
16. A n k h her a-to-aliy oiaZms
^'hema. the chamber (162) and the piston means (76, 163) form
an at least substantially sealed cavity comprising a fluid, the
fluid being compressed when the piston means moves from the
25first to the second longitudinal positions of the chamber
(162).
37-_0. sho t~ h h ri' y -h&
further comprising means for biasing the piston means toward
30the first longitudinal position of the chamber.
0 C"r r<. ~ ati r e of ~2< iaks ~a N1~ a ~w Z
An actuator comprising:
a combination according to any of claims 1 to 9,
X23
CA 02786315 2012-08-24
means for engaging the piston means from a position
outside the chamber (162),
means for introducing fluid into the chamber (162) in
order to displace the piston means (76, 163) between the first
Sand the second longitudinal positions of the chamber.
-t.~hYaAc 7.S~6FJ Z^z~~
1-9- l'-actuator further comprising a
fluid entrance connected to the chamber (162) and comprising a
valve means.
26: An actuator, ~.....-.o then comprising
a fluid exit connected to the chamber and comprising a valve
means.
' b _~ti..~c <~7
13211. tuat oFr w'~J rther
comprising means for biasing the piston means (76, 163) toward
the first or second longitudinal position of the chamber.
22". n actuator ac d' to any at--cna=ai wherein
20the introducing means comprise means for introducing
pressurised fluid into the chamber (162).
23-. n actuator wherein the
introducing means are adapted to introduce a combustible fluid,
25such as gasoline or diesel, into the chamber (162), and wherein
the actuator further comprises means for combusting the
combustible fluid.
-qr ,a'j< L,4..21,S
24: An actuator e~ as -tom=~ further
30comprising a crank adapted to translate the translation of the
piston means into a rotation of the crank.
653 SUMMARY OF THE INVENTION
In-the fast.tspeeE,-thesnvenFiozrrehtesto-a-tombuntion-ofa . m er, w erem:
the container is made to be elastically expacetable and to barer its
circampherical length in the
stressttee and undeformed state of its production size approximately the cirn
enpherential length of the
S inner chamber wail of the container at said second longitudinal position.
In the present context, the cross-sections are preferably taken
perpendicularly to the longitu-
dinal axis (= transversal direction).
Preferably, the second cross-sectional area is 98-5% , such as 95-70% of the
frost cross-
sectional area. In certain situations, the second cross-sectional area is
approximately S0% of the first
cross-sectional area.
CA 02786315 2012-08-24
A number of different technologies may be used in order to realise this
combination. These
technologies are described further in relation to the subsequent aspects of
the invention
One such technology is one wherein the piston comprises a container comprising
a deformable
material-
In that situation, the deformable material may be a fluid or a mixture of
fluids, such as water,
steam, and/or gas, or a foam- This material, or a part thereof, may be
compressible, such as gas or a
mixture of water and gas, or it may be at least substantially incompressible.
The deformable material may also be spring-fore operated devices, such as
springs-
Thus the container may he adjustable to provide sealing to the wall of the
chamber having different
cross .sectional area's and different circumpherential sizes.
This may be achieved by choosing the production size (stress free, undeformed)
of the piston
approximately equivalent to the cnumnl herencial length of the smallest cross-
sectional area of a cross-
section of the chamber, and to expand it when moving to a longitudinal
position with a bigger
circumpherential trngth and to contract it when moving in the apposite
direction.
And this may be achieved by providing means to keep a certain sealing force
from the piston on
The wall of the chamber: by keeping the internal pressure of the piston on (a)
certain predetermined
level(s), which may be kept constant during the stroke- A pressure lever of a
certain size depends on the
difference in circumpherential length of the cross sections, and on the
possibility to get a suitable sealing
at the cross section with the smallest circumpherential length. If the
difference is big, and the
appropriate pressure level too high to obtain a suitable sealing- force at the
smallest circumpherential
length, than change of the pressure may be arranged during the stroke. This
calls for a pressure
management of the piston. As commercially used materials are normally not
tight, specifically when
quite high pressures may be used, there must he a possibility to keep this
pressure, e.g. by using a valve
for inflation purposes. In the ease when spring-force operated devices are
being used to obtain the
pressure, a valve may not be necessary- -
CA 02786315 2012-08-24
12(7
When the cross-sectional area of the chamber changes, the volume of the
container may
change Thus in across-section through the longitudinal direction of the
chamber the rainec_ma -
have a first shape at the first longitudinal direction and a second shape at
the second longitudinal
direction, the first shape may be different from the second shape. In one
situation; at least part when the
deformable material is compressible and the first shape has an area being
larger than an area of the
second shape. In that situation, the overall volume of the container changes,
whereby the fluid should be
compressible. Alternatively or optionally, the piston may comprise an enclosed
space communicating
with the deformable container, said enclosed space having a variable volume.
In that manner, that the
enclosed space may take up or release fluid when the deformable container
changes volume. The change
of the volume of the container is by that automatically adjustable. It may
result in that the pressure in the
container remains constant during the stroke.
Also, the enclosed space may comprise a spring-biased piston. This spring may
define the
pressure in the piston. The volume of the enclosed space maybe varied. In that
manner, the overall
pressure or maximum/minimum pressure of the container may be altered.
When the enclosed space is updivided into a first and a second enclosed space,
the spaces
farther comprising means for defining the volume of the first enclosed space
so that the pressure of fluid
in the first enclosed space may relate to the pressure in the second enclosed
space. The last mentioned
space may be inflatable e.g. by means of a valve, preferably an inflation
valve, such as a Schrader
valve. A possible pressure drop in die container due to leakage e.g. through
the will of the container
may be balanced by inflation of the second enclosed space through the defining
means. The defining
means may be a pair of pistons, one in each enclosed space.
The defining means may be adapted to define the pressure in the first enclosed
space and in the
container at least substantially constant during the stroke. However, any kind
of pressure level in the
container may be defined by the defining means: e.g, a pressure raise may be
necessary when [he will
, - of the container expands when the piston moves to such a big cross-
sectional area at the fuss longitudinal
position that the contact area and/or contact pressure at the present pressure
value may become too little,
in order to maintain a suitable sealing. defining means may be a pair of
pistons, one in each enclosed
space. The second enclosed space may be inflated to a certain pressure level,
so [hat a pressure raise
may be communicated to the first enclosed space and the container, despite the
fact that the volume of
CA 02786315 2012-08-24
(2R
13-' kW 5~' 6-c
the container and thus the second enclosed space may become bigger as well
This may be achieved by
r g a nmh satin f a n~crn anr7 a rh hP (~hr c rn nL.: dosed-
pace}.watl~dzfemnt-sras muedenal--
area's in the piston rod. A pressure drop may also be designable-
Pressure management of the piston may also be achieved by relating the
pressure of fluid in the
enclosed space with the pressure of fluid in the chamber. By providing means
for defining the volume of
the enclosed space communicating with the chamber. In this manner, the
pressure of the deformable
container may be varied in order to obtain a suitable sealing. For example, a
simple manner would be to
have the defining means adapted to define the pressure in the enclosed space
to raise when the container
is moving from the second longitudinal position to the first longitudinal
position. In [his situaiion, a
simple piston between the two pressures may be provided (in order to not loose
any of the fluid in the
defoemable container).
In fact, the use of this piston may define any relation between the pressures
in that the chamber
in which the piston translates may taper in the same manner as the main
chamber of the combination.
A device which is transportable directly from the piston rod into the
container may also change
is the volume and/or the pressure in the container.
It may be possible that the piston does not have or communicate (closed
system) or does have
or 000teounicate with a valve for inflation When the piston does not have an
inflation valve, the fluid
may be non-permeable for the material of use wall of the container. A step in
the mounting process may
than be that the volume of the container is permanently closed, after having
put the fluid in the volume
of the piston, and after having been positioned at the second longitudinal
position of the chamber. The
obtainable velocity of the piston may depend on the possibility for a big
fluid flow without too much
1`611nn to and from the first closed chamber. When the piston does have an
inflation valve the wa11 of
the container may be permeable for the fluid.
The container may be inflated by a pressure source which is comprised in the
piston. Or an
external pressure source, like one outside the combination and/or when the
chamber is the source itself.
All solutions demand a valve communicating with the piston. This valve may
preferably an inflation
valve, best a Schrader valve or in general, a valve with a spring force
operated valve core. The Schrader -
CA 02786315 2012-08-24
tz3
valve has a spring biased valve core pin and closes independant of the
pressure in the piston, and all
.. kindg of fluids may flow throveh it T[ may h m alcahel7nnrt,Pr valve-
typereg. a-check_vaIv_.
The container may be inflated through an enclosed space where the spring-
biased tuning piston
operates as a check valve- The fluid. may flow through longitudinal ducts in
the bearing of the piston rod
of the spring biased piston, from a pressure source, e.g. an external pressure
source or e.g. an internal
pressure container.
When the enclosed space is divided up into a first and second enclosed space,
the inflation may
be done with the chamber as the pressure source, as the second enclosed space
may prohibit inflation
through it to the first enclosed space. The chamber may have an inlet valve in
the foot of the chamber.
For inflation of the container an inflation valve, e.g. a valve with a spring-
force operated valve core
such as a Schrader valve may be used, together with an actuator. This may be
an activating pin
according to WO 96/10903 or WO 97/43570, or a valve actuator according to
W099/26002 or US
5,094,263. The core pin of the valve is moving towards the chamber when
closing. The activating pins
from the above cited WO-docnrnents have the advantage that the force to open
the spring-force operated
valve core is so low, that inflation may be easily done by a manually operated
pump. The actuator cited
in the US-patent may need the force of a normal compressor.
When the working pressure in the chamber is higher than the pressure in the
piston, the piston
may be belled automxically.
When the working pressure in the chamber is lower than the pressure in the
piston than it is
necessary to obtain a higher pressure by e.g. temporary closing the outlet
valve in the foot of the
chamber. When the valve is e.g. a Schrader valve which may be opened by means
of a valve actuator
according to WO 99/26002, this may be achieved by creating a bypass in the
form of a channel by
connecting the chamber and the space between the valve aemator and the core
pin of the valve. This
bypass may be openened (the Schrader valve may remain closed) and closed (the
Schrader valve may
open) and may be accomplished by e.g. a movable piston. The movement of this
piston may be arranged
manually e.g by a pedal, which is fumingaround an axle by an operator-from an
inactive position to an
active position and vice versa- It may also be achieved by other means like an
actuator, initiated by the
result of a pressure measurement in the chamber and/or the container:
CA 02786315 2012-08-24
12~,
Obtaining the predetermined pressure in the container may be achieved manually
- the operator
'1min8~~~X~Prrssuie-8ange~g.~mantxmetr.>_r~h~ a,~'~ihe-pressu- ~ >~-remainez.-
it may also be achieved automatically, e.g. by a release valve in the
container which releases the fluid
when the pressure of the fluid exceeds the maximum pressure set- It may also
be achieved by a spring-
force operated cap which closes the channel from the pressure source above the
valve actuator when the
p ensure exceeds a certain pre-determined pressure value. Another solution is
that of a comparable
solution of the closable bypass of the outlet valve of the chamber - a
pressure measurement may be
necessary in the container, which may steer an actuator which is opening and
closing the bypass of the
valve actuator according to WO 9926002 of e.g. a Schrader valve of the
container at a pre-determined
pressure value. -
The above mentioned solutions are applicable too to any pistons comprising a
container, incl.
those shown in WO 00/65235 and WO 00/70227.
One such technology is one wherein the piston comprises a container comprising
an elastically
defonnablc container wall.
Is Expansion or contraction of the container wall which is initiated by the
changing size of the
eircompherential length of a cross-section may be enabled by choosing a
reinforcement which forces the
wall of the container to expand or contract in 3 dimensions. Therefore, no
surplus material between the
wall of the container and the wall of the chamber will remain.
Withstanding the influence of a pressure in the chamber on the piston in order
to limit the contact lengdn
(longitudinal stretching) may also be done by choosing a suitable
reinforcement. The reinforcement of
the wall of the container may be and/or may be not positioned in the will of
the container.
A reinforcement in the wall of the container may be made of a textile
material. It may be one
layer, but preferably at least two layers which cross each other, so that the
reinforcement may be easier
to mount. The layers may e.g. be woven or knitted- As the woven threads lay in
different layers closely
to each other, the threads may be made of an elastic material. The layers may
be vuicadized within e.g.
two layers of elastic material, e.g. tubber. When the container has its
production size, not only the
elastic material of the wail, but also the reinforcement is stress free and
undeformed. Expansion of the
reinforced wall of time container means that the distance between die
crossings (= stitch size) may
become larger as the threads expand, while contraction makes the stitch size
smaller as the threads
CA 02786315 2012-08-24
_ CA 02786315 2012-08-24
'3d
contract. The sealing of the wall of the container to the wall of the chamber
may be established by
__nre~gla y tiptainer t1La certair~pzc lti_L{erPbvTv+itl (hr nc~eade h "r.g" :
rxl-l a l;nle hit -
that the stitch size becomes a little bit larger. The contact of the wall of
the container prohibit the
internal pressure to expand the container in such a way that the contact
length will become too large,
and avoids by that jamming.
A knitted reinforcement may be e.g. made of an elastic thread and/or
elastically bendable
thread. The expansion of the wall of the container may be made by stretching
the beaded loops of the
knittings. The stretched loops may become back to its undeformed state when
the wall of the container
contracts.
A textile reinforcement may be produced on a production line where the woven
or knitted
textile reinforcement lay as a cylinder within two layers of elastic material-
Within the smallest cylinder
a bar is positioned on which caps are being held in a sequence top-down-top-
down etc and these may
move on that bar. At the end of the line an vulcanisation oven is being held.
The inside of the oven may
have the site and the form of the container in a stressfree and underformed
state. The part of the
cylinders being inside the oven is being cut on length, two caps being
positioned within the cylinders at
both ends, and being kept there The over is closed, and steam of over ]00 C
and high pressure is put
in. After approx 1-2 minutes the oven may be opened and the ready produced
container wall with the
two caps vulcanised in that wall. to order to use the minutes lead time of the
vulcanisation, there may
more than one oven, e.g. rotating or translating, and all ending at the end of
the production line. It may
also be possible to have more than one oven on the production line itself,
using the transport lead time as
the vulcanisation time.
Production of the fiber reinforced wall of the container may be done similar.
The reinforced
fibers may be produced by e.g. injection moulding, incl. an assembling socket
or by cutting a string,
which thereafter is being put at both ends onto assembling socket. Both
options may easily series
produced. For the rest will the production process be analogeous with the
above mentioned ones
rearding the textile reinforcement.
The piston comprising an elastically deformable container may also comprise
reinforcement
means which are not positioned in the wall, e.g. a plurality of elastic arms,
which may or may not be
131
CA 02786315 2012-08-24
fl
inflatable, connected to the wall of the container. When inflatable, the
reinforcement functions also to
--F5 it4he-defenauatien-oÃtho-wall-oÃthe-g0otainoo-dun-to-dan-pressure-iz>-the-
ahnsabur.
Another option is a reinforcement outside the wall of the container-
Another aspect of the invention is one relating to a combination of a piston
and a chamber,
wherein:
The chamber defines an elongate chamber having a longitudinal ..is,
- the piston being movable in the chamber at least from a second longitudinal
position to a first
longitudinal position,
the chamber having an elastically defonnable inner wall along at least part of
the inner chamber
wall between the first and second longitudinal positions,
- the chamber having, at a first longitudinal position thereof when the piston
is positioned at that
position, a first cross-sectional area thereof and, at a second longitudinal
position thereof when the
piston is positioned at that position, a second cross-sectional area, the
first cross-sectional area being
larger than the second cross-sectional area, the change in cross-section of
the chamber being at least
substantially continuous between the first and second longitudinal positions
when the piston is moved
between the first and second longitudinal positions.
Thus, alternatively to the combinations where the piston adapts to the cross-
sectional changes of
the chamber, this aspect relates ma chamber having adapting capabilities
- 20 Naturally, the piston may be made of an at least substantially
incompressible material - or a
combination may be made of the adapting chamber and an adapting piston - such
as a piston according,
to the above aspects.
Preferably, the piston has, in a cross section along the longitudinal axis, a
shape tapering in a
direction from to the second longitudinal positions-
A preferred manner of providing an adapting chamber is to have the chamber
comprise:
an outer supporting structure enclosing the inner wall and -
a fluid held by a space defined by the outer supporting structure and the
inner wall.
13 Z'
CA 02786315 2012-08-24
In that manlier, the choice of fluid or a combination of fluids may help
defining the properties of the
ehamhercn,.b as the sealaogheiweenlhe-walRantithe_piston-
as3azelLawthe.fnrceregoised-et_
In yet another aspect, the invention relates to a combination of a piston and
a chamber,
wherein:
the chamber defines an elongate chamber having a longitudinal axis,
the chamber having, at a first longitudinal position thereof, a first cross-
sectional shape and
area thereof and, at a second longitudinal position thereof, a second cross-
sectional shape and area, the
first cross-sectional shape being different from the second cross-sectional
shape, the change in cross-
sectional shape of the chamber being at least substantially continuous between
the first and second
longitudinal positions,
- the piston being adapted to adapt itself to the cross-section of the chamber
when moving from the first
to the second Longitudinal position of the ch[unber.
This very interesting aspect is based on the fact that different shapes of
e.g. a geometrical
figure have varying relations between the circumference and the area thereof.
Also, changing between
two shapes may take place in a continuous manner so that the chamber may have
one cross-sectional
shape at one longitudinal position thereof and another at a second lougimdinat
position while maintaining
the preferred smooth variations of the surface in the chamber.
In the present context, the shape of a cross-section is the overall shape
thereof - notwithstanding
the size thereof. Two circles have the same shape even though one has a
diameter different from that of
the other.
Preferably, the first eeess-sectional area is at least 2%, such at least 5%,
preferably at least
]0%, such as at least 20%, preferably at least 30%, such as at least 40%,
preferably at least 50%, such
as at least 60%, preferably at least 70%, such as at least 80, such as at
least 90%, such at least 95%
larger than the second cross-sectional area.
In a preferred embodiment, the first moss-sectional shape is at least
substantially circular Ind
wherein the second cross-sectional shane_c eI ng r Yrneh as. avat least 2,
such as at least 3, preferably at least 4 times a dimension at an angle to the
first dimension.
Id another preferred embodiment, the first cross-sectional shape is at least
substantially circular
and wherein the second cross-sectional shape comprises two or more at least
substantially elongate, such
as lobe-shaped, parts.
When, in the cross-section at the first longitudinal position, a first
circumference of the
chamber is 80-120%, such as 85-115%, preferably 90-110, such as 95-105,
preferably 98-102% of a
second circumference of the chamber in the cross-section at the second
longitudinal direction, a number
of advantages are seen. Problems may arise when attempting to seal against a
wall having varying
dimensions due to the fact that the sealing material should both provide a
sufficient sealing and change
its dimensions. If, as is the situation in the preferred embodiment, the
circumference changes only to a
small degree, the sealing may be controlled more easily. Preferably, the first
and second circumferences
are at least substantially identical so that the sealing material is only bent
and not stretched to any
significant degree.
Alternatively, the circumference may be desired to change slightly in that
when bending or
deforming a sealing material, e.g. a bending will cause one side thereof to be
compressed and another
stretched. Overall, it is desired to provide the desired shape with a
circumference at least close to that
which the sealing material would automatically "choose".
One type of piston, which may be used in this type of combination, is the one
comprising a
piston comprising a deformable container. The container may be elastically or
non-elastically
deformable. In the last way the wall of the container may bent while moving in
the chamber. Elastically
deformable containers with a production size approximately the size of the
circumphrnrncial length of
the first longitudinal position of the chamber, having a reinforcement type
which allows contraction wide
high frictional forces may also be used in this type of combination, and may
be specifically with high
velocities of the piston.
Elastically deformable containers with a production size approximately the
size of the circumpherencial
length of die second longitudinal position of the chamber, having a
reinforcement type of the skin which
CA 02786315 2012-08-24
CA 02786315 2012-08-24
t3~
allows parts of the wall of the container having different distances from the
central axis of the chamber
-;o-a-longitudinal-moss=seeamt oithe-chambea mnyalso-bn eaed.
It is clear that depending on from where the combination is seen, one of the
piston and the
chamber may be stationary and the other moving - or both may be moving. This
has no impact on the
fancaonning of the combination.
The piston may also slide over an internal znd an external wall. The internal
wall may have a
taper form, while the external wall is cylindrical.
Naturally, the present combination may be used for a number of purposes in
that it primarily
to foeuses on a novel manner of providing an additional manner of tailoring
translation of a piston to the
force required/taken up. In fact, the area/shape of the cross-section may be
varied along the length of
the chamber in order to adapt the combination for specific purposes and/or
forces. One purpose is to
provide a pump for use by women or teenagers - a pump that nevertheless should
be able to provide a
certain pressure. In that situation, an ergonomically improved pump may be
required by determining the
force which the person may provide at which position of the piston - and
thereby provide a chamber
with a suitable cross-sectional area/shape-
Another use of the combination would be for a shock absorber where the
area/shape would
determine what translation a certain shock (force) would require. Also, an
actuator may be provided
where the amount of fluid introduced into the chamber will provide differing
translation of the piston
depending on the actual position of the piston prior to the introducing of the
fluid.
In fact, the nature of the piston, the relative positions of the first and the
second longitudinal
positions and the arrangement of any valves corrected to the chamber may
provide pumps, moors,
actuators, shock absorbers etc. with different pressure characteristics and
different force characteristics.
- The preferred embodiments of the combination of a chamber and a piston have
been described
as examples to be used in piston pumps. This however should Oct limit the
coverage of this invention to
the said application, as it may be mainly the valve arrangement of the chamber
besides the fact which
item or medium may initiate the movement, which may be descisive for the type
of application: pump,
actuator, shock absorber or motor. In a piston pump a medium may be meted into
a chamber which
135
CA 02786315 2012-08-24
+e, Cr
may thereafter be closed by a valve arrangement. The medium may be compressed
by the movement of
rfie rhamhe anrifnr rhr nicrnn and~ffirca{Ier a_ual era release._thiicempmased-
medium-frem-the--
chamber. In an actuator a medium may be pressed into a chamber by a valve
arrangement and the piston
and/or the chamber may be moving, initiating the movement of an attached
device. In shock absorbers
the chamber may be completely closed, wherein a compressable medium may be
compressed by the
movement of the chamber and/or the piston In the case a non-compressable
medium may be positioned
inside the chamber, eg. the piston may be equipeed by several small channels
which may give a
dynamic friction, so that the movement may be slowed down.
Further the invention may also be used in propulsion applications where a
medium may be used
to move a piston and/or a chamber, which may turn around an axis as e.g. in a
motor. Any kind of
The principles according this invention may be applicable on all above
mentioned applications.
The principles of the invention may also be used in other pnenmaic and/or
hydraulic applications than
the above mentioned piston pumps.
Thus, the inventionalso retates to a pump for pumping a fluid, the pump
comprising:
a combination according to any of the above aspects,
- means for engaging the piston from a position outside die cbrwber,
a fluid entrance connected to the chamber and comprising a valve means, and
a fluid exit connected to the chamber.
In one situation, the engaging means may have an outer position where the
piston is in its first
longitudinal position, and an inner position where the piston is in its second
longitudinal position. A
pump of this type is preferred when a pressurised fluid is desired.
In another situation, the engaging means may have an outer position where the
piston is in its
second longitudinal position, and an inner position where the piston is in its
first longitudinal position. A
pump of this type is preferred when no substantial pressure is desired but
merely transport of the fluid.
In the situation where the pump is adapted for standing on the floor and the
piston/engaging
means to compress fluid, such as air, by being forced downwards, the largest
force may, ergonomically,
be provided at the lowest position of the piston/engaging means/handle. Thus,
in the first situation, this
CA 02786315 2012-08-24
42- 53-~
means that the highest pressure is provided there. In the second situation,
this merely means that the
-. lsitg ~r a.r'a and rnerehvrthe Iargrst-volume-is seen-auhe-lawgst-pesitioz>-
k3ownvÃr;-dt~-to-tA~Ãaeffhai-t~-
ppessme exceeding that in the e"g. tyre is required in order to open the valve
of the tyre, the smallest
cross-sectional area may be desired shortly before the lowest position of the
engaging means in order for
S the resulting pressure to open the valve and a larger cross-sectional area
to force more fluid into the
tyre"
As the pump according to the invention may use substantial less working force
than comparable pumps
based on the traditional piston-cylinder combination, e.g: water pumps may
extraxt water from greater
depths. This feature is of great significance e.g. in underdeveloped
countries. Also, inthe case of
pumping a liquid when the pressure- difference is almost zero, the chamber
according to the invention
may have another function. It may comply to the physical needs (ergonornical)
of the user by a proper
design of the chamber, e.g. as if there existed a pressure difference: e.g.
according to Figs. 17B and
17A respectively. This may also be accomplished by the use of valves.
is The invention also relates to a piston which seals to a cylinder, and at
the same time to a
tapered cylinder. The piston may or may not comprise an elastically deformable
container. The resulting
chamber may be of the type where the cross-sectional area's have differed,
circumpherential sizes or that
these may be identical. The piston may comprise one of more piston rods. Also
the cylinder at the
outside may be cylindrical or tapered as well.
Also, the invention relates to a shock absorber comprising:
a combination according to any of the combination aspects,
means for engaging the piston from a position outside the chamber, wherein the
engaging
means have an outer position-where the piston is in its first longitudinal
position, and an inner position
where the piston is in its second longitudinal position.
The absorber may further comprise a fluid entrance connected to the chamber
and comprising a -
valve means"
CA 02786315 2012-08-24
Also, the absorber may comprise a fluid exit connected to the chamber and
comprising a valve
It may be preferred that the chamber and the piston forms an at least
substantially sealed cavity
comprising a fluid, the fluid being compressed when the piston moves from the
first to the second
longitudinal positions-
Normally, the absorber would comprise means for biasing the piston toward the
first
longitudinal position.
Also, the invention relates to an actuator comprising:
a combination according to any of the combination aspects,
means for engaging the piston from a position outside the chamber,
means for introducing fluid into the chamber in order to displace the piston
between the first
and the second longitudinal positions.
The newsier may comprise a fluid entrance connected to the chamber and
comprising a valve
means.
Also, a fluid exit connected to the chamber and comprising a valve means may
be provided
Additionally, the actuator may comprise means for biasing the piston toward
the first or second
longitudinal position.
2D The invention relates to a motor comprising
- a combination according to any of the above mentioned combination aspects.
Finally, the invention also relates to a power unit, which preferably may be
movable, e.g.. by
parachute - a M(ovable) P(ower) U(nit).Such a unit may comprise a power source
of any kind,
preferably-at least one sot of solar sells, and a power device, e.g. a motor
according to the invention.
There may be at least one service device present, such as e.g. a pump
according to the invention, and/or
any other device utilising the excess energy derived from the low working
force of a device comprising
a combination of a piston and a chamber according to the invention. Due to the
very low working force
if may be possible to transport a MPU by parachute, as the construction of
devices based on the
" /ls4a nd"knt 62,
i7Iveh~ln, rk~) k. C6Ahtititct rel l,lf1? , 426 GfuaLf 14
ry$
IqIr
The various embodunents described above are provided by way of illustration
only and should not be
cons Wed to limit the invention. Those skilled in the art wilt readily
recoprvze vario ftcalions.__
changes, and combinations of elements which may he made to the present
invention without strictly
following the exemplary embodiments and applications illustrated and described
herein, and without
departing from the true spirit and scope of the present invention.
All piston types, specifically those which are containers with an elastically
deformable wall
may he sealingly connected to the chamber wall during its move between
longitudinal positions
engagingly connected or not connected to the wall of the chamber. Or may be
engagingly and sealingly
connected to the chamber wall. Additionally may there be no engaging between
said walls either,
possibly touching the walls each other, and this may happen eg. in the
situation where the container is
moving from a first to a second longitudinal position in a chamber.
The type.of connection (sealingly and/or engagingly and/or touching and/or no
connection) between said
walls may be accomplished by using the correct inside pressure inside said
container wall: high pressure
for sealingly connection, a tower pressure for engagingly roesoenion and e.g.
atmospheric pressure for
no camection (production sized container) - thus, a container with an enclosed
spare may be preferred,
because the enclosed space may be controlling the pressure inside the
container from a position outside
the piston.
Another option for an engagingly connection is thin wall of the container,
which may have
reinforcements which are sticking out of the surface of said wall, so that
leaking may happen between
the wall of container and the wall of the chamber.
19 09 B DESCRIP 10 OF THE D GS
In e to] owing, referee embed its of the invention ill be escribed Irene to
the
dra ing wherein:
CA 02786315 2012-08-24
11~
CA 02786315 2012-08-24
653 SPECIFICALLY PREFERRED EMBODIEMENTS
According to an embodiment of the invention, there is provided a piston-
chamber combination
comprising an elongate chamber which is bounded by an inner chamber wall, and
comprising a
piston in said chamber to be sealingly movable relative to said chamber wall
at least between a first
longitudinal position and a second longitudinal position of the chamber, said
chamber having cross-
sections of different cross-sectional areas and different circumferential
lengths at the first and second
longitudinal positions, and at least substantially continuously different
cross-sectional areas and
circumferential lengths at intermediate longitudinal positions between the
first and second
longitudinal positions, the cross-sectional area and circumferential length at
said second longitudinal
position being smaller than the cross-sectional area and circumferential
length at said first
longitudinal position, said piston comprising a ,container which is
elastically deformable thereby
providing for different cross-sectional areas and circumferential lengths of
the piston adapting the
same to said different cross-sectional areas and different circumferential
lengths of the chamber
during the relative movements of the piston between the first and second
longitudinal positions
through said intermediate longitudinal positions of the chamber, wherein: the
piston is produced to
have a production-size of the container in the stress-free and undeformed
state thereof in which the
circumferential length of the piston is approximately equivalent to the
circumferential length of said
chamber (162,186,231) at said second longitudinal position, the container
being expandable from its
production size in a direction transversally with respect to the longitudinal
direction of the chamber
thereby providing for an expansion of the piston from the production size
thereof during the relative
movements of the piston from said second longitudinal position to said first
longitudinal position.
Preferably is the container inflatable and said container being elastically
deformable and being
inflatable to provide for different cross-sectional areas and circumferential
lengths of the piston.
Preferably is the cross-sectional area of said chamber at the second
longitudinal position thereof
between 98 % and 5 % of the cross-sectional area of said chamber at the first
longitudinal position
thereof.
DT 2~r iyfl
CA 02786315 2012-08-24
Preferably is the cross-sectional area of said chamber at the second
longitudinal position thereof 95 -
15 % of the cross-sectional area of said chamber at the first longitudinal
position thereof.
Preferably is the cross-sectional area of said chamber at the second
longitudinal position thereof
approximately 50% of the cross-sectional area of said chamber at the first
longitudinal position
thereof.
Preferably is the container containing a deformable material.
to Preferably is the deformable material a fluid or a mixture of fluids, such
as water, steam and/or gas,
or a foam.
Preferably is the deformable material comprising spring-force operated
devices, such as springs.
Preferably has in a cross-section through the longitudinal direction, the
container, when being
positioned at the first longitudinal position of the chamber, a first shape
which is different from a
second shape of the container when being positioned at the second longitudinal
position of said
chamber.
Preferably is at least part of the deformable material compressible and
wherein the first shape has an
area being larger than an area of the second shape.
Preferably is the deformable material is at least substantially
incompressible.
Preferably is the container inflatable, to a certain pre-determined pressure
value.
Preferably is the pressure remaining constant during the stroke.
CA 02786315 2012-08-24
()
Preferably is the piston comprising an enclosed space communicating with the
deformable container,
the enclosed space having a variable volume.
Preferably is the volume of the enclosed space adjustable.
Preferably is the first enclosed space comprising a spring-biased pressure
tuning piston.
Preferably further comprising means for defining the volume of the first
enclosed space so that the
pressure of fluid in the first enclosed space relates to the pressure in the
second enclosed space.
Preferably the defining means are adapted to define the pressure in the first
enclosed space during the
stroke.
Preferably are the defining means adapted to define the pressure in the first
enclosed space at least
substantially constant during the stroke.
Preferably is the spring-biased pressure tuning piston a check valve through
which fluid of an
external pressure source can flow into the first enclosed space.
Preferably can the fluid from an external pressure source enter the second
enclosed space through an
inflation valve, preferably a valve with a core pin biased by a spring, such
as a Schrader valve from
an external pressure source.
Preferably is the piston communicating with at least one valve.
Preferably is the piston comprising a pressure source.
Preferably is the valve an inflation valve, preferably a valve with a core pin
biased by a spring, such
as a Schrader valve.
CA 02786315 2012-08-24
Preferably is the valve a check valve.
Preferably is the foot of the chamber connected to at least one valve.
Preferably is the outlet valve an inflation valve, preferably a valve with a
core pin biased by a
spring, such as a Schrader valve, said core pin is moving towards the chamber
when closing the
valve.
Preferably is the core pin of the valve connected to an actuator which opens
or close the valve.
Preferab ly is the actuator a valve actuator for operating with valves having
a spring-force operated
valve core pin, comprising a housing to be connected to a pressure medium
source, within the housing
a coupling section for receiving the valve to be actuated, a cylinder
surrounded by a cylinder well of a
predetermined cylinder wall diameter and having a first cylinder end and a
second cylinder end which is
farther away from the coupling section than the first cylinder end, a piston
which is movably located in
the cylinder and fixedly coupled to an activating pin for engaging with the
spring-force operated valve
core pin of the valve received in the coupling section, and a conducting
channel, for conducting pressure
media from the cylinder to the coupling section when the piston is moved into
a first piston position in
which the piston is at a first predetermined distance from the first cylinder
end, the conduction of the
pressure media between the cylinder and the coupling section being inhibited
when the piston is moved
into a second piston position in which the piston is at a second predermined
distance from the first
cylinder end which second distance being larger than said first distance,
wherein the conducting channel
is arranged in the cylinder wall and opens into the cylinder at a cylinder
wall portion having the
predetermined cylinder wall diameter, and the piston comprises a piston ring
with a sealing edge which
sealingly fits with said cylinder wall portion thereby inhibiting the
conduction of the pressure medium
into the channel in the second position of the piston and opening the channel
in the first position of the
piston.
CA 02786315 2012-08-24
2,3-57 1 13
Preferably is the actuator is a valve actuator for operating with valves
having a spring-force operated
valve core pin, comprising a housing to be connected to a pressure medium
source, within the
housing a coupling section for receiving the valve to be actuated, a cylinder
circumferentially
surrounded by a cylinder wall of a predetermined cylinder wall diameter and
having a first cylinder
end and a second cylinder end which is farther away from the coupling section
than said first cylinder
end and is connected to the housing for receiving pressure medium from said
pressure source, a
piston which is movably located in the cylinder and fixedly coupled to an
activating pin for engaging
with the spring-force operated valve core pin of the valve received in the
coupling section, and a
conducting channel between said second cylinder end and said coupling section
for conducting
pressure medium from said second cylinder end to the coupling section when the
piston is moved into
a first piston position in which the piston is at a first predetermined
distance from said first cylinder
end, said conduction of pressure medium between said second cylinder end and
the coupling section
being inhibited when the piston is moved into a second piston position in
which the piston is at a
second predermined distance from said first cylinder end which second distance
being larger than
said first distance, the conducting channel is arranged in said cylinder wall
and has a channel portion
which opens into the cylinder at a cylinder wall portion having said
predetermined cylinder wall
diameter, and the piston comprises a piston ring with a sealing edge which
sealingly fits with said
cylinder wall portion, said sealing edge of the piston ring being located
between said channel portion
and said second cylinder end in said second piston position, thereby
inhibiting said conduction of the
pressure medium from said second cylinder end into the channel in said second
piston position, and
being located between said channel portion and said first cylinder end in said
first piston position,
thereby opening the channel to said second cylinder end in said first piston
position.
Preferably is the activator an actuator valve for a container type piston
pressure management system
that selectively feeds pressurized air to the interior of a container type
piston, said valve comprising,
a valve body with a cylindrical central passage opening both to said
pressurized fluid and to the
interior of said container type piston, a spring loaded check valve tightly
received in said central
passage that blocks said central passage when closed and allows flow of fluid
through when opened,
~ rLrti
CA 02786315 2012-08-24
a spring loaded piston slidably received within said passage above said check
valve that slides from
an off-position toward said check valve to an on-position when said
pressurized fluid is supplied and
off again when said pressurized fluid is removed, said piston engaging the
surface of said central
passage with sufficient clearance to allow unrestricted sliding, but not
closely enough to prevent the
leakage of pressurized fluid between said piston and central passage surface,
a stem carried by said
piston and engageable with said check valve to open it and allow the passage
of pressurized fluid to
said check valve and to said container type piston interior as said piston
moves to the on-position, a
stationary plug in said central passage between said check valve and piston
through which said stem
extends that is normally axially spaced from said piston but abuts said piston
in its on-position, said
plug having a vent path running from atmosphere into the space between said
plug and piston at a
vent point radially near said stem so that pressurized fluid leaking past said
piston as it moves will
not compress between said plug and piston to retard its motion, and, a
circular compression seal
surrounding said vent point that is compressed between said piston and plug
when they are abutted to
that pressurized air leaking past said piston can not vent to atmosphere when
said check valve is
open.
Preferably is the activator an actuator valve for a container type piston
pressure management system
that selectively feeds pressurized fluid to the interior of said container
type piston, said valve
comprising, a valve body with a cylindrical central passage opening both to
said pressurized fluid and
to the interior of said container type piston, a spring loaded check valve
tightly received in said
central passage that blocks said central passage when closed and allows flow
of fluid through when
opened, a spring loaded piston slidably received within said passage above
said check valve that
slides from an off-position toward said check valve to an on-position when
said pressurized fluid is
supplied and off again when said pressurized fluid is removed, said piston
engaging the surface of
said central passage with sufficient clearance to allow unrestricted sliding,
but not closely enough to
prevent the leakage of pressurized fluid between said piston and central
passage surface, a stem
carried by said piston and engageablc with said check valve to open it and
allow the passage of
pressurized fluid to said check valve and to said container type piston
interior as said piston moves to
the on-position, an outer annular disk and an inner annular disk abutted in
said central passage to
CA 02786315 2012-08-24
form a plug between said check valve and piston through which said stem
extends, said piston being
normally axially spaced from said outer disk but abutted therewith in its on-
position, said outer disk
having a series of holes radially close to said stem opening to a series of
notches in said inner disk to
create a vent path canning from the atmosphere into the space between said
plug and piston so that
pressurized fluid leaking past said piston as it moves will not compress
between said plug and piston
to retard its motion, and, a circular compression seal surrounding said holes
that is compressed
between said piston and plug when they are abutted so that pressurized fluid
leaking past said piston
cannot vent to the atmosphere when said check valve is open.
Preferably is an activating pin for connecting to inflation valves, comprising
a housing to be
connected to a pressure source, within the housing a connection hole having a
central axis and an
inner diameter approximately corresponding to the outer diameter of the
inflation valve to which the
activating pin is to be connected, and a cylinder and means for conducting
liquid media between the
cylinder and the pressure source, and where the activating pin is arranged to
engage a central spring-
force operated core pin of the inflation valve, is arranged to be situated
within the housing in
continuation of the coupling hole coaxially with the central axis thereof, and
comprises a piston part
with a piston, which piston is to be positioned in the cylinder movable
between a first piston position
and a second piston position, the activating pin comprising a channel, said
piston part comprises a
first end and a second end, wherein the piston is located at said first end
and said channel has an
opening at said first end, a valve part being movable in the channel, drivable
by difference in forces
acting on surfaces of the valve part, between a first valve position and a
second valve position,
wherein said first valve position leaves said opening open, and said second
valve position closes said
opening, and the top of the piston part forming a valve seat for a seal face
of the valve the valve
means.
Preferably is the valve actuator an activating pin for connecting to inflation
valves, comprising a
housing, within the housing a coupling hole for coupling with an inflation
valve, the coupling hole
having a central axis and an outer opening, positioning means for positioning
the inflation valve when
coupled in the coupling hole, and an activating pin, which is arranged
coaxially with the coupling hole,
CA 02786315 2012-08-24
f `16
for depressing a central spring-force operated core pin of the inflation
valve, a cylinder having a
cylinder wall provided with a pressure port which is connected to a pressure
source, wherein the
activating pin is shiftable between a proximal pin position and a distal pin
position relative to the
positioning means so as to depress the core pin of the inflation valve in its
distal pin position and
disengage the core pin of the inflation valve in its proximal pin position
when the inflation valve is
positioned by the positioning means, the activating pin is coupled with a
piston and the piston is
slidingly arranged in the cylinder and is movable between a proximal piston
position, which
corresponds to the proximal pin position, and a distal piston position, which
corresponds to the distal
pin position, the piston is disposed in the cylinder between the pressure port
and the coupling hole and
is drivable from its proximal piston position to its distal piston position by
the pressure supplied into
the cylinder from the pressure source, and - that flow regulating means are
provided for selectively
interrupting or freeing a flow path between the pressure source and the
coupling hole depending on the
piston positions and are adapted such that the flow path is interrupted in the
proximal piston position
and the flow path is freed in the distal piston position at least when the
inflation valve is positioned by
the positioning means.
Preferably is the piston comprising means to obtain a pre-determined pressure
level.
Preferably is the valve a release valve.
Preferably is a spring-force operated cap which closes the channel above the
valve actuator when the
pressure comes above a certain pre-determined pressure value.
Preferably is a channel be opened or closed, the channel connects the chamber
and the space between
the valve actuator and the core pin, a piston is movable between an opening
position and a closing
position of said channel, and the movement of the piston is controlled by an
actuator which is steered
as a result of a measurement of the pressure in the piston.
CA 02786315 2012-08-24
Preferably is a channel be opened or closed, which connects the chamber and
the space between the
valve actuator and the core pin.
Preferably is a piston movable between an opening position and a closing
position of said channel-
Preferably is the piston operated by a operator controlled pedal, which is
turning around an axle from
a inactive position to an activated position and vice versa.
Preferably is the piston controlled by an actuator which is steered as a
result of a measurement of the
pressure in the piston.
Preferably is the combination further comprising means for defining the volume
of the enclosed space
so that the pressure of fluid in the enclosed space relates to the pressure
acting on the piston during
the stroke.
Preferably is the foam or fluid adapted to provide, within the container, a
pressure higher than the
highest pressure of the surrounding atmosphere during translation of the
piston from the second
tongitudi-nal position of the chamber to the first longitudinal position
thereof or vice versa.
Preferably is the combination comprising a pressure source.
Preferably has the pressure source a higher pressure level than the pressure
level of the container.
Preferably is the pressure source communicating with the container by an
outlet valve and an inlet
valve
Preferably is the outlet valve an inflation valve, preferably a valve with a
core pin biased by a
spring, such as a Schrader valve, said core pin is moving towards the pressure
source when closing
the valve.
CA 02786315 2012-08-24
~",~ 1 w8
Preferably is the inlet valve an inflation valve, preferably a valve with a
core pin biased by a spring,
such as a Schrader valve, said core pin is moving towards the container when
closing the valve.
Preferably is a channel be opened or closed, which connects the chamber and
the space between the
valve actuator and the core pin.
Preferably is a channel be opened or closed, which connects the chamber and
the space between the
valve actuator and the core pin-
Preferably is a piston movable between an opening position and a closing
position of said channel.
Preferably is a channel he opened or closed, the channel connects via the
space the chamber and the
space between the valve actuator and the core pin, a piston is movable between
an opening position
and a closing position of said channel, and the movement of the piston is
controlled by an actuator
which is steered as a result of the measurement of the pressure level in the
piston and that of the
pressure source.
Preferably is a channel be opened or closed, the channel connects via the
space the chamber and the
space between the valve actuator and the core pin, a piston is movable between
an opening position
and a closing position of said channel, and the movement of the piston is
controlled by an actuator
which is steered as a result of the measurement of the pressure level of the
pressure in the and that of
the pressure source.
Preferably is the wall of the container comprising an elastically deformable
material comprising
reinforcement means.
Preferably have the reinforcement windings a braid angle which is different
from 54 44'.
CA 02786315 2012-08-24
Preferably is the reinforcement means comprising a textile reinforcement,
which enable expansion of
the container when moving to a first longitudinal position, and enable
contraction when moving to a
second longitudinal position.
Preferably is the piston produced by a production system with multiple
vulcanisation caves.
Preferably is the reinforcement means comprising fibres, which enable
expansion of the container
when moving to bigger a first longitudinal position, and enable contraction
when moving to a second
longitudinal position.
Preferably is the piston produced by a production system with multiple
vulcanisation caves and where
the fibers are being mounted in the caves of the caps by rotation of the
fibers and the cabs at
different speeds, while the fibers are being pushed onto the inside of the
caps.
Preferably are the fibers arrangend as to the Trellis Effect.
Preferably is the reinforcement means comprising a flexable material
positioned in the container,
comprising a plurality of at least substantially elastic support members
rotatably fastened to a
common member, the common members connected to the skin of the container.
Preferably are said members andlor the common member inflatable.
Preferably is the pressure on the wall of the container build up by spring-
force operated devices.
Preferably is the piston comprising a reinforcement which is positioned
outside the container.
Preferably is the container moving in a cylinder around a tapered wall.
CA 02786315 2012-08-24
2 t2
Preferably is the chamber convex and the operating force tangents a set
maximum force during the
stroke.
According to an embodiment of the invention, there is also provided a
combination according to any
of the preceeding statements or a combination of a piston comprising a
container which has a wall
which is bendable, or a combination of a piston comprising a container with a
production size
approximately the size of the circumpherencial length of the first
longitudinal position of the
chamber, having a reinforcement which allow contraction with high frictional
forces, wherein: the
cross-sections of the different cross-sectional areas have different cross-
sectional shapes, the change
in cross-sectional shape of the chamber being at least substantially
continuous between the first and
second longitudinal positions of the chamber, wherein the piston is further
designed to adapt itself
and the sealing means to the different cross-sectional shapes.
Preferably is the cross-sectional shape of the chamber at the first
longitudinal position thereof at least
substantially circular and wherein the cross-sectional shape of the chamber at
the second longitudinal
position thereof is elongate, such as oval, having a first dimension being at
least 2, such as at least 3,
preferably at least 4 times a dimension at an angle to the first distension.
Preferably is the cross-sectional shape of the chamber at the first
longitudinal position thereof at least
substantially circular and wherein the cross-sectional shape of the chamber at
the second longitudinal
position thereof comprises two or more at least substantially elongate, such
as lobe-shaped, parts.
Preferably is a first circumferential length of the cross-sectional shape of
the cylinder at the first
longitudinal position thereof amounting to 80-120%, such as 85-115%,
preferably 90-110, such as
95-105, preferably 98-102%, of a second circumferential length of the cross-
sectional shape of the
chamber at the second longitudinal position thereof.
Preferably are the first and second circumferential lengths at least
substantially identical.
CA 02786315 2012-08-24
' 2-l- 15-/
According to an embodiment of the invention, there is also provided a piston-
chamber combination
comprising an elongate chamber bounded by an inner chamber wall and comprising
a piston in the
chamber to be sealingly movable in the chamber, the piston being movable in
the chamber at least
from a second second longitudinal position thereof to a first longitudinal
position thereof, the
chamber comprising an elastically deformable inner wall along at least part of
the length of the
chamber wall between the first and second longitudinal positions, the chamber
having, at the first
longitudinal position thereof when the piston is positioned at that position,
a first cross-sectional area,
which is larger than a second cross-sectional area at the second longitudinal
position of the chamber
when the piston is positioned at that position, the change in cross-sections
of the chamber being at
least substantially continuous between the first and second longitudinal
positions when the piston is
moved between the first and second longitudinal positions the piston including
an elastically
expandable container having changeable geometrical shapes which adapt to each
other during the
piston stroke thereby enabling a continuous sealing, and the piston having its
production size when
positioned at the second longitudinal position of the chamber.
Preferably is the piston made of an at least substantially incompressible
material.
Preferably has the piston, in a cross section along the longitudinal axis, a
shape tapering in a
direction from the first longitudinal position of the chamber to the second
longitudinal position
thereof.
Preferably is the angle between the wall and the central axis of the cylinder
at least smaller than the
angle between the wall of the taper of the piston and the central axis of the
chamber.
Preferably is the chamber comprising an outer supporting structure enclosing
the inner wall and
a fluid held by a space defined by the outer supporting structure and the
inner wall.
Preferably is the space defined by the outer structure and the inner wall
inflatable.
CA 02786315 2012-08-24
Z-W-Ir 151
Preferably is the piston comprises an elastically deformable container
comprising a deformable
material and designed according to statements 7 to 17.
According to an embodiment of the invention, there is provided a pump for
pumping a fluid, the
pump comprising a combination according to any of the earlier mentioned
statements, means for
engaging the piston from a position outside the chamber, a fluid entrance
connected to the chamber
and comprising a valve means, and a fluid exit connected to the chamber.
Preferably have the engaging means an outer position where the piston is at
the first longitudinal
position of the chamber, and an inner position where the piston is at the
second longitudinal position
of the chamber.
Preferably have the engaging means an outer position where the piston is at
the second longitudinal
position of the chamber, and an inner position where the piston is at the
first longitudinal position of
the chamber.
According to an embodiment of the invention, there is provided a shock
absorber comprising: a
combination according to any of the preceeding statements 1-80, means for
engaging the piston from
a position outside the chamber, wherein the engaging means have an outer
position where the piston
is at the first longitudinal position of the chamber, and an inner position
where the piston is at the
second longitudinal position.
Preferably is the shock absorber comprising a fluid entrance connected to the
chamber and
comprising a valve means. -
Preferably is the shock absorber further comprising a fluid exit connected to
the chamber and
comprising a valve means.
CA 02786315 2012-08-24
-De zof-63
Preferably form the chamber and the piston an at least substantially sealed
cavity comprising a fluid,
the fluid being compressed when the piston moves from the fast to the second
longitudinal positions
of the chamber.
Preferably a shock absorber further comprising means for biasing the piston
toward the first
longitudinal position of the chamber.
According to an embodiment of the invention, there is provided an actuator
comprising: a
combination according to any of preceeding the statements 1-80, means for
engaging the piston from
a position outside the chamber, means for introducing fluid into the chamber
in order to displace the
piston between the first and the second longitudinal positions of the chamber.
Preferably an actuator further comprising a fluid entrance connected to the
chamber and comprising a
valve means.
Preferably an actuator further comprising a fluid exit connected to the
chamber and comprising a
valve means.
Preferably an actuator further comprising means for biasing the piston toward
the first or second
longitudinal position of the chamber.
Preferably the introducing means comprise means for introducing pressurised
fluid into the chamber.
Preferably are the introducing means adapted to introduce a combustible fluid,
such as gasoline or
diesel, into the chamber, and wherein the actuator further comprises means for
combusting the
combustible fluid.
Preferably are the introducing means adapted to introduce an expandable fluid
to the chamber, and
wherein the actuator further comprises means for expand the expandable fluid.
CA 02786315 2012-08-24
CW- 157
Preferably is the actuator further comprising a crank adapted to translate the
translation of the piston
into a rotation of the crank.
Preferably a motor wherein comprising a combination according to any of the
foregoing statements.
Preferably a power unit comprising a combination according to any of the
foregoing statements, a
power source, and a power device.
Preferably is- the power unit movable.
25
CA 02786315 2012-08-24
653-2 SPECIFICALLY PREFERRED EMBODIMENTS
According to an embodiment of the invention, there is provided a piston-
chamber combination
comprising an elongate chamber which is bounded by an inner chamber wall, and
comprising a piston in said
chamber to be sealingly movable relative to said chamber wall at least between
a first longitudinal position
and a second longitudinal position of the chamber, said chamber having cross-
sections of different cross-
sectional areas and different circumferential lengths at the first and second
longitudinal positions, and at least
substantially continuously different cross-sectional areas and circumferential
lengths at intermediate
longitudinal positions between the fast and second longitudinal positions, the
cross-sectional own and
circumferential length at said second longitudinal position being smaller than
the cross-sectional area and
circumferential length at said fast longitudinal position, said piston
comprising a container which is
elastically deformable thereby providing for different cross-sectional areas
and circumferential lengths of the
piston adapting the same to said different cross-sectional areas and different
circumferential lengths of the
chamber during the relative movements of the piston between the first and
second longitudinal positions
through said intermediate longitudinal positions of the chamber, said
container is inflatable and being
elastically deformable to provide for different cross-sectional areas and
circumferential lengths, wherein said
piston is communicating with a pressure source.
Preferably takes the communication place through an enclosed space, the
enclosed space having a variable
volume.
Preferably takes the communication place through a valve.
Preferably is the pressure source communicating with the container by an
outlet valve and an inlet valve.
Preferably is the outlet valve an inflation valve preferably a valve with a
core pin biased by a spring, such as
a Schrader valve, said core pin is moving towards the pressure source when
closing the valve.
Preferably is the inlet valve an inflation valve preferably a valve with a
core pin biased by a spring, such as a
Schrader valve, said core pin is moving towards the container when closing the
valve.
According to an embodiment of the invention there is also provided a valve
actuator for operating with
valves having a spring-force operated valve core pin, comprising a housing to
be connected to a pressure
medium source, within the housing a coupling section for receiving the valve
to be actuated, a cylinder
surrounded by a cylinder wall ofa predetermined cylinder wall diameter and
having a first cylinder end and a
second cylinder end which is farther may from the coupling section than the
fast cylinder end, a piston which is
--IS6
CA 02786315 2012-08-24
movably located in the cylinder and fixedly coupled to an activating pin for
engaging with the spring-force
operated valve core pin ofthe valve received in the coupling section, and a
conducting channel, for conducting
pressure media from the cylinder to the coupling section when the piston is
moved into a first piston position in
which the piston is at a first predetermined distance from the ft cylinder
end, the conduction ofthe pressure
media between the cylinder and the coupling section being inhibited when the
piston is moved into a second
piston position in which the piston is at a second predermined distance from
the first cylinder end which second
distance being larger than said first distance, wherein the conducting channel
is arranged in the cylinder wall and
opens into the cylinder at a cylinder wall portion having the predetemrined
cylinder wall diameter, and the piston
comprises a piston ring with a sealing edge which sealingly fits with said
cylinder wall portion thereby inhibiting
the conduction of the pressure medium into the channel in the second position
of the piston and opening the
channel in the first position of the piston.
Preferably can a channel be opened or closed, which connects the chamber and
the space between the valve
actuator and the core pin.
Preferably can a channel be opened or closed, which connects the chamber and
the space between the valve
actuator and the core pin.
Preferably is a piston movable between an opening position and a closing
position of said channel.
Preferably can a channel be opened or closed, the channel connects via the
space the chamber and the space
between the valve actuator and the core pin, a piston is movable between an
opening position and a closing
position of said channel, and the movement of the piston is controlled by an
actuator which is steered as a
result of the measurement of the pressure level in the piston and that of the
pressure source.
Preferably cane channel be opened or closed, the channel connects via the
space the chamber and the space
between the valve actuator and the core pin, a piston is movable between an
opening position and a closing
position of said channel, and the movement of the piston is controlled by an
actuator which is steered as a
result of the measurement of the pressure level of the pressure in the piston
and that of the pressure source.
Preferably is said enclosed space comprising a first enclosed space.
Preferably is said enclosed space comprising a second enclosed space.
Preferably comprises the first enclosed space comprises a spring biased
pressure tuning piston.
W 15~
CA 02786315 2012-08-24
According to an embodiment of the invention there is also provided means for
defining the volume of
the first enclosed space, so that the pressure of fluid in the first enclosed
space relates to the pressure in the
second enclosed space.
Preferably is the spring-biased pressure tuning piston a check valve through
which fluid of an external
pressure source can flow into the first enclosed space.
Preferably enters the fluid from an external pressure source the second
enclosed space through an inflation
valve, preferably a valve with a core pin biased by a spring, such as a
Schrader valve.
Preferably is the piston produced to have a production-size of the container
in the stress-free and undeformed
state thereof in which the circumferential length of the piston is
approximately equivalent to the
circumferential length of said chamber at said second longitudinal position,
the container being expandable
from its production size in a direction transversally with respect to the
longitudinal direction of the chamber
thereby providing for an expansion of the piston from the production size
thereof during the relative
movements of the piston from said second longitudinal position to said first
longitudinal position,
Preferably is the cross-sectional area of said chamber at the second
longitudinal position thereof between 98
% and 5 % of the cross-sectional area of said chamber at the first
longitudinal position thereof.
Preferably is a combination wherein the cross-sectional area of said chamber
at the second longitudinal
position thereof 95 - 15 % of the cross-sectional eras of said chamber at the
first longitudinal position
thereof.
Preferably is the cross-sectional area of said chamber at the second
longitudinal position thereof
approximately 50% of the cross-sectional area of said chamber at the first
longitudinal position thereof.
Preferably comprises the wall of the container an elastically deformable
material, comprising reinforcement
means.
Preferably contains the container a deformable material.
Preferably is deformable material a fluid or a mixture of fluids, such as
water, steam and/or gas, or a foam.
CA 02786315 2012-08-24
507 SUMMARY OF THE INVENTION
The valve actuator of the present invention and embodiments thereof are
subjects of
claims 1 and 2 td 17, respectively. A valve connector and a pressure vessel or
hand pump,
-- compnsmg a valve a a or o e presen raven, on aze~is UjÃtit~lat~8 aa-tl-lfJ,
respectively. Claim 20 is directed to the use of the valve actuator in a
stationary construction-
The present invention provides a valve actuator which comprises an inexpensive
combination of a cylinder, within in which the piston driving the activating
pin moves, and an
activating pin, having a simple construction. This combination can be used in
stationary
constructions, such as chemical plants, where the activating pin engages the
spring-force
70 operated core pin of a valve (e.g. a release valve), as well as in valve
connectors (eg for
inflating vehicle tires). The disadvantage of conventional valve connectors
have been overcome
by the valve actuator of the present invention. This valve actuator features a
piston having a
piston ring fitting; into the cylinder, where the piston, in its first
position, is at a first
predetermined distance from the fast end of the cylinder. In the piston's
second position, it is at
a second predetermined distance from the fast end of the cylinder, wherein the
second
predetermined distance is larger than the first predetermined distance. The
cylinder wall
comprises a conducting channel for allowing conduction of gaseous andlor
liquid media between
the cylinder and the coupling section when the piston is in the first
position, whereas conduction
of gaseous and/or liquid media between the cylinder and the coupling section
is inhibited by the
piston when the piston is in the second position.
One embodiment of the valve actuator of the present invention according to
claim 6
features a conducting channel from the pressure source to the valve to be
actuated that comprises
an enlargement of the cylinder diameter which is arrangend around the piston
of the activating
pin in the bottom of the cylinder, when the piston is in the first position,
enabling the medium
from the pressure source to flow to the opened spring-force operated valve
core pin, e.g. from a
Schrader valve. The enlargement of the cylinder's diameter may be uniform, or
the cylinder wall
may contain one or several sections near the bottom of the cylinder where the
distance between
the center line of the cylinder and the cylinder wall increases so that
gaseous and/or liquid media
can freely flow around the edge of the piston ring when the piston is in the
first position A
variant of this embodiment has a valve actuator arrangement of which its
cylinder has the
enlargement of the diameter twice. The distance between the enlargements can
be the same as the
distance between the sealing levels of the sealing means. When three valves of
different sizes can
be coupled the valve actuator may comprise a cylinder with three enlargements.
It is however
also possible to cooect valves of diffetnt sizes to a valve actuator having a
single arrangement
for the enlargement of the diameter of the cylinder. Now therefore the number
of enlargements
CA 02786315 2012-08-24 .
can-be different from the number of different valve sizes of valves which can
be coupled.
Another embodiment of the present invention according to claim 10 features a
conducting
channel through a part of the body of the valve actuator. The channel forms a
passage for
g=o aud/9idi4uJd ",Ilia between th cylinder the art of the valy acn _ hich ie
coupled to the valve- The orifice of the channel opening in the cylinder is
located such that, when
the piston is in the first position, pressurized gaseous and/or liquid media
flowing from the
pressure source to the cylinder may flow further through the channel to the
valve to be actuated.
When the piston is in the second position, it blocks the cylinder so that the
flow of pressurized
gaseous and/or liquid media into the channel is not possible.
Instead of air, (mixtures of) gases and/or liquids of any kind can activate
the activation
pin and can flow mound the piston of the valve actuator when the piston is in
its first position.
The invention can be used in all types of valve connectors to which a valve
with a spring-force
operated core pin (e.g. a Schrader valve) can be coupled irrespective of the
method of coupling
or the number of coupling holes in the connector. Furthermore the valve
actuator can be coupled
to for example a foot pump, car pump, or compressor. The valve actuator can
also be integrated
in any pressure source (e.g. a handpump or a pressure vessel) irrespective of
the availability of a
securing means in d,e valve connector. It is also possible for the invention
to be used in
permanent constructions where the activating pin of the actuator engages the
core pm of a
permanently mounted valve.
CA 02786315 2012-08-24
507 SPECIFICALLY PREFERRED EMBODIMENTS
According to an embodiment of the invention, there is provided a valve
actuator for operating with
valves having a spring-force operated valve core pin, comprising - a housing
to be connected to a
pressure medium source, within the housing a coupling section for receiving
the valve to be actuated, a
cylinder surrounded by a cylinder wall of a predetermined cylinder wall
diameter and having a first
cylinder end and a second cylinder end which is farther away from the coupling
section than the first
cylinder end, a piston which is movably located in the cylinder and fixedly
coupled to an activating pin
for engaging with the spring force operated valve core pin of the valve
received in the coupling section,
and a conducting channel for conducting pressure media from the cylinder to
the coupling section when
the piston is moved into a first piston position in which the piston is at a
first predetermined distance
from the first cylinder end, the conduction of the pressure media between the
cylinder and the coupling
section being inhibited when the piston is moved into a second piston position
in which the piston is at a
second predermined distance from the first cylinder end which second distance
being larger than said
first distance, wherein: the conducting channel is arranged in the cylinder
wall and opens into the
cylinder at a cylinder wall portion having the predetermined cylinder wall
diameter, and the piston
comprises a piston ring with a sealing edge which sealingly fits with said
cylinder wall portion thereby
inhibiting the conduction of the pressure medium into the channel in the
second position of the piston
and opening the channel in the first position of the piston.
Preferably is said first predeternned distance greater than zero.
Preferably is said first predetermined distance approximately zero.
Preferably it is comprising a stopper to limit the movement of the piston in
the first piston position.
Preferably it is comprising a tapered portion at the first end of the cylinder
and a conical portion of the
piston to coincide with said tapered portion when the piston is in the first
piston position.
CA 02786315 2012-08-24
Preferably is the conducting channel formed by an enlargement of the cylinder
wall diameter which is
arranged to be radially around the piston when being in its first piston
position so that the pressure
medium can freely flow around the edge of the piston ring when the piston is
in its first piston position.
Preferably is the enlargement of the cylinder diameter formed at one or
several sections of the
circumference of the cylinder wall.
Preferably is the wall of the enlargement comprising a cylindrical enlargement
wall portion and an
inclined enlargement wall portion forming an angle with the cylinder axis
which is larger than 0 and
smaller than 20 , wherein the inclined enlargement wall portion is situated
between the cylindrical
enlargement wall portion and the cylinder wall portion having the
predetermined cylinder wall diameter.
Preferably is a channel portion of the conducting channel between the
cylindrical enlargement wall
portion and the coupling section designed as a tapered channel portion shaped
as a groove or is designed
as a hole (107) which is parallel to the center axis of the cylinder.
Preferably is the coupling section connected by the conducting channel to an
orifice in the cylinder wall
portion , said orifice being situated at a distance from the first cylinder
end so that the orifice is situated
between the piston and the second end of the cylinder when the piston is in
the first piston position.
Preferably is the piston further movable within the cylinder to a third
position and a fourth position,
corresponding to a third predetermined distance and a fourth predetermined
distance from the first end
of the cylinder, respectively, where said third predetermined distance is
larger than said second
predetermined distance and said fourth predetermined distance is larger than
said third predetermined
distance; and - the cylinder comprises a second channel for allowing the
conduction of gaseous and/or
liquid media between the cylinder and the coupling section when the piston is
in said third position and
inhibiting the conduction of gaseous and/or liquid media between the cylinder
and the coupling section
when the piston is in said fourth position.
CA 02786315 2012-08-24
167,
Preferably is the embodiment comprising within the coupling section sealing
means for sealing the valve
actuator onto valves of different types and/or sizes, and the sealing means
comprise a first annular
sealing portion and a second annular portion situated coaxially with the
centre axis of the coupling
section and being displaced in the direction of the centre axis of the
coupling section , said first annular
portion is closer to the opening of the coupling section than said second
annular portion and the diameter
of said first annular portion is larger than the diameter of said second
annular portion
Preferably is the embodiment comprising within the coupling section a securing
thread for securing the
valve actuator onto the inflation valve.
Preferably is said securing thread a temporary securing thread .
Preferably is the cylinder wall formed as a cylinder sleeve, fastened and
sealed in the housing and
formed with said inclined enlargement wall portion , the cylinder sleeve
having distant from the first
cylinder end a wall portion an angle so that the piston ring is not sealing
there.
Preferably is said cylinder sleeve fastened and sealed by a snap-lock in the
wall of the housing .
Preferaby is the embodiment provided within the coupling section a sealing
means for sealing the valve
actuator onto a valve with a spring-force operated valve core pin.
According to an embodiment of the invention there is also provided a valve
connector, coupled to a
handpump, a foot pump, a car pump, a pressure vessel or a compressor, for
inflating vehicle tires,
comprising a valve actuator of any of claims 1 to 16.
According to an embodiment of the invention there is also provided a pressure
vessel or a hand pump
for inflating a vehicle tire, wherein: an integrated valve actuator.
According to an embodiment of the invention there is also provided a valve
actuator in a stationary
construction, such as a chemical plant.
CA 02786315 2012-08-24
CA 02786315 2012-08-24
19597 SUMMARY OF THE INVENTION
In the first aspect, the invention relates to a combination of a piston and a
chamber,
comprising an elongate chamber which is bounded by an inner chamber wall, and
comprising a piston in said chamber to be sealingly movable relative to said
chamber wall
at least between a first longitudinal position and a second longitudinal
position of the
chamber, said combination engaging a rigid surface, enabling said movement,
where said
combination is movable relatively to said surface.
Force providers for enabling the relative movement of the parts of the
combination may move
themselves, and the path of the last mentioned movement does not at my time
comply
exactly with the path of the relative movement of the piston rod, the piston
and the chamber.
Thus the system of the force provider and the combination may provide a
flexibility
somewhere in the system in order to avoid damage. When the force provider may
engaging
the combination with changing forces, and which may also keeping the non-
moving part of
the combination towards a rigid surface, in order to enable said relative
movement, there may
be conflicting demands towards the combination, if said rigid surface also has
the function of
providing reaction forces for the combination. The last mentioned may happen
when a pump
is engaged by a human body, while the pump is beying held down to the rigid
surface e.g. a
floor, by a foot of said user. Specifically when a standing person is using a
floor pump for
pumping a tyre, and specifically if the floor is not in level. The combination
ought therefore
be movable in relation to the rigid surface, in order to follow the path of
the force provider.
Ina second aspect is the problem of noncompliance specifically important when
a
chamber is used with having cross-sections of different cross-sectional areas
at the first and
second longitudinal positions, and at least substantially continuously
different cross-
sectional areas and circumferential lengths at intermediate longitudinal
positions between
the first and second longitudinal positions, the cross-sectional area and
circumferential
length at said second longitudinal position being smaller than the cross-
sectional at said
first longitudinal position - this is also valid in the case where the cross-
sectional area's at
the first and second longitudinal position having a different size, but an
equal
circumferential size.
In an optnuzed embodiment for obtaining the highest level of reduction of
energy, the
chamber of e.g. a floor pump for tyre inflation has a smallest possible cross-
sectional area
at its bottom and a biggest at its top. Thus at the smallest cross-sectional
area is the biggest
16Y
CA 02786315 2012-08-24
force moment engaging the transition from the chamber to the basis of the
pump. The
combination should therefore be movable in relation to the rigid surface, in
order to follow
the path of the force provider-
In a third aspect the combination comprises a basis for engaging the
combination to a rigid surface, enabling the relative movement of the piston
and the
chamber, the combination is rigidly fastened to a basis, said basis is movable
relatively to
said rigid surface.
The basis may have three engaging surfaces on the rigid surface, ensuring a
stable
,10 positioning of the combination, even the rigid surface would not be flat.
The combination
may then turn around any line between two of the three engaging surfaces. This
however is
a poor solution, as the path of a human force provider normally is a 3-
dimensional path.
And compensation for a positioning of the combination when said surface is not
in level,
cannot be obtained by this solution. And, in the case of floor pumps for tyre
inflation.is
normally the foot of a user pressing the basis of the pump towards the rigid
surface, whiich
might prolubite said movement(s).
In a fourth aspect the combination comprises a basis for engaging the
combination to a rigid surface, enabling the relative movement of the piston
and the
chamber, the combination is flexibly fastened e.g. by means of an elastically
deformable
bushing, to said basis.
This solution, combined with a basis with three engaging surfaces, is an
optimized solution
which complies to all demands: the path of the combination maybe any path
which is used
by the force provider (e.g. user), while the basis is standing on the surface,
held down e.g.
by the foot of teh user. Not only can a rigid surface, not in level, be
compensated, so that
the combination, but not the basis, still is beying perpendicular water, the
user of the floor
pump is able to initiate any path during the stroke. After use may the
combination
automatically coming back to it rest position, namely perpendicular the rigid
surface.
Alternative technical solutions for said bushing are of course possible, e.g.
a ball joint at
the end of the cylinder, holding within a ball baring of the basis - the ball
may be
combined with a spring, which limits the deflection of the combination, and
returns a
deflection to default after use. This solution (not shown) may be more
expensive than the
bushing.
CA 02786315 2012-08-24
In a sixth aspect, the combination may be joined together with the basis
by means of an elastically deformable bushing. The bashing is mounted in a
hole of the
basis, and the chamber is mounted in the hole of the bushing, or vice
versa..With
appropriate fittings, the combination may be assembled in the basis without
being able to
move in the longitudinal direction. The combination may at least now rotate in
the bushing
relative to the basis, and thus relative to the rigid surface. The deflection
of the
combination is deforming the flexible wall of the bushing. The well thickness
of the
bushing may be much bigger than the wall thickness of the chamber, enabling
substantial
deflection angles of the chamber.
Moreover, it might be possible that the fitting is of such a character, that
it may also hold
the forces of the combination in relation to the basis during the stroke,
incl. the ends of the
stroke, so that a translation in the longitudinal direction of the combination
relative to the
basis is prevented.
In a seventh aspect, an improved bushing may have a protrusion on its
top, which is connected to the top of the basis. This prevents the bushing to
move in a
direction towards the basis. By adding another protrusion on the inside of the
bushing or at
the outside of the combination, combined with a groove the combination and
bushing,
respectively a possible translation of the combination to and from the basis
may be
prevented.
Moreover, the elastically deformable bushing may serve as the soft stop of the
combination, when the piston and/or the chamber is reaching its end point of
the
movement. This function makes in classic floor pumps for tyre inflation the
spring on the
piston rod, between the handle and the cap superfluous-
In a eigth aspect, the combination comprising an elongate chamber which
is bounded by an inner chamber wall, and comprising a piston in said chamber
to be
sealingly movable relative to said chamber wall at least between a first
longitudinal
position and a second longitudinal position of the chamber, said combination
engaging a
rigid surface, enabling said movement, where the combination comprises a
piston rod, said
piston rod guided by a guiding means connected to the combination, e.g. the
cab, said
guiding means is movable relatively to the chamber.
P-'6 I G ~
CA 02786315 2012-08-24
This is also valid for piston-chamber combinations with differing cross-
sectional area`sand
eqaul of differing cicamferentiual sizes.
The gadding means may be comprising a washer with a small hole with an
appropriate
filling with the piston rod, while this washer may be movable within a bigger
hole within
the cap: the piston rod may mainly translate in a transversal direction of teh
combination.
The washer may come back to its default position by means of a sprung-force
e.g. an 0-
ring between the hole in the cab, and the outside of the guiding means.
The size of the last mentioned hole is determing the deflection degree of the
piston rod,
together with how much the construction of the piston is allowing it. If the
piston rod is
rigidly fastened to the piston, the construction of the piston determines the
deflection
degree. If e.g. a ball joint is applied between the piston and the piston rod,
the deflection
degree is only determined by the guiding means.
In a nineth aspect, in order to allow a deflection of the piston rod in
relation to the
longitudinal centre axis of the rest of the combination, the contact surface
of the guiding
means may be circular line, e.g. by a convex cross-sectional inner wall of the
hole in the
guiding means.
In a tenth aspect, the piston may be rounded off, so as to comply to the
movement
of the piston rod, or the connection of the piston to the piston rod maybe
flexible, turnable.
hr the eleventh aspect, the invention relates to a combination of a piston and
a
chamber, wherein:
- the centre line of the portions of the handle, positioned opposite the
centre axis of
the combination have an in between angle different from 1800.
The centre lines of the hands of a user when operating a handle of a pump have
different
positions, depending on how the handle is beying gripped by the hand(s).
In the case of classic floor pumps, with cylinders with circular cross
sections of constant size,
high working forces may occur. If relatively high forces are to be transferred
from the arm of
the user through the hand, connected to this arm, the hand will be best
positioned in relation
to the ann, when no force moments would arise. This is obtained if the
longitudinal axis of
CA 02786315 2012-08-24
the arm goes through the center point of the axis of a portion of the handle,
the handle
gripped by the hand, connected to the arm.
Due to the relative big size of the force, the grip of the hand on the handle
ought to be firm -
this may be done by a hand curve like an open fist: the design of the handle
may comprise a
portion which has circular cross sections. The sizes of the sections may vary,
depending on
the distance to the centre axis of the piston chamber combination.
A preferred angle between the portions of the handle may in a plane
perpendicular the centre
axis of the piston-chamber combination be 180 . However, it may also be
different from 180 .
Additionally may the angle be in a plane which comprises said centre axis less
than 180 , In
order to avoid the hands from gliding from these protions, stops may be
provided for- these
may also be used for the force transfer. The other options, 180 and more than
1800 may of
course also occur.
In the case of innovative floor pumps with a chamber with transversal cross
sections
of varying sizes between two positions of the chamber in a longitudinal
direction, the forces
may be low. If relatively low forces are to be transferred from an arm of the
user through a
hand, connected to said anti, the hand may be positioned in relation to the
anti, so that a
certain force moment may arise. The contact area is that of an open hand. The
handle may be
designed with a cross section bounded by the curve of e.g. an ellips. The axis
perpendicular
the centre axis of the piston-chamber combination may be larger than the axis
parallel to said
axis.
Preferred angles between the two portions of the handle in a plane
perpendicular to the centre
axis of the piston-chamber combination maybe bit less than bit bigger (best!)
than 180 .
These positions of the portions of the handle comply to the rest position(s)
of the hand(s).
Both positions may be obtained by one handle design, if the handle may be able
to bun
around the centre axis of the piston-chamber combination.
In order to avoid the existance of a force moment, a line through the centres
of both portions
of the handle in a plane perpendicular the centre axis of the piston-chamber
combination cut
the last mentioned axis.
In a plane which comprises the centre axis of the piston-chamber combination
the angle may
be 180' or less, dr different than that.
The conical shape of the cylinder may provide a substantial reduction of the
size
CA 02786315 2012-08-24
of the working force. By a special arrangement is the shape of the conical
cylinder in the
longitudinal direction of the chamber formed in such a way, that the force on
the handle
remains constant during the stroke. This force may be altered when a valve is
opening late,
e.g. due to the fact that the valve piston is sticking on the valve seed, or
that there be
dynamic frictions, e.g. due to small sizes of cross sections of channels -
thus by forces
originated by other sources than the shape of the chamber. Additionally may
the friction of
the piston to the wall of the chamber alter during the stroke, due to a change
in size of the
contact area. The shape of the cylinder shown in the longitudinal direction in
all relevant
drawings of this patent application is made in the above mentioned way while
the
transversal cross-sections of the conical cylinder are circular - also this is
shown in
relevant drawings. The limitation to the shape is the smallest size of the
piston.
Thus, the invention also relates to a pump for pumping a fluid, the pump
comprising:
a combination according to any of the above aspects,
- incurs for engaging the piston from a position outside the chamber,
- a fluid entrance connected to the chamber and comprising a valve means, and
- a fluid exit connected to the chamber.
In one situation, the engaging means may have an outer position where the
piston is
in its first longitudinal position, and an inner position where the piston is
in its second
longitudinal position. A pump of this type is preferred when a pressurised
fluid is desired.
In another situation, the engaging means may have an outer position where the
piston is in its second longitudinal position, and an inner position where the
piston is in its
first longitudinal position. A pump of this type is preferred when no
substantial pressure is
desired but merely transport of the fluid.
In the situation where the pump is adapted for standing on the floor and the
piston/engaging means to compress fluid, such as air, by being forced
downwards, the largest
force may, ergonomically, be provided at the lowest position of the
piston/engaging
means/bandle. Thus, in the first situation, this means that the highest
pressure is provided
there. In the second situation, this merely means that the largest area and
thereby the largest
volume is seen at the lowest position. However, due to the fact that a
pressure exceeding that
in the e.g. tyre is required in order to open the valve of the tyre, the
smallest cross-sectional
area may be desired shortly before the lowest position of the engaging means
in order for the
io
CA 02786315 2012-08-24
resulting pressure to open the valve and a larger cross-sectional area to
force more fluid into
the tyre (See Fig. 2B).
Also, the invention relates to a shock absorber comprising:
a combination according to any of the combination aspects,
- means for engaging the piston from a position outside the chamber, wherein
the
engaging means have an outer position where the piston is in its first
longitudinal position,
and an inner position where the piston is in its second longitudinal position.
The absorber may further comprise a fluid entrance connected to the chamber
and
comprising a valve means.
Also, the absorber may comprise a fluid exit connected to the chamber and
comprising a valve means.
It may be preferred that the chamber and the piston forms an at least
substantially
sealed cavity comprising a fluid, the fluid being compressed when the piston
moves from the
first to the second longitudinal positions.
Normally, the absorber would comprise means for biasing the piston toward the
first
longitudinal position.
Finally, the invention also relates to an actuator comprising:
a combination according to any of the combination aspects,
means for engaging the piston from a position outside the chamber,
- means for introducing fluid into the chamber in order to displace the piston
between
the first and the second longitudinal positions.
The actuator may comprise a fluid entrance connected to the chamber and
comprising a valve means.
Also, a fluid exit connected to the chamber and comprising a valve means may
be
provided.
Additionally, the actuator may comprise means for biasing the piston toward
the
first or second longitudinal position.
CA 02786315 2012-08-24
19597-1 SPECIFICALLY PREFERRED EMBODIMENTS
According to an embodiment of the invention, them is provided a piston-chamber
combination
comprising an elongate chamber which is bounded by an inner chamber wall, and
comprising a piston
in said chamber to be sealingly movable relative to said chamber well at least
between a first
longitudinal position and a second longitudinal position of the chamber,
wherein the combination is
flexibly fastened to a basis for engaging the combination to a rigid surface,
the combination being
movable relatively to said surface wherein the combination is flexibly
fastened to the basis by means
of an elastically flexible bushing.
Preferably is the elastically flexible bushing mounted in a hole in the basis
and the cylinder is mounted
in a hole in the bushing.
Preferably is the bushing provided with a groove cooperating with a
corresponding protrusion on the
cylinder.
Preferably is the bushing provided with a protrusion cooperating with a
corresponding groove on the
cylinder.
Preferably comprises the bushing a protrusion connected to the top of the
basis.
Preferably is the wall thickness of the bushing bigger than the wall thickness
of the chamber.
Preferably is the basis provided with three engaging surfaces for engaging a
rigid surface.
Preferably has the chamber cross-sections of different cross-sectional areas
and different
circumferential lengths at the first and second longitudinal positions, and
continuously differing cross-
sectional areas and circumferential lengths at intermediate longitudinal
positions between the first and
second longitudinal positions, the cross-sectional area and circumferential
length at said second
longitudinal position being smaller than the cross-sectional area and
circumferential length at said first
longitudinal position, wherein the piston means can change dimensions thereby
providing for different
cross-sectional areas and circumferential lengths of the piston means adapting
the same to said
different cross-sectional areas and different circumferential lengths of the
chamber during the relative
movements of the piston means between the first and second longitudinal
positions through said
intermediate longitudinal positions of the chamber.
Preferably has the chamber cross-sections of different cross-sectional areas
and equal circumferential
lengths at the first and second longitudinal positions, and continuously
differing cross-sectional areas
I ~1_
CA 02786315 2012-08-24
and circumferential lengths at intermediate longitudinal positions between the
first and second
longitudinal positions, the cross-sectional area and circumferential length at
said second longitudinal
position being smaller than the cross-sectional area and circumferential
length at said first longitudinal
position, wherein the piston can change dimensions thereby providing for
different cross-sectional
areas and circumf tial lengths of the piston adapting the same to said
different cross-sectional areas
and equal circumferential lengths of the chamber during the relative movements
of the piston mesas
between the first and second longitudinal positions through said intermediate
longitudinal positions of
the chamber.
Preferably is the piston-chamber combination a pump, comprising a means for
engaging the piston
from a position outside the chamber, and wherein a fluid exit and a fluid
entrance comprising a valve
means are connected to the chamber.
Preferably is the piston-chamber combination a shock absorber comprising means
for engaging the
piston from a position outside the chamber, wherein the engaging means have an
outer position whom
the piston is at the first longitudinal position of the chamber, and an inner
position where the piston is
at the second longitudinal position, wherein the chamber and piston form a
sealed cavity comprising a
fluid, which is compressed when the piston moves from the first to the second
longitudinal position.
Preferably is the piston-chamber combination an actuator comprising means for
engaging the piston
from a position outside the chamber, and means for introducing fluid into the
chamber in order to
displace the piston between the first and second longitudinal position.
CA 02786315 2012-08-24
19597-2 SPECIFICALLY PREFERRED EMBODIMENTS
According to an embodiment of the invention, there is provided a piston-
chamber combination
comprising an elongate chamber which is bounded by an inner chamber wall, and
which comprises a
piston means in said chamber to be sealingly movable relative to said chamber
wall at least between a
first longitudinal position and a second longitudinal position of the chamber,
said combination
engaging a rigid surface, where the combination comprises a piston rod running
through a cap capping
the chamber, wherein the piston rod is guided by a guiding means movably
connected to the cap.
Preferably is the guiding means a washer with an opening fitting around the
piston rod, the washer
being held within the cap between two surfaces and wherein a flexible firing
is held within the cap in
a space between the surfaces and the guiding means, wherein the cross
sectional area of the space is
bigger than the cross-sectional area of the 0-ring.
Preferably comprises said guiding means a convex guiding surface guiding the
piston rod.
Preferably is the piston rounded offat the connection with the wall of the
chamber.
Preferably is the connection of the piston rod to the piston (44) flexible.
Preferably is the piston-chamber combination is a pump, comprising a means for
engaging the piston
from a position outside the chamber, and wherein a fluid exit and a fluid
entrance comprising a valve
means are connected to the chamber.
Preferably is the piston-chamber combination a shock absorber comprising means
for engaging the
piston from a position outside the chamber, wherein the engaging meaus have an
outer position where
the piston is at the first longitudinal position of the chamber, and an inner
position where the piston is
at the second longitudinal position, wherein the chamber and piston form a
sealed cavity comprising a
fluid, which is compressed when the piston moves from the first to the second
longitudinal position.
Preferably is the piston-chamber combination an actuator comprising means for
engaging the piston
from a position outside the chamber, and means for introducing fluid into the
chamber in order to
displace the piston between the first and second longitudinal position.
Preferably has the chamber cross-sections of different cross-sectional areas
and different
circumferential lengths at the first and second longitudinal positions, and
continuously differing cross-
sectional areas and circumferential lengths at intermediate longitudinal
positions between the first and
second longitudinal positions, the cross-sectional area and circumferential
length at said second
1~H
CA 02786315 2012-08-24
longitudinal position being smaller than the cross-sectional area and
circumferential length at said fast
longitudinal position, wherein the piston means can change dimensions thereby
providing for different
cross-sectional areas and circumferential lengths of the piston means adapting
the same to said
different cress-sectional areas and different circumferential lengths of the
chamber during the relative
movements of the piston means between the fast and second longitudinal
positions through said
intermediate longitudinal positions of the chamber.
Preferably has the chamber cross-sections of different cross-sectional areas
and equal circumferential
lengths at the first and second longitudinal positions, and at least
substantially continuously differing
cross-sectional areas and circumferential lengths at intermediate longitudinal
positions between the
first and second longitudinal positions, the cross-sectional area and
circumferential length at said
second longitudinal position being smaller than the cross-sectional area and
circumferential length at
said fast longitudinal position, wherein the piston can change dimensions
thereby providing for
different cross-sectional areas and circumferential lengths of the piston
adapting the same to said
different cross-sectional areas and equal circumferential lengths of the
chamber during the relative
movements of the piston means between the first and second longitudinal
positions through said
intermediate longitudinal positions of the chamber.
CA 02786315 2012-08-24
.19618 BRIEF DESCRIPTION OF THE DRAWINGS
e o owing, pre n em en ot- a raven on a escn vn re eoeo o e
drawings wherein: -
!fib
4T
Fig. fA shows a longitudinal crass-section of a chamber with fixed different
areas of the
transversal crass-sections and a first embodiment of the piston comprising a
textile reinforcement with radially-axially changing dimensions during the
stroke - the piston arrangement is shown it the beginning, and at the end of a
t stroke - pressurized - where it his unprcssoriznd its production size.
Fig. ¾B shows an enlargement of the piston of Fig. ftA at the heginning of a
Bunke.
Fig. PoC shows an enlargement of the piston of Fig. RA at the end of a snake.
Fig. 7A shows a laapituclinal emac-section of a. chamber with fixed different
.cis of the
transversal -as-sections and it second embodiment of the piston comprising
a fiber reinforcement ('Trellis Effect') with radially-axially changing
dimensions ,fire elastic material of the will during the snake - the piston
arrangement is shown at the beginning. and at the end or a Bunke -
pressurized - where it has unpressm-ized its production size.
L e.
Pig. XB shows an enlargement of the piston of Fig. 2A at the heginning of a
smoke.
Fig. RC shows an enlargement nt the piston of Fig. 'A at the end of a stroke.
Fig)A shows a longitudinal cross-section of a chamber with fixed different
areas Mile
transversal cross-sections and a third embodiment of the piston etnnprising a
fiber reinforcement (nn 'Trellis Effect') with radially-axially changing
dimensions dining the stroke - the piston
arrangement is slwwn at the beginning, and at the end of a stroke where it bas
its production size.
Fig. RD shows an enlargement of the piston of Fig. RA it the bcgimiing of a
stroke.
Fig AC zhowc n enlargement or the piatae of Fib sA ni site sell gar a et
roke.
Wig. 7 RU shows it top vidw of the piston of FigX. RA with a reinforcement in
[he wall in planes
through the central axis of the piston - left. at the first longitudinal
position,
right: at the sewncl longitudinal position.
Fig. 8E shows it top view of the piston of Fig. i(A having reinforcements in
the skin in planes
partly through the central axis and partly outside the central axis- left: at
the -
first longitudinal position, right: at the second Iongitoclinal position.
CA 02786315 2012-08-24
CA 02786315 2012-08-24
Fig. 4 shows a non-moving expandable piston inside a chamber with walls, which
are parallel
to the centre axis, while there are no pressure differences in the chamber
between both
sides of said piston.
Fig. 5A shows the piston of Fig. 4, instantaneously non-moving inside a
chamber with a
conical shaped wall, when the piston is beginming to expand- the movable cab
is
moving toward the non-movable cab.
Fig. 5B shows the piston of Fig. 5A, instantaneously non-moving, and thereby
expanding,
so that the contact area of the piston wall with the wall of the chamber
increases at
second longitudinal positions of said contact area-the movable cab is non-
moving.
Fig. 5C shows the piston of Fig. 5B, instanteneously non-moving, and thereby
expanding,
so that the contact area of the piston wall with the wall of the chamber
decreases at
second longitudinal positions of said contact area, while the contact area of
the piston
wall with the wall of the chamber increases at first longitudinal positions of
said
contact area -the movable cab is non-moving.
Fig. 5D shows the piston of Fig. 5C, where the non-movable cap is
instantaneously
beginning to move from second to first longitudinal positions, thereby moving
the
piston in the same direction.
Fig. 5E shows the piston of Fig. 5D, where the movement of the piston is
decreasing due to a
increasing contact area.
Fig. 6A shows an expandable piston moving in a closed cone shaped chamber.
Fig. 6B shows an expandable piston moving in a closed cone shaped chamber,
where said
chamber on both sides of the piston is communicating with the surrounding's
atmosphere.
Fig. 6C shows an expandable piston moving in a closed cone shaped chamber,
when said
chamber on both sides of the piston is communicating with each other through a
closed
channel outside said chamber.
Fig. 6D shows an expandable piston moving in a closed cone shaped chamber,
where said
chamber on both sides of the piston is communicating with each other through a
closed
channel inside said piston.
Fig. 6E shows an expandable piston moving in a closed cone shaped chamber,
where said
chamber on both sides of the piston is communicating with each other through a
4t- (~S
CA 02786315 2012-08-24
channel between the chamber wall and the piston wall
Fig. 6F shows the expandable piston of Fig. 6E having a duct in the contact
surface of the wall
of the piston and the wall of the chamber.
Fig. 60 shows the transversal cross-section of the piston rod of Fig. 6F and
the view on the
actuator piston from a 1'r longitudinal position.
Fig. 7A shows an enlargement of the piston of Fig. 1A at the end of a stroke,
pressurized, but
non-moving, due to the wall being parallel to the centre axis.
Fig. 7B shows the piston of Fig. 7A, at a point where the centre of the wall
of the piston has a
positive angle in relation to the centre axis, so that the container is moving
towards a
first position.
20
30
st~-
20 F9.6C nhe v -nrenntecgemep
Fig. ¾b shows a 3-dimensional drnwing of a reinforcement matrix of an sleds
textile material, positioned in the watt of the container when the
contniner is to be expanded.
Fig. shows the pattern of Fig. 6D when the wall of Hie container has been
26 expanded,
Fig, 7fF shows a 3-dimensions] drawing of a reinfocement pattern of an
inelastic
textile mateinl, positioned in Use wall of the container when the
piston is to be expanded,
>F#g: 6H--' :mac cmrtainertrtFOOOl
30 expanded,
Fig:5I3----shows-predxetier-deters-wf-n-pistoo-wih-a tooti e-soissfaoaemen[_
Fq~
FrSg ykowb 0_ &3e'6:õc.4t2a Wl fL5 9') foss -11
Il- a- 0 sh 5e b,,,_ 0.,d AJWw'-4 0- 0,U.
CA 02786315 2012-08-24
Fig. 9A shows a tongitndinai etus-section of s chamber with fixed diffnnnt
areas of the
isomorr al crass-sections anti a fourth embodiment of the piston enmprising
an "oetopos" device, limiting stretching of the container wall by temacles,
which may be intlaisble, -the piston arrmgemem is shown at the beginning.
and at the end of n stroke whore it has its production size.
Fig. 911 shows an enlargement of the piston of Fig. 9A at tot heginning of a
arms.
Fig. 9C shows in enlargement of the piston of Fig_ 9A at ncI, no or a stroke.
Gm'.~'.Ca-C-
FL clsmb~= 1
CA 02786315 2012-08-24
jer 181
CA 02786315 2012-08-24
Fig. tOA shows a piston-chamber combination where a pressurized ellipsoYde
shaped piston is
moving from a second longitudinal position to a first longitudinal position,
enlarging the internal volume of said piston, the enclosed space having a
fixed volume, thereby reducing the internal pressure of said piston, the
piston may change its shape into a sphere - the dashed lines at both ends
show the outer contour of said piston, where the chamber has a wall parallel
to the centre axis of said chamber, in the middle the size of said piston
compared to where same size of said piston in Fig. 10B occurs, thereby
showing that the piston in Fig. 10B may engagingly be connected to the wall
of said chamber, while in Fig.10A this is sealingly connected.
Fig. IOB shows the piston-chamber combination of Fig.10A where the internal
pressure of the piston additionally has been decreased by changing the
volume of the enclosed space, at a furthest first longitudinal position or
during its return to the second longitunal position, thereby changing the size
of said piston, adapting it contineously to the size of the chamber, in order
to
avoid jamming.
Fig. IOC shows a piston-chamber combination as that of Fig. IOA,B, but where
the
internal pressure of the piston alternatively has been decreased by removing
fluid from the enclosed space, at a furthest first longitudinal portion or
during its return to the second longitunal position, thereby changing the size
of said piston, adapting it contineously to the size of the chamber, in order
to
avoid jamming.
Fig. I OD shows the process of Fig.1 OA, when the piston is a sphere type, as
produced
at a second longitudinal position.
Fig, 10E shows the process of Fig. I OB, when the piston is a sphere type, as
produced
at a second longitudinal position.
Fig. I OF shows the process of Fig. IOC, when the piston is a sphere type, as
produced
at a second longitudinal position.
Fig. IOG shows the process of Fig. IOA, with the exception that the enclosed
space
has a decreasing size during the moving from the 2' to the Ia longitudinal
A-1 (82
CA 02786315 2012-08-24
position, so that the use of the pressurized medium per stroke is being
reduced.
Fig. 1011 shows the comparable process of that of Fig. I OB.
Fig. 101 shows the comparable process of that of Fig. IOC
Fig. 1OJ shows the process of Fig. l OD, with the exception that the enclosed
space
has a decreasing size during the moving from the 21a to the 1n longitudinal
position, so that the use of the pressurized medium per stroke is being
reduced.
Fig. 1OK shows the comparable process of that of Fig. IOE.
- Fig. 1OL shows the comparable process of that of Fig. I OF.
Fig. I OM shows schematically a motor of the configuration of Figs. 12A and
12C?
having a propulsion system comprising an expandable inflatable actuator
piston rotating in a circular chamber, having a circleround centre axis,
around the centre of the centre axle of said motor.
Fig. ION shows schematically a motor of Fig. 13A, 13B having a propulsion
system
comprising (e.g) 5 non-moving expandable inflatable actuator pistons, within
a rotating circular chamber, said chamber having a centre line which is
concentrical to the centre of rotation, comprising four sub-chambers in
continuation of each other, having continuing differing transitional cross-
sectional area's and circumferences, said chamber is rotating around a main
axle through the center of said axle
CA 02786315 2012-08-24
183
CONSUMPTION TECHNOLOGY
Fig. 11A shows schematically a motor having a propulsion system comprising an
expandable inflatable actuator piston, and a two step piston pumping system,
within an elongated chamber having continuing differing cross-sectional area's
and circumferences, all assembled on a crankshaft axle, and a pressure storage
vessel, and an electric starter motor, the smallest pump and starter motor
being
energized by among others solar energy.
Fig. 11 B shows schematically the controting means and the pressure management
for
the motor of Fig. 11A.
Fig. I1C shows some worked out mechanical assemblies of the motor of Figs. 11
A and
11B, where the main cylinder is not moving.
Fig. 11D shows the pressure management of the inflatable actuator piston on
the joint
of the crankshaft and the connecting rod, shown in Fig. 11C.
Fig. 11E shows a detail of the joint of the piston rod and the connecting rod,
shown in
Fig. 11C.
Fig. 11F shows a detail of the suspension of the crankshaft, and the channel
inside said
crankshaft, shown in Figs. 1IA and 11B.
ENCLOSED SPACE VOLUME TECHNOLOGY
Fig. 1IG shows an alternative method of managing the pressure change in the
inflatable
actuator piston, by changing the volume of the enclosed space through a
piston of a second piston-chamber combination, and an additional adjustment
of the pressure through a piston of a third piston-chamber combination for
managing the speed/power of said motor, without a constant repressuration of
the pressure storage vessel, for pressurizing the 2-way actuator for said
change of volume of the enclosed space.
Fig. 11H shows the configuration of Fig. 1I G, where a constant repressuration
of the
pressure storage vessel is done by a cascade of pumps, shown in e.g. Fig.
11A.
Fig. III shows a partially worked out one cylinder motor, based on the concept
shown
in Fig. IIH, where the velocity controller and the ESVT-pump are being
19
CA 02786315 2012-08-24
powered by a 2-way actuator, which is powered by a battery; the pump for
re-pressurating the pressure storage vessel is being powered by a separate
electric motor, powered by a battery- the respective power lines are clearly
shown - auxilliarly power sources are according to Figs. 15A,B,C,E,F of
which at least one may charging said batteries.
Fig. 11J shows a partially worked out two cylinder motor, based on Fig. 111,
where
each actuator piston-chamber combination has a separate velocity controller
and an ESVT-pump - said velocity controllers are communicating with each
other. -
- Fig. IIJ left shows a scaled up of the left part of Fig. 11J.
Fig, ItJ right shows a scaled up of the right part of Fig. 11J.
Fig. 11K shows a partially worked out one cylinder motor, based on the concept
shown
in Fig. 1 IH, where the ESVT-pump of the actuator piston now is being
powered by a crankshaft, the last mentioned being powered by an electric
motor, which is powered by a battery - the velocity controller (2 way-
actuator) is according the one of Fig. 11H; the pump for re-pressurating the
pressure storage vessel is being powered by a separate electric motor,
powered by a battery; auxilliarly power sources are according to Figs.
15A,B,C,E,F of which at least one may charging said batteries.
Fig. 11L shows a partially worked out two cylinder motor, based on Fig. 11 K.
One
crankshaft is being used for the ESVT-pumps, one for each actuator-piston
combination. The velocity controllers, one for each actuator piston are
communicating with each other; the pump for re-pressurating the
pressure storage vessel is being powered by a separate electric motor,
powered by a battery; auxilliarly power sources are according to Figs.
15A,B,C,E,F of which at least one may charging said batteries.
Fig. 11 L left shows a scaled up of the left part of Fig. I1 L.
Fig, 11 L right shows a scaled up of the right part of Fig. I I L.
Fig. I IM shows a partially worked out one cylinder motor, based on the
concept shown
in Fig. 111, where the ESVT-pump for the actuator piston chamber
combination now is being powered by a camshaft, said camshaft driven by an
-i-sy (85
CA 02786315 2012-08-24
electric motor, powered by a battery; the velocity controller is a 2-way
actuator, which is communicating with a speeder. The pump for
repressurating the pressure storage vessel is being powered by a separate
electric motor, powered by a battery; auxilliarly power sources are according
to Figs. 15A,B,C,E,F of which at least one may charging said batteries.
Fig. 1IN shows a partially worked out two cylinder motor, based on Fig. 1IM -
one
camshaft is used for the ESVT-pumps, one for each actuator piston-chamber
combination.The velocity controllers, one for each actuator piston, are
communicating with each other; the pump for repressurating the pressure
- storage vessel is being powered by a separate electric motor, powered by a
battery; auxilliarly power sources are according to Figs. 15A,B,C,E,F of
which at least one may charging said batteries.
Fig. 11N left shows a scaled up of the left part of Fig. l IN.
Fig, 11N right shows a scaled up of the right part of Fig. 1IN.
Fig. I to shows a partially worked out one cylinder motor, based on the
concept shown
in Fig. 11K, where the ESVT-pump of the actuator piston-chamber is being
powered by a crankshaft, which is directly driven by the auxilliarly power
from a gas (e.g. air) cooled combustion motor, using Hz, derived by
the electrolyses of H20, said electrolyses powered by a battery; the pump
which is re-pressurating the pressure storage vessel is additionally directly
driven by said combustion motor; the velocity controller is powered by a 2-
way actuator, powered by a battery; the batteruies according to Fig. 15D are
being charged by an alternator, which is mounted on the main motor axle.
The generated heat of said combustion motor may be used e.g. for
warming up the vehicle interior.
Fig. 11P shows a partially worked out two cylinder motor, based on Fig. I to,
where
the ESVT-pumps, one for each actuator piston-chamber combination, are
being powered by a crankshaft, which is directly driven by the auxilliarly
power from a forced liquid cooled combustion motor, using H2, derived by
the electrolyses of H2O, said electrolyses powered by a battery; the pump
pump, which is re-pressurating the pressure storage vessel is directly driven
I"
CA 02786315 2012-08-24
by said combustion motor; the velocity controllers, one for each actuator
piston chamber combination are powered by a 2-way actuator, are
communicating with each other, and are powered by a battery; the batteries
according to Fig. 15D are being charged by an alternator, which is mounted
on the main motor axle. The generated heat of said combustion motor may be
used e.g. for warming up the vehicle interior.
Fig. 11P left shows a scaled up of the left part of Fig. 11P.
Fig, I IP right shows a scaled up of the right part of Fig. 11P.
Fig. 11Q shows a partially worked out one cylinder motor, based on the concept
shown
in Fig. IIK, where the ESVT-pump of the actuator piston-chamber
combination are being powered by a camshaft which is directly driven by the
auxilliarly power from a forced gas (e.g. air) cooled combustion motor, using
H2, derived by the electrolyses of H2O, said electrolyses powered by a
battery; the pump, which is re-pressurating the pressure storage vessel is
directly driven by said combustion motor; the velocity controller is powered
by a 2-way actuator, powered by a battery; the batteries according to Fig.
15D are being charged by an alternator, which is mounted on the main motor
axle. The generated heat of said combustion motor may be used e.g. for
warming up the vehicle interior.
Fig. I IR shows a partially worked out two cylinder motor, based on Fig. I IQ -
where the ESVT-pumps, one for each actuator piston-chamber combination,
are being powered by a camshaft, which is directly driven by the auxilliarly
power from a gas (e.g. air) forced cooled combustion motor, using H2,
derived by the electrolyses of H20, said electrolyses powered by a battery;
the pump which is re-pressumting the pressure storage vessel is directly
driven by said combustion motor; the velocity controllers, one for each
actuator piston-chamber combination are powered by a 2-way actuator, are
communicating with each other, and are powered by a battery; the batteries
according to Fig. 15D are being charged by an alternator, which is mounted
on the main motor axle. The generated heat of said combustion motor maybe
used e.g. for warming up the vehicle interiour.
--(RI-
CA 02786315 2012-08-24
Fig. 11R left shows a scaled up of the left part of Fig. I1R.
Fig. 11R right shows a scaled up of the right part of Fig. 11R.
Fig. 11S shows a detail of the joint of the base of the piston-chamber
combination
1061 of Figs. III - 11R with the main axle of the motor.
Fig. I IT shows a detail of the joint of the connecting rod of the
actuatorpiston and the
crankshaft on the main axle of the motoer according to Figs. 111- I IR.
Fig. 11U shows a detail of thejoint of the base of the piston-chamber
combination
1060 of Figs. 111 - I IR with the main axle of the motor.
Fig. 11 V shows the meehanisme driving a pump of Figs. 11H - I IR, and its
base.
Fig. 11 W shows the connecting joint between the two crankshafts of the 2-
cylinder
motor according to Figs. I IJ, I IL, I 1 N, I IP, IIR.
Fig. 1 I W' shows an improved sealing between the c akshafta of Fig. 11 W.
Fig. I1X shows the connecting joint between the two crankshafts of a 2-
cylinder
motor where the channels of each crankshaft are being separated.
Fig. I IX' shows an improved sealing between the crankshafts of Fig. 11X.
lj 188
CA 02786315 2012-08-24
CONSUMPTION TECHNOLOGY
Fig. 12A shows schematically a motor having a propulsion system comprising an
expandable inflatable actuator piston rotating in a circular chamber, and a
two step piston pumping system, within an elongated chamber having
continuing differing transitional cross-sectional area's and circumferences,
all
assembled on a crankshaft axle, and a pressure storage vessel, and an electric
starter motor, the smallest pump and starter motor being energized by solar
energy, including control means.
It Fig. 12B shows schematically a motor of Fig. 12A having a propulsion system
comprising an expandable inflatable actuator piston moving within a non-
moving chamber, having a centre line which is concentrically the centre of
rotation, comprising four sub-chambers in continuation of each other, having
continuing differing transitional cross-sectional area's and circumferences.
Fig. 12C shows schematically the controlling means and pressure management for
the
motor of Fig. 12B, where the change of the pressure in the actuator piston is
controlled by adding to and removing fluid from the actuator piston
ENCLOSED SPACE VOLUME TECHNOLOGY
Fig. 12D shows schematically the controlling means and pressure management for
the
motor of Fig. 12B, where the change of the pressure in the actuator piston is
controlled by changing the volume of the enclosed space of the actuator
piston.
CA 02786315 2012-08-24
CONSUMPTION TECHNOLOGY
Fig. 13A shows schematically a motor having a propulsion system comprising
more
than one non-moving expandable inflatable actuator pistons in a rotating
chamber, said chamber having a centre line which is concentrically the centre
of rotation, and a two step piston pumping system, within an elongated
chamber having continuing differing transitional cross-sectional area's and
circumferences, all assembled on a crankshaft axle, and a pressure storage
vessel, and an electric starter motor, the smallest pump and starter motor
being energized by solar energy.
Fig. 13B shows the motor of Fig. 13A, wherein the piston pumps of the two step
piston pumping system have been exchanged by rotational pumps, mounted
on the main axle of the motor.
Fig.13C shows schematically a motor of Fig. 13A, 13B having a propulsion
system
comprising nun-moving expandable inflatable actuator pistons, within a
rotating chamber, said chamber having a centre line which is concentrically
the centre of rotation, comprising four sub-chambers in continuation of each
other, having continuing differing transitional cross-sectional area's and
circumferences, said chamber is rotating around an axle through the center of
said chamber.
Fig. 13D shows schematically the suspension of the motor of Fig. 13A, 13B,
incl. a
drive belt.
Fig. 13E shows schematically the controlling means and pressure management for
the
motor of Fig. 13A,13B had, a storage pressure vessel, where the
contineously changing internal pressures of said actuator pistons are
determined by a separate piston-chamber combination for each of said
actuator pistons, computer controlled.
CA 02786315 2012-08-24
ENCLOSED SPACE VOLUME TECHNOLOGY
Fig. 13F shows the pressure management of the inflatable pistons of Fig. 13C,
according to the principle of Fig. 11F, where each actuator piston is managed
by two piston-chamber combinations - one for the contineously changing
pressure and one for the adjustment of the pressure level for adjusting the
speed/power of the motor.
Fig. 13 G shows the pressuration system for the configuration of Fig. 13F.
to
20
30
!Li
CA 02786315 2012-08-24
ENCLOSED SPACE VOLUME TECHNOLOGY
Fig. 14A shows the several stages of an actuator piston, around which a
circular chamber
is running, and what is necessary to change the inside pressure of said
actuator
piston, by changing the volume under a pump piston of a connected chamber.
Fig. 14B shows the configuration of Fig. 14A, where a cam-wheel which is
connected to
the piston rod of the pump piston, is communicating with a cam of an
appropriate profile.
Fig. 14C shows
Fig. 14D shows a moving circular chamber according to Fig. 13A, where the
pressure
in actuator pistons is being defined by the pressure in a piston-chamber
combinationm which has a cam-wheel communicating with the piston of said
piston-chamber combination, said cam-wheel is running over a main axle,
which is comprising a cam with a certain profile.
Fig. 14E shows a rim with its suspension, in which the configuration of Fig.
14D has
been built in, together with an auxilliarly motor, shown as an electric motor,
which is turning said cam profile; communicating to a channel comprising the
enclosed space of said actuator piston is a pressure controller according to
the
configuration of Fig. 16 ("drive by wire"), which is communicating with a
remotely speeder.
Fig. 14F shows an enlarged detail of the cross-section of said piston in said
circular
chamber of Fig. 14E, when the piston is at a first circular position.
Fig. 14G shows an enlarged detail of the cross-section afraid piston in said
circular
chamber of Fig. 14G, when the piston is at a second circular position.
Fig. 1414 shows the configuration of Fig. 14F., wherein between the rim of the
wheel
and said circular chamber has been built in a gearbox, e.g. of the type of a
planet gray.
I q
CA 02786315 2012-08-24
AUXILLIARLY POWER SOURCES
Fig. 15A shows a Hz-fuel eel as electrical power source for repressuration
pump(s) for
pressurizing the pressure storage vessel, the necessary components and the
power lines.
Fig. 15B shows a combustion motor, using H2 as power source, which has been
generated by electrolyses of conductive water-the axle of said combustible
is driving an alternator which is charging a battery -the battery let an
electric motor ran, which is communicating with (a) pump(s), for
- repressuration of the pressure storage vessel.
Fig. 15C shows a combustion motor, using H, as power source, which has been
generated by electrolyses of conductive water - the axle of said combustible
is directly communicating with (a) pump(s) through (a) crankshaft, for
repressuration of the pressure storage vessel.
Fig. 15D shows a combustion motor, using Hz as power source, which has been
generated by electrolyses of conductive water - the axle of said combustible
is directly communicating with (a) rotational pump(s), for repressuration
of the pressure storage vessel.
Fig. 15E shows a capacitator, which is electrically charged, and which is the
power
source for electrical motor(s), which are communicating with (a) pump(s) for
repressuraton of the pressure storage vessel.
30
1 143
CA 02786315 2012-08-24
ESVT - CRANKSHAFT DESIGN - MULTIPLE USE OF COMPONENTS
Fig. 16A shows a scaled up 2-way actuator of the Figs. 11 G-R.
Fig. 16B shows a pre-study of the 2-way actuator of Fig. 16A.
20
30
orgy
CA 02786315 2012-08-24
ESVT - CRANKSHAFT DESIGN- MULTIPLE USE OF COMPONENTS
Fig. 17A shows schematically the two strokes of an actuator piston according
to Figs.
10A,B of a one cylinder motor, where the stroke from a 2n to a 1s0
longitudinal position is the power stroke, and the stroke from the I" to the
2nd
longitudinal position the (powerless) return stroke.
Fig. 17B shows a two cylinder motor ("A" and "B") with strokes according to
Fig.
17A, whereby the crankshaft (comprising of two sob-crankshafts) is
designed, so that the power strokes of each cylinder are moving in opposite
(1800) direction.
Fig. 17C shows a two cylinder motor according to Fig.l 1R, whereby the
combustion
motor here is forced liquid cooled, whereby one of the ESVT-pumps has
been exchanged by an inlet/outlet for one sub-crankshaft, which is
communicating with the ESVT-pump for the other sub-crankshaft, and where
said communcatinn is controlled by valve actuators according to Fig. 210E, of
which motion are initiated by cams of a camshaft, said camshaft being driven
by said combustible motor, and, such that the beginning of the power stroke of
the left cylinder, is synchronized with the beginning of the return stroke of
the
right cylinder; the second enclosed space of one sub-crankshaft has been
separated from the third enclosed space of the other sub-crankshaft.
Fig. 17C 1. shows an enlagement of Fig. 17C left and a diagram of the in-
between
relationship of the connection rods of both actuator pistons.
Fig. 17C r. shows an enlagement of Fig. 17C right.
Fig. 17D shows the middle of the power stroke of the left cylinder, and the
middle of
the return stroke of the right cylinder of the motor according to Fig. 17C.
Fig. 17D 1. shows an enlagement of Fig. 17D left and a diagram of the in-
between
relationship of the connection rods of both actuator pistons.
Fig. 17D r. shows an enlagement of Fig. 17D right.
CA 02786315 2012-08-24
Fig. 17E shows the end of the power stroke of the left cylinder and the end of
the
return stroke of the right cylinder of the motor according to Fig. 17D.
Fig. 17E 1. shows an enlagement of Fig. 17E left and a diagram of the in-
between
relationship of the connection rods of both actuator pistons.
Fig. 17E r. shows an enlagement of Fig. 17E right.
Fig. 17F shows the beginning of the return stroke of the left cylinder and the
beginning of the power stroke of the right cylinder of the motor according to
Fig. 17E.
Fig. 17F I. shows an enlagement of Fig. 17F left and a diagram of the in-
between
relationship of the connection rods of both actuator pistons.
Fig. 17F r. shows an enlagement ofFig_ 17F right.
Fig. 170 shows the middle of the return stroke of the left cylinder and the
middle of
the power stroke of the right cylinder of the motor according to Fig. 17F.
Fig. 17G 1. shows an enlagement of Fig. 17G left and a diagram of the in-
between
relationship of the connection rods of both actuator pistons.
Fig. 17G r. shows an enlagement of Fig. 17G right
Fig. 17H shows the end of the return stroke of the left cylinder and the end
of the
power stroke of the right cylinder of the motor according to Fig. 17G.
Fig. 17H 1. shows an enlagement of Fig. 17H left and a diagram of the in-
between
relationship of the connection rods of both actuator pistons.
Fig. 17H r. shows an enlagement of Fig. 17H right.
13T +
CA 02786315 2012-08-24
ESVT - CRANKSHAFT DESIGN - MULTIPLE USE OF COMPONENTS
Fig. 18A shows a two cylinder motor ("A" and `B") with strokes according to
Fig.17A, whereby the crankshaft (comprising of two sub crankshafts) is
designed, so that the power strokes of each actuator pistons are moving in the
same (00) direction.
Fig. 18A 1. shows an enlagement of Fig. I8A left and a diagram of the in-
between
relationship of the connection rods of both actuator pistons.
Fig. 18A r. shows anenlagement of Fig. I SA right.
Fig. 18B shows a simple configuration of a two cylinder motor according to
Fig.17C,
whereby the combustion motor here is forced liquid cooled, comprising one
ESVT-pump serving both actuator pistons has, the second enclosed space of
one sub-crankshaft is communicating with the third enclosed space of the
other sub-crankshaft,
such that the beginning of the power stroke of the left cylinder, is
synchronized with the beginning of the power stroke of the right cylinder.
Fig. 18B 1. shows an enlagement of Fig. 18B left and a diagram of the in-
between
relationship of the connection rods of both actuator pistons.
Fig. 18B r. shows an enlagement of Fig. 18B right.
Fig. 18C shows the middle of the power strokes of the left and the right
cylinder of the
motor according to Fig. 18B.
Fig. 18C 1. shows an enlagement of Fig. 18C left and a diagram of the in-
between
relationship of the connection rods of both actuator pistons.
Fig. 18C r. shows an enlagement of Fig. 18C right.
Fig. 18D shows the end of the power strokes of the left and the right cylinder
of the
motor according to Fig. 18C.
Fig. 18D 1. shows an enlagement of Fig. 18D left and a diagram of the in-
between
relationship of the connection rods of both actuator pistons.
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CA 02786315 2012-08-24
Fig. 18D r. shows an enlagement of Fig. 18D right.
Fig. 18E shows the beginning of the return stroke of the left and the right
cylinder of
the motor according to Fig. 18D.
Fig. 18E 1. shows an enlagement of Fig. 18E left and a diagram of the in-
between
relationship of the connection rods of both actuator pistons.
Fig. 18E r. shows an enlagement of Fig. I8E right.
Fig. 18F shows the middle of the return stroke of the left and the right
cylinder of the
motor according to Fig. 18E.
Fig. 18F I. shows an enlagement of Fig. 18F left and a diagram of the in-
between
relationship of the connection rods of both actuator pistons.
Fig. 18F r. shows an enlagement of Fig. 18F right.
Fig. 18G shows the end of the return stroke of the left and the right cylinder
of the
motor according to Fig. 18F.
Fig. 180 1. shows an enlagement of Fig. 18G left and a diagram of the in-
between
relationship of the connection rods of both actuator pistons.
Fig. Mr. shows an enlagement of Fig. 18G right.
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CA 02786315 2012-08-24
CT - CRANKSHAFT DESIGN - MULTIPLE USE OF COMPONENTS
Fig. 19A shows a one cylinder motor, based on Figs. 11B, I IC, where some
parts
have been worked out further -the auxilliarly power source is a combustion
motor, which is burning Hz, derived from electrolyses of HzO.
Fig. 19B shows a two cylinder motor, based on Fig. 19A, where the two
cylinders
have been rnirrowedly positioned to the center line of the connection, so that
the 3m enclosed spaces (exits) are communicating with each other through
the connection of the two sub-crankshafts, while the 2"d enclosed spaces
(inlets) are communicating outside said crankshaft with each other (with a
check valve), and where the crankshaft (comprising of two sub-crankshafts)
is designed, so that the power strokes of each actuator piston are moving
simultaneously in the same (0') direction (synchrone), according to the
principle of Fig. 18A.
Fig. 19B I. shows an enlargement of Fig. 19B left.
Fig. 19B r. shows an enlargement of Fig. 19B right.
Fig. 19C shows a two cylinder motor, based on Fig. 19A, where the comparable
enclosed spaces (here the 3r enclosed spaces) have been connected to each
other through the sub-crankshafts, while the 2nd enclosed spaces have been
brought externally together (with a check valve), and where the whereby
the crankshaft (comprising of two sub-crankshafts) is designed, so that the
power strokes of each actuator pistons are moving in the same (180') direction
(asynchrone), according to the principle of Fig. 18A.
Fig. 19C 1. shows an enlargement of Fig. 19C left.
Fig. 19C r. shows a enlargement of Fig. 19C right.
CA 02786315 2012-08-24
l9,
19620 BRIEF DESC I1IFTION OF TflE DRAWINGS
In the following, preferred embodiments of the invention will be described
with reference to
the drawings wherein;.
Fig. 21A shows a longitudinal cross-section of a conical shaped
chamber with constant
maximum work force characteristics of a pump showing the common
(pressure) borders, and the convex and conical shapes of
the sides of the
longitudinal cross-sectional sections between said borders.
Fig. 21B shows the chamber of Fig. 21A (10 Bar overpressure),
and (dashed) the
shape of another chamber (16 Bar overpressure), for the
same chamber -
length
Fig. 22 shows a longitudinal cross-section of a conical shaped
chamber of Fig- 21
showing an expansion chamber as pan of said chamber.
Fig. 23 shows a advanced conical shaped chamber with constant
maximium work
force characteristics of a pump showing the specific
internal concave
transition from the internal conically shaped pan of the chamber to the
straight inside at secind longitudinal positions, which is
paralel to the centre
- - axis of the chamber-
Fig. 24 shows an expandable deformable piston, which will not -
move by itself from
a second longindinal pisiotiea to a first longitudinal
position, because the
internal wall of the chamber of Fig. 23 is parallel to the
centre axis.
Fig. 25 shows a chamber of a constant force type, with a hose
nipple as exit, which
is connected to a hose.
P-r 24sv
CA 02786315 2012-08-24
19630 BRIEF DESCRIPTION OF THE DRAWINGS
In the following, preferred embodiments of the invention will be described
with reference to the
showings wherein:
Fig. 30A shows the circular chamber of Fig. 12B, where a piston is moving in a
non-moving chamber.
Fig. 30B shows the circular chamber of Figs. 13C and 14D where the piston is
not moving, but the chamber, Here is the design of the circular
0 chamber and the sub-chambers identical with the design of Fig. 30A.
Fig. 31 A shows the Fig. 14D, where the section X-X has shown.
Fig. 31B shows an sealed up detail of section X-X of the chamber of Fig. 31A.
MATHEMATICAL DESCRIPTION OF THE CIRCULAR CHAMBER AND A PISTON
15 Fig. 32A shows the wall of the chamber and the orthogonal plane to the base
circle intersects in a circle whose center is at the has circle.
Fig. 32B a section of the boundary of the piston.
Fig. 32C shows the cap geometri - for area and internal volume of the cap we
need need values of a and h only - see formulas (2.1) and 2.2) - the
20 radius of the virtual sphere is given in (23).
Fig. 32D shows the piston with end caps.
Fig. 32E shows the piston with end caps inside a transparent Fermi tube
chamber.
Fig. 32F shows the pure contact area between the piston and the chamber,
25 visible inside the transparent chamber wall.
Fig. 32G shows the contact area between the piston and the choenber.
Fig. 32H shows a section of the chamber wall - the chamber reaction force is
marked by gray - the total force on the section is orthogonal to the
chamber wall - for the section is the value of the force proportional to
30 the (variable) longitudinal length of the shown section and to the internal
pressure of the piston.
Fig. 321 shows the section of Fig. 32H, with an additional section in order to
provide an open view.
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CA 02786315 2012-08-24
Fig. 32J shows Fig. 321, and the red vector is the component of the gray force
in the longitudinal direction.
Fig. 32K shows Fig. 32J, with an additional section in order to provide an
open
view.
Fig, 32L shows Fig. 32J, where the actual sliding force along the wall is
shown
in blue - it is obtained by projecting the red vector orthogonally to the
chamber wall.
Fig. 32M shows Fig. 32L, with an additional section in order to provide an
open
view.
0
CA 02786315 2012-08-24
19640 BRIEF DESCRIPTION OF THE DRAWINGS
In the following, preferred embodiments of the invention will be described
with references to the
drawings wherein:
Fig. 40A shows a longitudinal cross-section of a pump with a piston comprising
support means, an O-ring and a flexible impervious layer, the last
mentioned supported by a foam, at a first longitudinal position.
Fig. 40B shows a detail of the suspension of the support means, 0-ring and the
flexible impervious layer, vulcanised together.
Fig. 40C shows a longitudinal cross-section of the piston of Fig. 40A at a
second
longitudinal position.
Fig. 41A shows top view of the piston of Fig. 40A and a cross-section of the
chamber from a first longitudinal position.
Fig. 41B shows a detail of the suspension on the support means of the 0-ring
and the lying spring of the piston of Fig. 40A.
Fig. 41C shows a transversal cross section of the chamber with the piston of
Fig.
40A at a second longitudinal position.
Fig. 41D shows a bottom view of the piston of Fig. 40A, and cross-section of
the chamber at a rust longitudinal position, showing the spriral erinfor-
ment of the impervious sheet.
Fig. 41E shows a bottom view of the piston of Fig. 40A, and cross-section of
the chamber at a rust longitudinal position, showing the spiral reinfor
ments of the impervious sheet.
Fig. 42A shows a longitudinal cross-section of a piston comprising support
means, an O-ring and a flexible impervious layer, the last mentioned
at a remain angle with the centre axis of the chamber, at a first longitu-
dinal position.
Fig. 42B shows a detail of the suspension of the support means, O-ring and the
flexible impervious layer, vulcanised together.
Fig. 42C shows a longitudinal cross-section of the piston of Fig. 42A at a
second
longitudinal position.
CA 02786315 2012-08-24
Zn5
19650 BRIEF DESCRIPTRION OF THE DRAWINGS
Fig. 50. shows the top view of a foam piston, specifically the suspension of
the
reinforcement pins-
Fig. 51 shows a longitudinal cross-section A-A of a piston made of a PU foam.
Fig. 52 shows a longitudinal cross-section B-B of the piston of Fig. 50
15
25
2ON
CA 02786315 2012-08-24
19650-1 DESCRIPTION OF THE DRAWINGS
In the following, preferred embodiments of the invention will be described
with reference to the
drawings wherein:
Fig. 55A shows the piston at In longitudinal position of an advanced pump,
said
piston is comprising metal pins, which are rotatably fastened by
magnetic force to a holder plate of a holder, which is mounted on the
piston rod.
Fig. 55B shows an enlargement longitudinal cross-section P-P of the holder
plate
mounted on said holder.
Fig. 55C shows an enlargement of the holder plate on the holder from Fig. 55B.
Fig. 55D is showing an enlargement of the protuberance in a reces between the
holder and the holder plate for an improved squeezing of the impervious
layer.
Fig. 55E shows an alternative solution for the reinforcement and the fastening
of
the foam to the one shown in Figs. 55A-D.
Fig. 55F shows an enlargement of the holder plate on the holder from Fig. 55E.
Fig. 55G shows a solution for an automatic clockwise rotation of the
reinforcement pins of the foam when the piston is conning towards a 1"
longitudinal position.
Pig. 55H shows an enlargement of the holder plate on the holder from Fig. 55G.
CA 02786315 2012-08-24
+~j 205'
19660 BRIEF DESCRIPTION OF THE DRAWINGS
Fig. 60 shows a longitudinal view and cross-sections of the ends of a
container type piston
Fig. 61 shows the details of both end of the container type piston of Fig. 60.
Fig. 62 shows the container type piston at the begin and end of a stroke, in a
chamber where
the f on the piston rod is constant (please see 19620).
15
25
35
2,~ 6
CA 02786315 2012-08-24
19660-2 BRIEF DESCRIPTION OF THE DRAWINGS
In the following, preferred embodiments of the invention will be described
with reference to the
drawings wherein:
Fig. 63 shows the forces from an actuator piston to the wall of a longitudinal
chamber.
Fig. 64A shows an ellipsoide type piston in a chamber with a longitudinal
centre
to axis, with a 20 angle.
Fig. 64B shows an ellipsoide type piston in a chamber with a longitudinal
centre
axis, with a 10 angle.
CA 02786315 2012-08-24
2, 7-
19680-2 BRIEF DESCRIPTION OF THE DRAWINGS
In the following, preferred embodiments of the invention will be described
with reference to the
drawings wherein:
Fig. 80A shows a chamber of a pump according to section 19620, with a piston
according to section 19680 on three different longitudinal positions, said
piston wall is comprising a separate rotatable part, which adapt to the
slope of the wall of said chamber, and of which surfaces are sealingly
connected to the wall of the chamber and said piston wall.
Fig. 80B shows a scaled up detail of said contact area's when said piston is
in a
first longitudinal position.
Fig. 80C shows a scaled up detail of the contact area's when said piston is in
a
second longitudinal position.
Fig. 80D shows the separate part when the piston is in a second longitudinal
position.
Fig. 80E shows an alternative sphere shape of the separate part of that shown
in
Figs. 80A-C.
Fig. 80F shows an alternative halfround shape of the separate part of that
shown
in Figs. 80A-C, which has been vulcanized on a (scaled up) piston
according to section 19660. when said piston is in a second longitudinal
position.
Fig. 80G shows the piston according to Fig. 80F, where the separate part is
positioned under a line through the longitudinal middle point of the
flexible wall of said piston.
Fig. 80H shows the piston according to Fig. 80C where the separate part is
positioned under a line through the longitudinal middle point of the
flexible wall of said piston.
Fig. 801 shows the piston of Fig. 80J at a second longitudinal position of the
chamber according to section 19620.
Fig. 80J shows an enlargment of the piston of Fig. 801, as produced.
Fig. 81 A shows a chamber of a pump according to section 19620, with an
inflatable piston according to section 19680 on three different
CA 02786315 2012-08-24
longitudinal positions, said piston wall is comprising two separate
rotatable parts, which adapt to the slope of the wall of said chamber, and
of which surfaces are sealingly connected to the wall of the chamber and
said piston wall.
Fig. 81B shows a scaled up detail of said contact area's when said piston is
in a
first longitudinal position.
Fig. 81C shows a scaled up detail of said contact area's when said piston is
positioned between a first and a second longitudinal position.
Fig. SID shows said (scaled up) piston, which is positioned in a second
longitudinal position.
Fig. 82A shows a chamber of a pump according to section 19620, with an
inflatable piston according to section 19680 on three different
longitudinal positions, said piston wall is comprising two parts, having
different circumferences, where the biggest is comprising the contact
area between the wall of the chamber and the piston wall.
Fig. 82B shows a scaled up detail of said contact area when said piston is in
a first
longitudinal position.
Fig. 82C shows a scaled up detail of said contact area when said piston is
positioned between a first and a second longitudinal position.
Fig. 82D shows said (scaled up) piston, which is positioned in a second
longitudinal position.
Fig. 83A shows the piston of Fig. 82D, comprising a piston rod, uninflated.
Fig. 83B shows the piston of Fig. 83A at a first longitudinal position, being
inflated.
Fig. 83C shows the the piston of Fig. 83B, with a clamp in the piston rod,
holding
the piston in position, when deflated.
Fig. 83D shows the piston of Fig. 83C, when a foam is being inserted through
the
enclosed space of the piston rod.
Fig. 83E shows the piston of Fig. 83D, after insertion and hardening of the
foam,
which has been unclamped thereafter.
Fig. 83F shows the piston of Fig 83E on a second longitudinal position, having
a
pressure sensor and a inflation valve.
Z'q
CA 02786315 2012-08-24
Fig. 83G shows the enlargment of the pressure sensor and the inflation valve
of
the piston of Fig, 83E.
Fig. 83H shows the piston of Fig, 83E on a second longitudinal position, with
a a
pressure sensor and a inflation valve of another type than the one shown
in Fig. 83F or 83G.
Fig. 831 shows the enlargement of the pressure sensor and the inflation valve
of
the piston of Fig, 83H.
Fig. 83J shows the piston of Fig, 83E on a second longitudinal position, with
a a
pressure sensor and a inflation valve of another type than the one shown
in Fig. 83F, 83G or 83H.
Fig. 83K shows the enlargement of the pressure sensor and the inflation valve
of
the piston of Fig, 83J.
Fig. 84A shows the piston of Fig. 83H for e.g. small size use, where a palling
spring is giving a expansion force for the piston wall, besides the force
derived from the inflatable toroid, which communicate with the enclose
space - the pressure side of the pump piston has foam inside, so to keep
expanding that part properly under external pressure.
Fig. 84B shows an improved piston based on Fig. 84A, which has foam inside the
whole piston, communicating through a venting hole to the non-
pressurized outside of the piston, and a separate channel assembled on
the inside of the piston wall, which is communicating with the enclosed
space of said piston.
Fig. 84C shows the piston of Fig. 84A, where the low-pressure side of the wall
of
the piston is a flat cone.
Fig. 84D shows a sphere shaped piston on a second and first longitudinal
position
of a chamber with a separate part on the outer wall as shown in Figs.
80F, 80G, 80J for an ellipsoide type of piston.
Fig. 84E shows a sphere shaped piston with a piston wall, said piston wall is
comprising two parts, having different circumferences, where the biggest
is comprising the contact area between the wall of the chamber and the
piston wall (such as shown in Figs. 82A-D for ellipsoide shaped piston
CA 02786315 2012-08-24
2 CO
types), while the piston is shown on a second and fast longitudinal
position.
Fig. 84F shows a sphere piston with a inflatable torpid as separate part, as
shown
in Fig. 84B for a ellipsoide shaped piston.
CA 02786315 2012-08-24
207 BRIEF DESCRIPTION OF '1 DRAWINGS
-- ~trfbe-fallawing-pfefer>-ed-ea3badimcaissfihe ime~iaa-wi}1-be-desettbed-
wish-referenc~to-he-drawiag-
whereet
The invention is explained in detail below by means of diagrams and drawings.
The following
is shown in the diagrams or drawings - a transversal moss-section means across-
section perpendicular to
the moving direction of the piston andlor tie chamber, while the longitudinal
moss-section is the one in
the direction of said moving direction:
Fig. 101 shows a so-called indicator diagram of a one-stage single working
piston pump with a cylinder and a piston with a fixed diameter.
Fig. 102A shows an indicator diagram of a piston pump according the invention
part A shows the option where the piston is moving, while part B
shows the option where the chamber is moving.
Fig. 102E shows an indicator diagram of a pump according to the invention
where
the transversal cross-section increases again from a certain point of the
(weep stroke, by still increasing pressure.
Fig. 103A shows a longitudinal mess-section of a pump with fixed different
areas
of transversal cross-sections of the pressurizing chamber and a piston
with radially-axially changing dimensions during the stroke - the piston
arrangement is shown at the beginning and at the end of a pump stroke
(first embodiment)-
Fig 103B shows an enlargement of the piston arrangement of Fig. 103A at the
beginning of a stroke-
Fig. 103C shows an enlargement of the piston arrangement of Fig. 103A at the
end
of a Poke-
Fig- 103D shows a longitudinal cross-section of a chamber of a fl...pump
according to the invention with such dimensions that the operating
force remains approximately constant - as a comparison the cylinder
- of an existing low pressure (dotted) and high pressure floor (dashed)
pump are shown simultaneously-
CA 02786315 2012-08-24
Fig_ 104A shows a longiuduml cross-section of a pump with fixed different
areas
of the transversal cross-sections of the pressurizing chamber and a
piston with radially/partially axially changing dimensions during the
stroke -.the piston arrangement is shown at the beginning and at the
end of the pump stroke (second embodiment).
Fig. 104B shows an enlargement of the piston arrangement of Fig. 104A at the
beginning of a stroke.
Fig. 104C shows an enlargement of the piston arrangement of Fig. 104A at the
end
of a stoke.
Fig. 104D shows section A-A of Fig. 104B.
Fig. 104E shows section B-B of Fig. 104C.
Fig. 104F shows an alternative solution for the loading portion of Fig 104D.
Fig. 105A shows a longitudinal cross-section of a pump with fixed different
areas
of the transversal cross-sections of the pressurizing chamber and a
piston with radially-axially changing dimensions during the stroke - the
piston arrangement is shown at the beginning and at the end of the
pump stroke (third embodiment).
Fig- 105B shows an enlargement of the piston arrangement of Fig. 105A at the
beginning of a stroke.
Fig. 105C shows an enlargement of the piston anangement of Fig. 105A at the
end
of a stroke.
Fig. 105D shows section C-C of Fig. 105A.
Fig. 105E shows section D-D of Fig. 105A. -
Fig. 105F shows the pmssurizing chamber of Fig. 1OSA with a piston means with
sealing means which is made of a composite of materials- -
Fig. 105E shows an enlargement of the piston means of fig. 105F during a
stroke.
Fig- 105H shows an enlargement of the piston means of Fig. 105F at the end of
a
stroke, loth while it is still tinder pressure and while it is not anymore
under pressure. -
CA 02786315 2012-08-24
3-2 -
Fig. 106A shows a longitudinal cross-section of a pump with fixed different
areas
of the transversal cross-sections of the pressurizng chamber and
fourth embodiment of the piston with radially-axially changing
dimensions during the stroke - the piston.arrangement.is shown at the
beginning and at the end of the purrlp stroke.
Fig 106B shows an enlargement of the piston arrangement of Fig. 106A at the
beginning of a stroke.
Fig. 106C shows an enlargement of the piston arrangement of Fig. 106A at the
end
of a stroke.
Fig. 106D shows the pressurivng chamber of Fig. 106A and a fifth embodiment of
the piston with radially-axially changing dimensions during the stroke -
the piston arrangement is shown at the beginning and at the end of a
pump stroke.
Fig. 106E shows an enlargement of the piston arrangement of Fig. 106D at the
beginning of a stroke.
Fig. 106F shows an enlargement of the piston anarkgement of Fig. 106D at the
end of a stroke.
Fig. 107A shows a longitudinal cross-section of a pump comprising a concave
portion of the wall of the pressurizing chamber with fixed dimensions
and a sixth embodiment of the piston widt radially-axially changing
dimensions during the stroke - the piston arrangement is shown at the
beginning and at the end of the pump stroke-
Fig. 107B shows an enlargement of the piston arrangement of Fig. 105A at the
beginning of a stroke.
Fig. 107C shows an enlargement of the piston anangement of Fig. 105A at the
end
of a stroke. -
Fig. 107D shows section E-E Mg- 10713-
Fig. 107E shows section F-F of Fig. 1070.
CA 02786315 2012-08-24
2+h
4b I AT
Fig. 107F shows examples of transversal cross sections made by Fourier Series
Expansions of a pressuzny chamber of which the transversal cross
.... ._._....___
sectional area decreases, while the citcwnpherical size remains
constant-
Fig. 107G shows a variant of the pressurizing chamber of Fig.107A, which bas
now a longitudinal cross-section with fixed transversal cross sections
which are designed in such a way that the area decreases while the
circumference of it approxunately remains constant or decreases in a
lower degree during a pump stroke.
Fig. 1071-I shows transversal cross-section G-G (dotted lines) and 1-I H of
the
longitudinal cross section of Fig. 107G
Fig. 1071 shows transversal cross-section G-G (dotted tines) and I-I of the
longitudinal cross section of Fig. 107H.
Fig. 1071 shows a variant of the piston of Fig. 107B, in section H-H of Fig.
107H.
Fig. 107K shows other examples of transversal cross-sections made by Fourier
Series Expansions of a pressurizing chamber of which the transversal
cross-sectional area decreases, while the circumpherical size remains
constant.
Fig. 107L shows an example of an optimized convex shape of the transversal
cross section under certain contraints.
Fig. 107M shows an example of an optimized non convex shape of the transversal
cross section under certain contraints.
Fig. I08A shows a longitudinal cross-section of a pump comprising a convex
portion of the wall of the pressurizing chamber with fixed dimensions
and a seventh embodiment of the piston with radially-axially changing
dimensions during the stroke - the piston arrangement is shown at the
beginning and at the end of a pump stroke.
Fig. 108B shows an enlargement of the piston arrangement of Fig. 105A at the
beginning of a stroke.
CA 02786315 2012-08-24 - - -
Fig. 108C shows an enlargement of the piston arrangement of Fig. 105A at the
end
n.a_strokc- -
Fig_ 109A shows a longitudinal cross-section of a pump with fixed different
areas
of the transversal cross-sections of the pressurizing chamber and an
eight embodiment of the piston with radially-axially changing
dimensions during the stroke - the piston arrangement is shown at the
beginning and at the end of a pump stroke.
Fig. 109E shows an enlargement of the piston arrangement of Fig. 109A at the
beginning of a stroke.
Fig. 109C shows an enlargement of the piston arrangement of Fig. 109A at the
end
of a stroke.
Fig, 109D shows the piston of Fig 10913 with a different tuning arrangement.
Fig. 1 IOA shows a ninth embodiment of the piston similar to the one of Fig
109A
with fixed different areas of the transversal cross-section of the
pressurizing chamber. -
Fig. 1108 shows an enlargement of the piston of Fig. I IOA at the beginning of
a stroke
Fig. I IOC shows an enlargement of the piston of Fig. I tOA at the end of a
stroke.
Fig. 111A shows a longitudinal moss-section of a pump with fixed different
areas
of the transversal cross-sections of the pressurizing chamber and an
tenth embodiment of the piston with radially-axially changing
dimensions during the stroke - the piston arrangement is shown at the
beginning and at the end of a pump stroke
Fig. 111B shows an enlargement of the piston of-Fig. 1IIA at the beginning of
a stroke.
Fig. 1-I1C shows an enlargement of the piston of Fig. 111A at the end of a
stroke.
Fig. 112A shows a longitudinal cross .section of a pump with fixed different
areas
of the transversal cross-sections of the pressurizing chamber and an
eleventh embodiment of the piston with radially-axially changing
CA 02786315 2012-08-24
dimensions during the stroke - the piston arrangement is shown at the
_ _, beginning and at the end of a pump stroke.
Fig. 112B shows an enlargement of the piston of Fig. 112A at the beginning of
a stroke
Fig. 112C shows an enlargement of the piston of Fig. 112A at the end of a
stroke.
Fig. 113A shows a longitudinal cross-section of a pump with variable different
areas of the transversal cross-section of the pressurizing chamber and
a piston with fixed geometrical sizes - the arrangement of the
combination is shown at the beginning and at the end of the pump
stroke.
Fig. 113B shows an enlargement of the arrangement of the combination at the
beginning of a pump stroke.
Fig- 113C shows an enlargement of the arrangement of the combination during
a pump stroke.
Fig. 113D shows an enlargement of the arrangement of the combination at the
end
of a pump stoke.
Fig. 114 shows a longitudinal cross-section of a pump with variable different
areas of the transversal cross-section of the pressurizing chamber and
- a piston with variable geometrical sizes - the arrangement of the
combination is shown at the beginning, during and at the end of the
pump stroke.
CA 02786315 2012-08-24
j Zt}
653 BRIEF DESCRIPTION OF THE DRAWINGS
2is lh inllo ink f d emtiodimentz-of.tke. invention- aitL -described-witl>-
reference-to *h: _
drawings wherein:
Fig. 201A shows a longitudinal cross-section of a non-moving piston in a non-
pressurized cylinder at the first longitudinal position - the piston is shown
in
its production size, and when pressurized.
Fig. 201B shows the contact pressure of the pressurized piston of Fig. 201A on
the wall
of the cylinder.
Fig 202A shows a longitudinal cross-section of the piston of Fig- 201A in a
cylinder at
. the first (right) and second (left) longitudinal position, the piston is non-
pressurized.
Fig. 2028 shows the contact pressure of the piston of Fig. 202A on the wall of
the
cylinder at the second longitudinal position.
Fig. 202C shows a longitudinal cross-section of the piston of Fig. 201A in a
cylinder at
the second longitudinal position, We piston is pressurized on the same
pressure level as the one of Fig. 201A - also is shown the piston at the first
longitudinal position (production) size-
- Fig. 202D shows the contact pressure of the piston of Fig. 202C on the wall
of the
cylinder at the second longitudinal position.
Fig. 203A shows a longitudinal cross-section of a piston of Fig- 201A in a
cylinder at
the first longitudinal position shown in its production size, and pressurized
while the piston is subjected to a pressure in the chamber.
Fig. 203B shows the contact pressure of the piston of Fig. 203A on the wall of
the
cylinder.
-- Fig. 204A shows a longitodinal cross-section of a non-moving piston
according to the
invention in a Don pressurized cylinder at the second longitudinal position,
shown in its production size, and when pressurized to a certain level.
Fig. 204B shows the contact pressure of the pressurized piston of Fig. 204A on
the wall
of the cylinder.
CA 02786315 2012-08-24
Zl~
KIT VT Ts~ A-0- f-5T
Fig. 204C shows a longitudinal cross-section of a non-moving piston according
to the
invention in a cylinder at the second longitudinal position, shown in its
production size, and at the first longitudinal position when pressurized to
the
same Level as that of Fig. 204A.
Fig. 204D shows the contact pressure of the piston of Fig. 204C on the wall of
the
cylinder-
Fig. 205A shows a longitudinal cross-section of the piston of Fig. 204A in a
non-
pressurized cylinder at the second longitudinal position, the piston with its
production size, and when pressurized.
t 0 Fig. 205B shows the contact pressure of the pressurized piston of Fig.
205A on the wall
of the cylinder.
Fig. 205C shows a longitudinal cross-section of the piston of Fig. 204A in a
cylinder at
the second longitudinal position, the piston with its production size, and
when
pressnized, subjected to a pressure from the cylinder.
Fig. 205D shows die contact pressure of the piston of Fig. 205C on the wall of
the
cylinder.
Fig. 206A shows a longitudinal cross-section of a chamber with fixed different
areas of
the transversal cross-sections and a first embodiment of the piston comprising
a textile reinforcement with radially-axially changing dimensions during the
- stroke - die piston arrangement is shown at the beginning, and at the end of
a
stroke - pressurized - where it has unpressurized its production size.
Fig. 206B shows an enlargement of the piston of Fig. 206A at the beginning of
a stroke.
Fig. 206C shows an enlargement of the piston of Fig. 206A at the end of a
stroke.
Fig. 206D . shows a 3-dimensional drawing of a reinforcement matrix of an
elastic textile
material, positioned in the wall of the container when the container is to be
expanded,
Fig. 206E shows the pattern of Fig. 206D when the wall of the container has
been
expanded,
CA 02786315 2012-08-24
Fig. 206F shows a 3-dimensional drawing of a reinforcement pattern of an
inelastic
textile material,-positioned in the wall of the container when the piston is
to
be expanded,
Fig. 206G shows the pattern of Fig. 206F when the wall of the container has
been
expanded,
Fig. 206F1 shows production details of a piston with a textile reinforcement.
Fig. 207A shows a longitudinal cross-section of a chamber with fixed different
areas of
the transversal cross-sections and a second embodiment of the piston
comprising a fiber reinforcement ('Trellis Effect') with radially-axially
changing dimensions of the elastic material of the wall during the stroke -
the
piston arrangement is shown at the beginning, and at the end of a stroke -
pressurized - where it has unpressorized its production size.
Fig. 207B shows an enlargement of the piston of Fig 207A at the beginning of a
stroke.
Fig. 207C shows an enlargement of the piston of Fig. 207A at the end of a
spoke.
Fig. 208A shows a longitudinal cross-section of a chamber with fixed different
areas of
the transversal cross-sections having different circumphcrical length, and a
third embodiment of the piston comprising a fiber reinforcement (no 'Trellis
Effect') with radially-axially changing dimensions of the elastic material of
the wall during the stroke - the piston arrangement is shown at the first
longitudinal position, and at the second longitudinal position - pressurized -
where it has impressurized its production size.
Fig. 208B shows an enlargement of the piston of Fig. 208A at the beginning of
a stroke.
Fig. 208C shows an enlargement of the piston of Fig. 208A at the end of a
stroke.
Fig. 208D shows a top view of the piston of Fig. 208A with a reinforcement tin
the wall in planes through the central axis of the piston - left: at the
first longitudinal position, right: at the second longitudinal position.
Fig. 208E shows a top view of the piston alike the one of Fig. 208A with a
reinforcement in the wall in planes partly. through the central axis and
partly
CA 02786315 2012-08-24
outside the central axis of the piston - left: at the first longitudinal
position,
.right: at the second IongiNdinal position-
Fig.208F shows a top view of the piston alilce the one of Fig. 208A with a
reinforcement in the wall in planes not through the central axis of the piston
-
left: at the first longitudinal position, right: at the second, longitudinal
position.
Fig. 208G shows production details of a piston with a fiber reinforcement.
Fig. 209A shows a longitudinal crosssecron of a chamber with fixed different
areas of
the transversal cross-sections having different cirrumpherical length and a
fourth embodiment of the piston comprising an "octopus" device, limiting
stretching of the container wall by tentacles, which may be inflatable - the
piston arrangement is shown at the first longitudinal position of the
chamber, and at the second longitudinal position of the chamber -
pressurized - where it has unpressurized its production size.
1s Fig. 209B shows an enlargement of the piston of Fig. 209A at the first
longimdinal
position of the chamber.
Fig. 209C shows an enlargement of the piston of Fig 209A at the second
longitudinal
postien of the chamber.
Fig. 210A shows the embodiment of Fig. 206 where the pressure inside the
piston may
be changed by inflation tlmmgh e.g. a Schrader valve which is positioned in
the handle and/or e.g. a cheek valve in the piston rod, and where an enclosed
space is balancing the change in volume of the piston during the stroke.
Fig. 210B shows instead of an inflation valve, a bushing enabling connection
to an
external pressure source.
- Fig. 210C shows details . of the guidance of the rod of the check valve.
Fig. 210D shows the flexible piston of the check valve in the piston rod. -
Fig. 210E shows the embodiment of Fig. 206, where the volume of the enclosed
space
of Fig. 210A-D has been exchangend by a pressure source.and an inlet valve
for inflating the piston from the pressure source, and an outlet valve for
z2l
pressure release to the pressure source -- enlarged details of the valve-valve
actuator combinations according; to Fig 211D
Fig- 210F shows the embodiment of Fig. 10E, where there are steerable valves
and a jet
or a nozzle .. shown as black bases-
Fig. 211A shows the embodiment of Fig. 206 where the pressure inside the
piston may
be maintained constant during the stroke and where a second enclosed space
may be inflated through a Schrader valve which is positioned in the handle,
communicating with the first enclosed space through a piston arrangement -
the piston may be inflated by a Schrader valve + valve actuator arrangement
with the pressure of the chamber as pressure source, while the otlet valve
- of the chamber may he manually controlled by a turnable pedal.
Fig. 211B shows a piston arrangement and its bearing where the piston
arrangement is
communicating between the second and the first enclosed space
Fig. 21IC shows a alternative piston arrangement adapting itself to the
changing cross-
sectional area's in its longitudinal direction inside the piston rod.
Fig. 211D shows an enlargement of the hrflation arrangement of the piston of
Fig. 21 IA
at the end of the stroke.
Fig. 211E shows an enlargment of the bypass arrangement for the valve actuator
for
closing and opening of the outlet valve. -
Fig. 211E shows an enlargement of an.automatic closing and opening arrangement
of
the outlet valve - a comparable system is shown for optaining a
predetermined pressure value in the piston (dashed)-
Fig - 211G shows an enlargement of an inflation arrangement of the piston of
Fig-
21 1A, comprising a combination of a valve actuator and a spring-force
operated cap, which makes it possible to automatically inflate the
piston from the chamber to a certain predetermined pressure-
Fig. 211n - shows an alternative solution for the one of Fig. 211G,
comprising, a
combination of a valve actuator and a spring positioned below the piston of
the valve actuator. -
CA 02786315 2012-08-24
222
CA 02786315 2012-08-24
Fig. 212 shows an arrangement where the pressure in the container may depend
of thr prmse ;n the rhambcc ___,,,
Fig. 213A shows a longitudinal cross-section of a chamber with an elastical or
flexible wall having different areas of the transversal cross-sections and
a piston with fixed geometrical sizes - the arrangement of the
combination is shown at the, beginning and at the end of the pump stroke.
Fig. 213B shows an enlargement of the arrangement of the combination at the
beginning of a pump stroke.
Fig. 213C shows an enlargement of the arrangement of the combination during
a pump stroke.
Fig. 213D shows an enlargement of the arrangement of the combination et the
end
of a pump stroke.
Fig. 214 shows a longitudinal cross-section of a chamber having an classical
or
flexible wall with different areas of the transversal cross-sections and
a piston with variable geometrical sizes - the arrangement of the
combination is shown at the hegimu , doting and at die end of the
stroke.
Fig. 215A shows examples of transversal cross-sections made by Fourier Series
Expansions of a pressurizing chamber of which the transversal cross-
sectional area decreases, white the circumpherical size remains
constant.
Fig. 215B shows a variant of the pressurizing chamber of Fig. 207A, which has
now a longitudinal cross-section with fixed transversal cross-sections
- which are designed in such a way that the area decreases while the
circurnfcrence of it approximately remains constant or decreases in a
lower degree during a pump stroke.
Fig. 215C shows transversal cross-section G-G (dotted lines) and H-H of the
longitudinal cross section of Fig. 215B.
Fig. 215D shows transversal cross-section G-G (dotted lines) and I-I of the
z23
CA 02786315 2012-08-24
,,,.per
longitudinal cross section of Fig. 215C.
Fig- 215E shows other examples of transversal cr sections made by Fourier
Series Expansions of a pr -ssuriz ng chamber of which the transversal
cross-sectional area decreases, while the cucumpherical size remains
constant.
Fig. 215F shows an example of an optimized convex shape of the transversal
cross section under certain contraints-
Fig 216 shows a combination where the piston in moving in a cylinder over a
tapered center. -
Fig. 217A shows an ergonomical optimized chamber for pumping purposes
and manual operation.
Fig. 217B shows the corresponding force-stroke diagram-
Fig. 218A shows an example of a Movable Power Unit, hanging under a parachute
Fig. 218B shows details of the Movable Power Unit.
CA 02786315 2012-08-24
22ti
.f-~ -~~l lei ~r ~r
,67 DESCRIPTION OF TEE DRAWINGS
------'r'ne-froregoing feat+rres-and-athe~espeets-of-fbe-ittvenekm-aze-
expYamerrin-f}>~foHewing-'
descoiption in connection with the accompagning drawings, wherein:
Figure 301 shows a font embodiment of the valve actuator in a clip-on valve
connector to
which a Schrader valve can be coupled,
Figure 301A shows an enlargement of a detail of Figore 301 with channels
around the piston,
Figure 301B shows section G-G of Figure 301A,
Figure 302 shows a second embodiment of the valve actuator in a universal clip-
on valve
connector with a streamlined activating pin,
Figure 302A shows an enlargement of a detail of Figure 302,
Figure 302E shows section H-H of Fig. 302A,
Figure 303 shows a third embodiment of the valve actuator in a squeeze-on
valve connector,
Figure 303A shows an enlargement of a detail of Figure 303,
Figure 304 shows the valve actuator including an activating pin and the wall
of the cylinder
in a permanent assembly (e.g. from a chemical plant),
Figure 305 shows a fourth embodiment of the valve actuator in a universal
valve connector
~" ZV
CA 02786315 2012-08-24
19597 BRIEF DESCRIPTION OF THE DRAWINGS
In the following, preferred embodiments of the invention will be described
with reference to
the drawings wherein the invention is explained in detail below by means of
diagrams and
drawings. The following is shown in the diagrams or drawings - a transversal
cross-section
means a cross-section perpendicular to the moving direction of the piston
and/or the chamber,
while the longitudinal cross-section is the one in the direction of said
moving direction
Fig. 401A shows a top view of a pump of a floor pump type of Fig 401B,
where the combination can turn around a line XX, YY or ZZ in
relation to the floor surface, while the angle is not restricted by the
suspension.
Fig. 401B shows a back view of the floor pump of Fig. 401A.
Fig. 402A shows lop view of a pump of a floor pump type of Fig 402B,
where the combination can move in 3 dimensions in relation to
the srnfaeo, while the angle is restricted by spring force of the.
transition between the combination and the basis.
Fig. 402B shows the back view of the floor pump.
Fig. 402C shows a top view of the pmnp of Fig 4023, where the handle has
been moved to a position in front of its rest position.
Fig. 402D shows a top view of the pump of Fig 402B, where the handle has
been proved to a position at the back of its rest position.
Fig. 402E shows a top view of the pump of Fig 402B, where the handle has
been moved to a left position in front of its rest position.
Fig. 402F shows a top view of the pump of Fig 402B, where the handle has
been moved to a left position at the back of its rest position.
Fig. 402G shows a top view of the pump of Fig 402B, where the handle has
been moved to a right position in front of its position when out of
function.
Fig. 402H shows a top view of the pump of Fig 4023, where the handle has
been moved to a right position at the back of its rest position.
Fig. 40 3A shows a side view of a floor pump with a flexible transition
between the
chamber of the combination and the basis.
2'1 G
L(I
CA 02786315 2012-08-24
Fig. 403B shows an enlargement of the transition of Fig. 403A.
Fig. 403C shows aback view of a floor pump with another flexible transition
between the chamber of the combination and the basis.
Fig. 403D shows an enlargement of the transition of Fig. 3C.
Fig. 404A shows a back view of of a floor pump with a cab which allows the
piston rod to move in the transversal direction of the combination.
Fig. 404B shows an enlargment of a transversal cross-section of the cab of
Fig. 4A when the piston rod is pulled out to its maximum- no
transversal movement.
Fig. 404C shows the transversal cross-section of Fig. 404B when the piston
rod is pulled out to its maximum, with a rotation of the piston rod
to the left.
Fig. 404D shows an enlargement of a transversal cross-section of the cab of
Fig. 404A when the piston rod is not pulled out- no transversal
movement.
Fig. 404E shows the transversal cross-section of Fig. 404D when the piston
and is not pulled out, with a transversal translation of the piston
and to the left.
Fig. 405A shows a top view of a floor pump type of Fig 405B, where the
angle between the centerlines of the handle parts opposite the
centerline of the combination is less than 180 .
Fig. 405B shows a side view of handle of the floor pump of Fig. 405A.
Fig. 406A shows a top view of a floor pump type of Fig 4065, where the
angle between the centerlines of the handle parts opposite the
centerline of the chamber is more than 180 .
Fig. 406B shows a side view of handle of the floor pump of Fig. 406A.
CA 02786315 2012-08-24
22
1961 DESCRIPTION OF PREFERRED EMBODIMENTS
In the following, preferred embodiments of the invention will be described
with reference to the
drawings wherein:
15
25
1.3
Fig. ~-$ deal with the limitation of the stretching of the will of the piston.
'T'his comprises a limitation of
thh/rcetching in the longimdinnl eBreetinnwhenthe'piston 'iin s'ub'jected ni a
pressnrc !h the chmmber, and
to allow expansion in the transversal direction, when moving from the second
to the heel longimdinnl
position.
'T'he stretching in the longitudinal direction of the will of the container
Type piston may be
limited by several methods. It may be tinne by a reiofometnem of the wall or
The comaioer by using e.g.
textile andlor fiber reinforcement. It catty also be done by mt inside [he
chamber of the container
positioned expanding body with a limitation for its expansion, while it is
connected to The wa11 of the
container. Other methods may be toed, e-g. pressure management of ft chamber
in-between two wails of
The container, pressmt management of the space above the container etc.
The expansion behaviour or the wail of the trootaiecr may be depending on the
type of the
stretching limitation used. Moreovar, the keeping of the piston which is
moving over the piston 'ad,
while expanding, may be guided by a mecit'.mical stop. She positioning of such
a stop may be depending
nn the use of the piston-chamber combination. 'fhia atop also be the case for
the guidance of the
container over [he piston rod, while expanding and/nr anjected to external
faces.
All hinds of Fluids may be used - a eonthination of it emnpreseahle and anon-
emnpratisahle
median, a compressable medium Only m' a non-eompressable medium only.
As the change of the size of the container mny be snlxstcotial from the
Smallest cross-sectional
area, where it has Its probatetion size, and expanded at the biggest cross-
sectional area, a eommuniention
of the chamber in the container wilh a first enclosed space, e.g. in the
piston rod may he necessary. In
order to keep the pressnrc in the chamber, the first enclosed space mny be
pressurized as well, also
daring the change of the volume of the chamber of the container. Pre.ssurc
management for al least file
first enclosed space mny be needed.
Fig. r+A shows it longimdinnl crtus-section of the chamber 186 with a concave
wall 185 and an
inflatable piston comprising a container 209 at theheginning (- first
Iongimdioat position in the chamber
186) and the same 208' at the end of a stake (= second Iungitndina) position
in the chamber 186).
Central axis of the chant her 186 is 184, The container 208' shows its
production size, having a textile
reinforced 189 in The skin 188 of the will M. During the stroke, the wall 187
of the container expands
anlil a stop arrangement, which may be the textile reinforcement 189 andlm' n
mechanical stop 196
CA 02786315 2012-08-24
CA 02786315 2012-08-24
onlside the eomniner 208 hid/or another stop E'rangemenl slope ilia movement
(hiring the stroke. And
bits the expansion of the containers,.72py~.tllliug.nn.d>L-pres.cucc-.iubc-
c6tntv>berFRfi;-nc~~c-stithiiw-
tiecnr a longinldinal snfrehing or rho will of rho container, due to pressure
Ili the chamber 196. The
main Section however of the reinf)eoemonl is to limit this longitudinal
welching of the wall IR7 of the
eolitniner 209. During the stroke the pressure inside the cnnainer 208.208'
only remain cdnsninl. This
pressure depends on the change in the vnlome of the container 200,208', thus
on the change in the
ci orrorierential length of the cross-seeriotss= of the chamher I R6 during
the strike. it may also be possible
Sr the pressure changes during the stroke. 11 may also be passible Ihat rho
pressure changes daring the
.stroke, dependIing or nor of the pressure in the Chamber 196.
Pig. OB shows It first enbndiment of the expanded piston 208 al the heginning
of n shake. The
^rda11 I97 or the cnntniner is build up by a Skin IRS -fit flexible material,
which may be e.g. r rctober
type or the like. With a iextiie reinforcement 189, which allows expansion
'rho direction of the textile
rclnforccmcnt in rciaiion to the cenual axis 164 1- braid Engle) is different
from 54 44', The change or
the size or the pis[an during the troika results not nece,sssrily in an
identical shape, as drawn Poe to
[he expansion the thickness of the will) of the c0ntaints may be sailor than
that or the container as
produced when positioned no rheencl or the sh'oke (= second longitnclinal
position). An impervious layer
190 inside the wall 187 may be present. It Is tightly squeezed in the cap 191
in the lop and the cap 192
in the holies of the eonntiner 208,209'. Ihmils of said caps ire nil shown and
ill kings of assembling
methods inny be used - those mny be expnhte to adapt themselves to the
changing thickness of the wml or
the container. both caps 191,192 can translate ond]or romro over the piston
rid 195. These movements
cry he finite by various methods as e.g. different types of bearings which me
not shown. The cap 191
in the top of the container mny move uPwmrds msd downwards. The smp 196 nn the
pismn roll 195
outside the container 20R limits the upwards movement Ollie container 208. The
cap 192 in the h000tso
may oey move downwards hcenuse the stop 197 prevent a movement upwards -.This
embodiment miry
he thought to be used in a piston chamber device which Inc pressure in chamber
186 beneath the piston.
Other arrangements of slips nnay be possible in Either pump types, such as
doable working ptnps.
vaeIlUn pumps etc,-;Ind depends solely of the design spiefejuio Is. Other
arrangelnenrs for enabling
and/ar Ilmiting the relative movement of the piston to the piston red nosy
occur. The tuning of lilt ,
senling t'nt'ce may comprise a canblotirnl of nn ine0mpressnble fluid 205 and
a cempreirsablc Fluid 206
y l0./ [~ Wf ^t~",~Iy ,, '6 I lit- Q'fzc
a-x lc p /L/ ) pcSr'h'dYfd v<wot /)L i- m S 2 S.c CDE
d' F1aL~ C 7O$:!-I'oracS-
CA 02786315 2012-08-24
23c,
(both alone ore also a possibility) inside the container, while the chamber
209 or the container ntny
v_ . _ 1tesig tl9tlirj9ilh itOttl15it 7 chsmbet250 cnmpcisiubcn-
,spring.:tiarce-opoctaoÃI-p swn-l'1)&'inside-[hc'pistnn--
rod 195. The fluid(s) may freely flow through the well 207 of the piston rod
through the hale 201. It
may be possible that the second chamber is emmhnnieating with n third chamber
(sec 111g. 12), while the
-pi'dsswn inside the container also may be depending on the pressure in the
elinmbe j86. The container
may be inflatable through the piston rod 195 and/or by cmnmunicnling with the
ehmnber 116. 0-rings
or the like 202, 203 in said cap in Ilia top and in said cap in the bellrnn,
eespeetivcly sent the enps
191,192 to the piston red.'l ien cap 204, shown as a screwed tnssemb{y m the
and of the pislnn rod 195
hisighthens said piston rod. Comparable stops may be pn shinned elsewhec nn
till piston nnnl, depending
on the demanded movement of the wall or the container.'rhe contain area
belwcal the wail or the
enntnioe' and the wall or file chnntbeeis 198..
Pig. ~C allows the piston of Fig. 013 al the end ilia pump slope, where it has
its prndnedon
situ. The cap 191 in [he top is moved over 11 distance a' Ironic the slop 196.
The spring-rtrce ,pealed
valve piston 126 has been moved over a distance W. The bntotn cap 192 is shown
ntljacent to the stop
197 - when there is pressure in the chnntber 192, then the bottom enp 192 is
pressed against the stop
197. The emnpressabie Fluid 206' and the non-compcssnhle Fluid 205', The
enamel area 198' between
the cnggntnleer 201)' and )he wall of the chamber at the second Iiengimdinal
posilino.
Fig. 7A shows a longiudinal crtxs-seutiint of the chamber 186 with a concave
will 182 and an inllntnble
pislnn comprising a container 217 of the ricst longih+diaal position tf the
chnmher and the some 217' in
the second longitudinal position. The container 217' shows its production
sine, having n fiber reininreetl
219 in the skin 216 of the wall 218 according to the 'Trellis Effect'. During
the stroke, the wall 216 of
the container expands until a slop arrangement, which may be the fiber
reinfotscmenl 219 andror a
mcchnnienl stop 214 inside the container and/m' another snip nrrangencent
stops the movement during
the slo-kc. A ld thus stops the expotsln, nr the wall 2i R nr the ennminer
217, ')'he main futletlon or the
fiber minfaleenton is to limit the lotgihalinnl stretching tribe wall 219 of
the contnine 217, paring the
stroke the pressure inside Ilia container 217,217' may remain conslnnt. ')'his
pressure depends on then
change in the vnhtnte of the container 217,217', thus on the change in the
cireuml'e'entinl length erthe
crass-sections of the chamber 186 dtn'ing the .shake. it mny also be possible
that the pressure changes
(. -( rOs7& r1) line elaebe,e t96 wh,,,t tT pa,7n(-/o P
ce> (=u a-nc / Sv . / /- 'J Pau; h'd Y e /, gta,
CA 02786315 2012-08-24
danieg the stake, depending oer.nnt of the pressure in the chamber 186. The
contact urea 211 between
the cnnoinor 217 tied t Y tl oo chamhm.nt_llta-tint-bnagitudhttd-prmiti em -
Pig. 75 dhows a second em6 aliment of the espontlad pistol 217 m the beginning
of a stroke.
The will 218. of the eonioloer is build up by a skin 216 of a flexible
malarial. which only he e.g. it
rohher.type or the like, with n fiber reinforeement 219, which allows
expansion of the coilmim wild
218, and thus the direction of the fibers in relation In the control axis 184
(= braid 'Ingle) only lie
different from 54 44'. Due to the expansion the thickness of the wall of the
cnntniner may he smaller,
bill not ooeesarily very different than that of the soutanes as pnxiuccd when
positinnetl at the end of the
stroke (= second longitudinal positron). An impervious Inye, I90 inside the
wall 187 cony be present. It
is tightly squeezed in the cap 191 in [he top and the cep 192 in the hmhno of
the container 217,217'.
Details of said caps are not shown mxl nil kinds of assembling wetlands may be
used - these may he
capable to adept ihwnselvev to the changing [hiclmass of the wail of the
cnnlaioer. Huth cops 191,192
can translate and/or matte over the, piston rant 195. These movement.. tray
tie done by various mothsdr
ns e.g. different types of bearings which arc tint shown. 1ftc cap 191 in [he
top can move upwards and
downwinds until stop 214 limits this mnvetnent.'rhe cap 192 ill the hollow
ctur only move downwards
batiste the STOP 197 prevent n movement upwards - this embndhnent is thuughl
to be used in a piston
chamber device which has presanra in chamber 186. Otter an ingements of slops
may be possible in
other pump types, auch as double working pumps, vacuttnt pumps etc. and
!legends solely of the design
specifications, Other 1.lonfcoents for enabling and/nr limiting the relative
movement of the piston in
the piston rOil nay oeeur. Thu hating of [he scaling fame may comprise at
eomhinition of in
itu.nmpressnhle fluid 205 and as onmpressahle fatid 206 (boil) alone are also
n possibility) inside [be
contaner, while the chamber 215 of the contnioar 217,217' may conninimeae with
a second chamber
210 comprisioa n sRrioa-force nperitcd piston 12C inside the piston nil 195.
The Onid(c) cony Onaty
Flow thtnngh the wan 207 of the piston rnil through [he hole 201. 11 may be
possible dint the second
Chamber is comtmmicn[ing with a ]bird chamber (see Fig. I9), while the
preasute inside theconlnlner
also only be depending on the pressure in the chmnher i 86.7he containar may
he inlattble throuth the
Piston rod 195 old/or by conununicating with Sr chamber 186. 0-rings or the
like 202, 203 in anal cap
in the top and in said cap in the holism, respectively seal the caps 191,192
10 the piston rod. 'file cap
201, shown as a screwed assembly of the end of [he piston rod 195 thighthen
said piston rod.
Bqt
T (,5mg, {?~ c~cnk rB6 wi oz :t pazwee,( -fo t15 Ce. PU
(Q(/Y =T l BY. ~Y %S ' h pP eao Y 1 a fl~o~c a L ~ v9
2~2 ~q
'La ti
Fig. IC shows the piston of FIg.' f at the end are pump snake, where it his
ha, prothlction
_ _ si?E _ }!.12J-_is:iniw cLnucc.a{tisFnnse-a= Srotirttie-stop-2~-
4:'7'he"s}m1 -oreu nprn[cd valve piston
.126 hiss been moved over a distance tl', The bettose cop 192 is :shown
ndjoeent to the stop 197 - if there
is pressure in the cha"her 186, than the cap 192 is pressed against the mop
197. The compeessable thud
206' and the non-compresseble fluid 205'. The cacao nice 211' of the container
217' and the wall of
the chamber 186 at the second longitudinal position,
Fig.B$A,B,C show an inflatable piston emnprising a container 229 at she
beginning and 228' at
the end of n stroke. The production size is that of piston 228' at this
.second longitudinal position in the
ehnmber 186. The construction of the piston may be identical with [List or
Fig. 6A,fl,C with the
exception that the reinforcement comprises of Wily hint) of reinf rcement
means which may be bendable,
nod which may ly in a pattern of reinforcement 'colsoes' which do not crass
each other, 'this pattern
may Ix the of pnrn0el to the central axis 1114 of the chamber 186 or one of
where e per[ of the
reintmrccment"'ane may be in a plane through the ',,nonl axis 184.
Fig. Al shows the wail 218 with the skin 222 and 224. The reinforcement 223.
The contact
area 225 between the container 228 and the wall of the chamber at the first
longitudinal position. The
impervlosin toper 226.
Pig. 3C
shows the contact even 225' between the c nutiaer 226' ;tad the well of Lite
chnmbcr at
the secoost longitutlinnl position.
Fig. 8D shows a top view of die piston 228 and 228', respectively will) the
reinfor-cement looses 227,
11111227' respectively.
Flg.1E shows it top view of the piston 228 and 228', respectively with the
eeinfnreetnent
means 229, mall 229' respectively.
1 e l u X 5 6 t~ Y~ cl ams / b~ G1l ;c/ p az a Pr C
} n /~ Cewf ze Lc~ S r6'1. D115 ea-)' a a f e ,(
ph z po -I aF secs -~i ; JzwG -o -e pelda r87t .
CA 02786315 2012-08-24
CA 02786315 2012-08-24
2)~
~,VO 41
Pig. 4 shows a non-moving expandable piston 228' inside a chamber 186 with a
wall 185a,
which is parallel to the centre axis 184 of said chamber 186 at a position
where the contact surface 225'
between the piston 228"and the wall 185 of said chamber 186, while there are
no pressure differences in
the chamber between both sides of said piston. The part 185 of the chamber
further 1o a first ptuition
has so angle with the centre axis 184. The projection 1000 of the middle point
(centre) 1001 of the
elasfically deformable wall of the piston on the centre axis 184.
Fig. 5A shows the piston of Fig. 4, instantaneously non-moving inside a
chamber 186 with a
conical shaped wall 185, where the piston is beginning to expand - the.movahle
cab 191 is moving
toward the non-movable cab 192. The contact surface 225" has been increasing,
and is now
positioned below the centres 1002 and 1003, respectively of the elastically
deformable wall of the
piston - its projection on the centre axis 1004 (old) and 1005 (new),
respectively. The distance F.
The direction of moving 1006 of the movable cab 191. The force 1007 from the
wall 187 of the
piston to the wall 185 of the chamber 186. The distance g'.
Fig. 5B shows the piston of Fig. 5A, instonteneonsly non-moving, and thereby
expanding, so
that the contact area 225"' of the piston wall 187 with the 185 will of the
chamber 186 increases at
second longitudinal positions of said contact surfcce 225"' - the movable cab
191 is currently non-
moving. The contact surface 225is around the point where the middle point
(centre) is of the
elastically deformable wall of the container. The centres 1008 (old) and 1009
(new) of the the elastically
deformable wall of the piston - its projections 1010 (old) and 1011 (new) on
the centre axis 184
respectively. The distance C. The force 1012 from the piston will 187 on the
wall 185 of the chamber.
The direction of movement 1013 of the force 1012. The movement 1014 of the
movable cap 19].
Fig. 5C shows the piston of Fig. 513, instanteneously non-moving, and thereby
expanding, so
that the contact surface 225of the piston wall 187 with the. watt 185 or he
chamber decreases at
second longitudinal positions of said contact area, while the contact area of
the piston will with the
wall of the chamber increases at first longitudinal positions of said contact
area - the movable cab is
non-moving. The centres 1015 (old) and1016- (new) of the the elastically
deformable well of the piston
its projections 1017 (old) and 1018 (new) on the centre axis 184 respectively.
The distance g'. The
direction of movement 1019 of the reaction force 1020 of the chamber will 185
on the will 187 of the
piston. The direction of the movement 1021 of will 187 of the piston.
Fig. 5D~ shows the piston of Fig. 5C, where the non-movable cap 192 is
inslanleneonsly
beginning to move from second to first longitudinal positions, thereby moving
the piston in the same -
direction. The contact area 225 .. which is much smaller than that 225"" of
Fig. 5C. The distance
h'. The projection 1022 of the centre 1023 of the elastically reformable will
of the piston on the
centre axis 184 respectively. The moving direction 1024 of the movable cap
191, and that 1025 of
the non-movable cab 192, thus that of the whole piston. The leakage 1026,
which occurs at that point
of time.
Fig. 5E shows the piston of Fig. 5D, where the movement of the piston is
decreasing (Ill, to A
increasing contact area 225 ....... The projection 1027 on the centre axis 184
of the centre 1028 of the
elastically deformable will of the piston. The moving direction 1029 of the
movable cap 191. The
moving direction 1030 and 1031 of the wall of the piston. 6,1 iA.r.d
Fig. 6A shows an expaulable piston 896, moving engagingly / sealingly 900 in a
cone-formed
chamber 899, comprising a reinforced (Do[ shown) will 901, which is embedded
in unmovable cab 903.
and a movable cab 904. Said cab 904 is slidingly movable over the piston rod
902, which is hollow,
comprising the enclosed space, and communicating with the space in the piston
898. There is Fluid or a
mixlmc of fluids in she piston. Said chamber is closed at bosh sides of the
piston with spaces 906, 907,
and may be comprise a fluid or a mixture of fluids at one or at both sides of
the piston 898. The contact
211 area 905 between the will 901of the piston 898 and the will 897 of the
chamber 899. The existaoce of
fluid at both sides of the piston may cause the piston move in a different
moaner than desired.
Fig. 6B shows the piston 898 of Fig. 6A moving engagingly / sealingly 900 in a
cone-formed
chamber 896, which has spaces 908 and 909 at the respective sides of the
piston 898. In the wall 895 of
[he tout rormed chamber 896 nt t" longitudinal positions in a who 911, which
allows crnmnumcn[ion
between the space 908 with the annosphere 910 of the surroundings, while tube
912 is assembled in the
will 895 of said cone-formed chamber 896, which allows communication between
the space 909 with
the atmosphere 910 of the surroundings. The contact area 905 between the will
901 of the piston 898
non the wall 897 of the chamber 896,
CA 02786315 2012-08-24
76
14- 23'<
CA 02786315 2012-08-24
atmosphere 910 of the surroundings. the contact area 905 between the wall 901
of the piston 898 and the
wall 897 of the chamber 896.
Fig. 6C shows the piston 898 of Fig. 6A moving engagingly / seatingly 900 in a
cone-formed
chamber 894, which has spaces 908 and 909 at the respective sides of the
piston 898. In the wall 893 of the
cone formed chamber 894 at 1 longitudinal positions is a tube 913, which
allows communication between
the space 908 with the inside of tube 915 which communicates with the tube
914, which is assembled in
the wall 893 of said cone-formed chamber 896, and which communicates with the
space 909 of said cone-
shaped chamber 894.. The contact area 905 between the wall 901 of the piston
898 and the well 893 of the
chamber 896.
Fig. 6D shows the piston 892 moving engagingly in a cone-shaped chamber 899,
which has
spaces 906 and 907 at the respective sides of the piston 892. Said spaces 906
and 907 are communicating
with each other through tube 918, which is assembled in cabs 891 and 890,
respectively.
The contact area 905 between the wall 901 of the piston 898 and the wall 897
of the chamber 899.
Fig. 6E shows the piston 898 engagingly movable in a cone-shaped chamber 899
Said chamber is
closed at both sides of the piston with spaces 906, 907, and may be comprise a
fluid or a mixture of fluids
at one or at both sides of the piston 898. There is no contact area between
the internal wall 922 of the cone-
formed chamber 899 and the external wall 923 of the piston 924, and instead
there is a gab 920 between
said walls 922 and 923, allowing a flow of fluid 921 in the opposite direction
of the motion 900 of said
piston 898.
Fig. OF shows an actuator piston 925, based on the piston 924 shown in Fig.
6E, having a duct
926, preferably 3 ducts 926 equally spread over the contact area 927 of the
wall 928 of the actuator piston
925 and the wall 922 of the chamber 899. The ducts 926 are allowing
communcation of the fluid between
both spaces 906 and 907 of the chamber 899. The part 929 of the contact area
927 where sealingly contact
is taking place with the wall 922 of the chamber 899 along the circumference
is smaller, than when said
ducts 926 were not present, but the obtained driving fame of said actuator
piston 925 may still be
acceptable. The length of said duct 926 in the longitudinal direction is
bigger than longitudinal length of
the contact area 927 in order to obtain communication between said spaces 906
and 907 of said chamber
899, at all longitudinal positions. The piston rod 929. The movable cab 930.
Fig. 6G shows the a transversal cross-section of the piston rod 929 of Fig. OF
and the view on the
actuator piston 925 from a 1" longitudinal position. The chamber wall 922. The
movable cab 930. The
23t
CA 02786315 2012-08-24
ducts 926, equally updividing the circumference of said actuator piston 925
approx. at the contact area 927
with the wall 922 of said chamber 899.
Fig. 7A shows the piston of Fig. 1C atthe end of a pump stroke. The wall of
the chamber is
parallel with the centre axis 184, and which is why the container is non-
moving, even when pressurized.
Fig. 7B shows the piston of Fig. 7A, in a part of the chamber where the walls
are not paralell to
the centre axis, but with a positive angle. The piston will move toward a fast
position, because the midt
point of its flexible wall is above the contact surface with the wall.
Figs. IOA-F (incl.) show the pressure arrangement of a combination of an
inflatable actuator
piston, ng in a conical chamber, where the size of the volume of the enclosed
space is constant
when the am actuator piston is running from a second to a first longitudinal
position. s may be
done in both tee ologies (CT and ESVT). Figs 10G- (incl.) show the pressure
arrangement of a combination of an inflatable actuator
piston, running in a cduical chamber, where the size of the enclosed space is
decreasing when said
actuator piston is rmmms ' ~oma second to a first longitudinal position. This
is done in order to reduce
the volume of the pressurizbd medium, and thus is a reduction .of the energy
to be used for the
repressuration of said mediurrl,\This may be preferably do a in embodiments
using the ESV
Technology, because there the than e of the size of the ennclosed space volume
is done much more easy
that in embodiments using the Cons ption Technolog
Fig. I SA shows a piston-chamber c bination with a chamber 186, having a
centre line 184, a
wall 185 of said chamber 186, where pressurized ellipsoYde shaped piston 217' -
as described in
sections 207, 653, 19660 and 1996 of this p\ddttent application - is moving
2003 from a second
longitudinal position 2000 to frist longitudinal position 2001. At said first
longitudinal position 2001
has said piston 217' has,~bexpanding into a piston 2 , having a sphere shape,
while having a fixed
volume of the enclosed space 210. This means that the pr smc inside the piston
has been decreased
when arriving llaaid first longitudinal position 2001. The sh' e of the piston
217 may also be at said
first longitgdonal position be ellipsoide (not shown) - as described and shown
in section 19660 of this
patent application - and this will not effect the size of the internal
pressure of said piston. The position
2004 of the valve 126 is during said run unchanged, so that the volume of the
enclosed space 210
Z7}
- Frg. ~D is a 3-dimensional drawing and shows a reinforcement matrix of
textile material,.
2.0 allowing elastically expansion and contraction of the wall of the
container 208,208', when sealingly
moving in the chamber 186.
The textile material may be elastical, and laying in separate layers over each
other. The layers may
also lay woven in each other. The angle between the two layers may be
different from 5444'.
When the material type and thiclmess is the same for all layers, and the
number of layers ev n,
26 while the stitch sizes for each direction are equal, the expansion sod
onetraction of the well of the
container may be equal in the XYZ-direclion. When expanding the stitch as and
d, respectively in
each of the directions of the matrix will become bigger, while contracting
these wit become
smaller. As the material of the darends may be elastical, another device may
be necessary to stop
the expansion, such as a mechanical slop. This may be the wall of the chamber
andlor a mechanical
30 atop shown on the piston rod, as shown in Fig. 4f8.
Fig. C is a 3-dimeesio al drawing and.shows the reinforcement matrix of Fig.,
D which
has been expanded. The stitches ss' and tt' which are laegar than the stitches
en and it. The result of
the contraction may result in the matrix shown in Fig, ~D.
$ig.P is a 3-dimensional drawing and shows a reinforcement matrix of textile
material
which may be made of inelastic thread (but elastically bendable), and lay in
separate layers over
each other or knitted in Bash other. The expansion is possible because of the
extra length of each
loop )00,, which is available, when the container is in the production size -
also pressurized, when
b positioned at the second longitudinal position of the chamber, Stitches ss"
and d" in each direction.
When the wall of the container is expanding die inelastic material (but
elastically bendable) may
limit the m,mlm,,,, expansion of the wall 187 of the container 217. It may be
necessary m slop the
movement of the container 217 over the piston rod 195 by e.g. stop 196, on
that sealing may
remain. lire lack of such a stop 196 may give the possibility of creating a
valve.
Fig.' G is a 3-dimensional drawing and shows the reinforcement matrix of Fig.
7which
has been expanded. The stitches ss"' and It"' which are large than the
stitches ss" and it", The
result of the contraction may result in the matrix shown in Fig. F. CA
02786315 2012-08-24
Fig. J.s shows a combination where the piston comprising an elastically
deformable
container 372 which is moving in a chamber 375 within a cylinder wall 374 and
n taper wall 373
e.g. shown her in the centre around the central axis 370. The piston is hanged
up in at least one
piston rod 371. The container 372,372' is shown at the second longitudinal
position of said
6 chamber (372') and at the host longitudinal position (372).
All solutions disclosed in this document may also be combined with piston
types for
which the chambers having cross-sections with constant circlunpherential sizes
may be the solution
for the problem of jam,ning.
CA 02786315 2012-08-24
271
Fig. 9A shows a longitudinal arose-section of the chamber with it
convex/concave wall 185 and
a i n inflntnhle-piston comprisinga-cnntxiner 258 at the h e g 1 0 h i rt g a -
M l T O s a i ft e 2 3 8 ' a t T t i e eml of a shake.
The container 258' shows its production size.
Fig. 98 shows the longitudinal cross-section of the piston 258 having a will
251 and a
reinforced skin 252 by a plurality of at least elastically ieformable support
members 254 rnnttnhly
fastenecl ton common member 255, connected to the an skin 252 of said piston
258,259', These
members are in tension, amt depending on the hardness of the material, they
have a certain maximum
stretching length. This limited length limits the stretching of the skin 252
of said piston. The common
member 25S may slide with dieting means 256 over the. piston rod 195. For the
rest is the ennsltuclion
cnmparnhle with that of the piston 208,208'. The contact area is 252.
Fig. 9C shows the Iongitudinnt cross-section of the piston 258'. The contact
as-en is 253'.
oyo
UJ121 0. Peu] wt c et a ii )/ e CnH~ze - r L k~~v4 y ~~S r
[yplc /1 1~' fat hi- j~ /-iet, 1L 62 M põ~ t-2,V
6> ce-ha,a .~ 1022
CA 02786315 2012-08-24
2qo
CA 02786315 2012-08-24
Figs. l0A-F (incl.) show the pressure arrangement of a combination of an
inflatable
actuator piston, running in a chamber, said chamber having cross-sections of
different cross-
sectional areas and different circumferential lengths at the first and second
longitudinal positions,
and at least substantially continuously different cross-sectional areas and
circumferential lengths at
intermediate longitudinal positions between the first and second longitudinal
positions, the cross-
sectional area and circumferential length at said second longitudinal position
being smaller than the
cross-sectional area and circumferential length at said first longitudinal
position, wherein the size of
the volume of the enclosed space is constant when the said actuator piston is
running from a second
to a first longitudinal position. This may be done in both technologies (CT
and ESVT).
Figs. 1OG-L (incl.) show the pressure arrangement of a combination of an
inflatable actuator piston, running in a chamber, said chamber having cross-
sections of different
cross-sectional areas and different circumferential lengths at the first and
second longitudinal
positions, and at least substantially continuously different cross-sectional
areas and circumferential
lengths at intermediate longitudinal positions between the fast and second
longitudinal positions,
the cross-sectional area and circumferential length at said second
longitudinal position being
smaller than the cross-sectional area and circumferential length at said first
longitudinal position,
where the size of the enclosed space is decreasing when said actuator piston
is running from a
second to a first longitudinal position. This is done in order to reduce the
volume of the pressurized
medium, and thus is a reduction of the energy to be used for the
repressuration of said medium. This
may be preferably done in embodiments using the ESV Technology, because there
the change of
the size of the enclosed space volume is done much more easily than in
embodiments using the
Consumption Technology.
Fig. 10A shows a piston-chamber combination with a chamber 186, having a
centre line
184, a wall 185 of said chamber 186, where a pressurized ellipsoide shaped
piston 217' - as
described in sections 207, 653, 19660 and 19680 of this patent application -
is moving 2003 from a
second longitudinal position 2000 to a first longitudinal position 2001. At
said first longitudinal
position 2001 has said piston 217' been expanding into a piston 217, having a
sphere shape, while
having a fixed volume of the enclosed space 210. This means that the pressure
inside said piston
217 gradually during the movement 2003, and is at its lowest value at the
first longitudinal position
2001. The shape of the piston 217 may also be at said first longitudinal
position be ellipsoide (not
shown) - as described and shown in section 19660 of this patent application -
and this will result in
CA 02786315 2012-08-24
2'1)
a less increase in pressure of said piston. The position 2004 of the valve 126
is during said run
unchanged, so that the volume of the enclosed space 210 remains unchanged. The
arrow 2005
shows that the next stage of the operation is shown in Fig. 1OB or Fig IOC,
the last mentioned
shown by the arrow 2011.
The position 2025 shows the piston 217' at a second longitudinal position,
where the wall
2030 of said chamber 186 is parallel to the centre axis 184. The position 2026
of piston 217 at a
first longitudinal position, where the wall 2031 of of said chamber 186 is
parallel to the centre axis
184. The shape 2027 shows said piston 217, when at a first longitudinal
position, the piston is
(delayed) beginning to depressurizing. Shape and size 2028 is when the piston
217" is
approximately on half of the return stroke, where it is just free of the wall
185 of the chamber 186,
due to a delayed depressuration. The same shape and size 2028 of the piston
217' maybe positioned
closer (distance y) to a second longitudinal position than when the piston
217" is moving to a
second longitudinal position, as said piston 217' is engaging the wall 185 of
said chamber 186 (and
not free of it).
The size of the enclosed space under the valve 126 is determined by the length
of the channel .......
to the bottom of the piston rod - this length is `a' at a 2 d longitudinal
position and is `b' at a ls`
longitudinal position, wherein a - b.
Fig. I OB shows the valve 126 has been retracted 2006 from the its position
2004 to a
position 2007 further away from said piston 217. The enclosed space 210'. The
result is that the
volume of the enclosed space 210' is decreasing so much that the pressure
inside the piston 217"
has
become approximately that of when said piston had been produced (e.g.
atmospheric pressure) - the
size and shape are approximately those of when the piston is on the second
longitudinal passion
2000, but now unpressurized - this means that the piston 217" may not engaging
and/or may
engaging, but not seal the wall 185 of said chamber 186, when returning 2008
firm the first
longitudinal position 2001 to the second longitudinal position 2000. The wall
2024 of the piston.
When the piston 217" is moving 2008 from a first 2001 to a second 2000
longitudinal position,
may the internal pressure drop be so relatively slowly obtained, that the
piston 217B"during said
moving stil may have an ellipsolde shape larger than that of the shape of 217'
at a second
longitudinal position 2000, so that said piston 217B" during said moving 2008
is engaging and/or
It, L
CA 02786315 2012-08-24
non-engaging the wall 185. Asa comparison: the same size of said piston 217B"
is obtained further
away to a 2nd longitudinal position than when the piston is (sealingly and/or
engagingly) moving
2003 from a 2"d longitudinal position 2000 to a 1" longitudinal position 2001.
Said pressure drop
may also be obtained already at a first longitudinal postion 2001.
When the piston 217", 217B" has returned to the second longitudinal position
2000, the position of
valve 126 in the enclosed space 210' changes from 2007 to 2004 - arrowed 2009,
so that the
enclosed space 210' has got its original volume of Fig. I OA again, so that
said piston 217' again has
its original pressure. The arrow 2010 shows that the next stage of the
operation shown in Fig. 10A.
Fig. 1 OC shows the alternative solution for changing the internal pressure of
the piston 217,
and shall be regarded together with Fig. I OA, where in this case the valve
126 is lacking and instead
may an inlet/outlet configuration 2020 be present - e.g. please see Figs. 21
OA-F (incl.) and Figs.
21 IA-F (incl.) of section 653 of this patent application. The pressurized
piston 217' is moving 2003
from the second longitudinal position 2000 to the first longitudinal position
2001, as described in
Fig. 1OA. No adding or removing fluid from the enclosed space 210 is occuring,
The arrow 2011
shows that the next stage of the operation is shown in Fig. I OC. The
depressurization in piston 217"
is obtained by removing the necessary amount of fluid from the enclosed space
210: arrow 2020.
When said piston 217" has been returned from the first longitudinal position
2001 to (arrow 2021)
to the second longitudinal position 2000, sufficient fluid is added (arrow
2022) to the enclosed
space 210, resulting in piston 217"' - the arrow 2023 shows that the next
phase is shown in Fig.
I SA, resulting in piston 217'. The watt 2024 of the piston.
It should be emphasized that a combination of both above mentioned
technologies may be an
additional solution for the pressure management of the piston. It may
additionally be possible that
the
pressure drop from piston 217 Or 2081o piston 217" br 208", respectively may
be a gradual one -
e.g. computerized - on the condition that the wall 2024 of the piston only is
engaging the wall 185
of the chamber 186 or not at all during the return from a t' longitudinal
position 2001 to a 2"d
longitudinal position 2000.
The wall 185 of the chamber 186 in the drawings l OA-L at the second and first
longitudinal
2t,t3
CA 02786315 2012-08-24
positions may be not parallel to the centre axis. No channels as shown in
Figs. 4, 5A-E (met.),
Figs. tOD-F show the analogue process of that shown in Figs. l OA-C, now with
a sphere
shaped piston 208.
Figs. I OG-I show an analogue process of that shown in Figs. l0A-C, with the
difference
that the pressure may be maintained more when the piston 217' is moving from a
2"d longitudinal
positions 2000 to a fast longitudinal position 2001, wherein the valve 126 is
not so much removing
from the bottom end of the piston, as shown in Fig. 1 OA. The length of the
piston rod under piston
126, which is giving the size of the enclosed space volume, is `e', while
between 2nd and I `
longitudinal positions this length has been decreased to '17 and at a I"
longitudinal position said
length is further decreased to `g', wherein e > f > g.
Figs. 101-L show the comparable process of that shown in Figs. I OD-F, wherein
pressure is
maintained as described in Fig. l OG, but now with a sphere shaped piston 208.
The length of the
piston rod under valve 126, which is giving the size of the enclosed space
volume, is `h', while
between 2 d and 1" longitudinal positions this length has been decreased to
`i' and at a I"
longitudinal position said length is further decreased to `j', wherein h > i >
j.
The process called the E(nclosed)S(pace)V(olumeehange) T(echnology) shown in
Figs. IOA,I OB or
Figs. I OD, lOE are being used in a motor according this invention, shown in
Figs. I IF,G (crankshaft)
and in Figs, 13F, 13G, 14A-H (incl.) (rotational).
The process called C(onsumption) T(echnology) shown in Figs. IOA,tOC or Figs.
IOD,lOF
and in Figs. 21 OA-F (incl.) and Figs.21 IA-F (incl.) are being used in a
motor according this
invention, shown in Figs. 1 IA-C (incl.) (crankshaft) and in Figs. 12A-C 13A-D
(incl.).
Fig. tOM shows B-B section of Fig. 12 C (and said B-B section can be partly
seen on Fig.
12A) and the motor where the piston of an actuator piston-chamber combination
is moving, while the
chamber is not moving. The motor comprising a chamber 960, which is comprising
4 sub-chambers
961, 962, 963 and 964, respectively, which lie around the same centre axis 965
in continuation of each
other, which has an axle 966 through the center 967 of said chamber 960.
Within said sub-chambers
961, 962, 963 and 964, respectively is I piston 968 positioned, shown on two
important positions,
2LII
CA 02786315 2012-08-24
namely position 968' when at a 1" rotational position of the sub-chamber 964,
having the largest
diameter, and position 968" when at a 2"d rotational position of the sub-
chamber 961, which is lying in
continuation with sub-chamber 964, so that the to rotational position of sub-
chamber 964 lies closest to
the 2"d rotational position of sub-chamber 961, when it has its smallest
diameter. Said actuator piston
968 is rotating clockwise around said axle 966 - there are shown 4 holes 970
for assembling said
chamber 960 on axle 966.
Fig. I ON shows the B-B section of Figs. 13A and 13B and the motor is of a
type where the
chamber of an actuator piston-chamber combination is moving, and the piston is
not moving.
The motor comprising a chamber 860, which is comprising 4 sub-chambers 861,
862, 863 and 864,
respectively, which lie around the same centre axis 865 in continuation of
each other, which has an
axle 866 through the center 867 of said chamber 860. Within said sub-chambers
861, 862, 863 and
864, respectively are 5 pistons 868, 869, 870, 871 and 872, respectively
positioned, each at a different
rotational position said sub-chambers 861, 862, 863 and 864, on an angle a =
72 from each other.
Each piston comprising a piston rod 873, 874, 875, 876 and 877, respectively.
The pistons 868, 869,
870, 871 and 872 are of a "sphere - sphere" type, and are shown all having
different diameters. Said
chamber 860 is rotating clockwise around said axle 866 and the sub-chambers
861, 862, 863 and 864
having a second rotational position and a first rotational position in the
clockwise rotational direction -
there are shown 4 holes 878 for assembling said chamber 860 on axle 866.
The motor according to Figs. l OG and IOH may comprise a chamber 860 of which,
at least a part, may
be parallel to the centre axis of said chamber (not shown).
2W`f
19615 amended - Regarding a pressure management system for Figs. 11F, 13F and
Fig. 13E
It depends on the system of the bidirectional actuator (e.g. Fig. 11F
references 1056
and 1057) whether or not a repressuration system is necessary, when the change
of direction may
cause a loss of pressure - this may be caused by a "consumption" of fluid,
where the fluid during
the directional change may be realesed to the atmosphere or it may also be
caused by a pressure
drop - please see Fig. 13E. The repressuration system is than alike those
shown in earlier
drawings, e.g. Figs. 11A, 11B and Fig. 12A.
It may possible to develop a system which does not "consume" fluid, and
possibly
only "consume" pressure. In the drawings Fig. 1IF, 13F it is assumed to be
present already, so
that only a pressure storage vessel of a certain volume may be necessary. The
pressure should be
preferably low pressure (e.g. 10-15 Bar), optionally high pressue (e.g. 300
Bar).
This system may comprising a classic cylinder, in which a bidirectional piston
is positioned. On
each sides of the piston has the cylinder an inlet and outlet valve, so that
the inlet valve of one
side is communicating with an outlet valve at the other side of the piston.
Thus the total
accumulated volume on both sides of said piston may remaim constant - this may
lead to the fact
that it is possible to move the piston from one side of said cylinder to
another side, without
consuming fluid. Either pressure is consumed. That means that there only would
be e.g.
electricity present forcontroting said valves, and this could very well come
from anb accumulator
which is loaded by a sustainable power source, e.g. a solar photovoltaics cell
e.g. a volt and/or a
generator which may be connected to a main axle. This reduces the energy
needed still more for
this motor. We assume, that the pressure storage vessel has been loaded at the
production of the
motor.
Instead of the bidirectional actuator an electric step motor may be used,
controlled by a computer.
Such a motor may be precisely and quickly enough react on controling impulses
from said
computer.
Or, the system shown in Fig. OF references 1093 and 1094 may be used here.
Addition to the description of preferred embodiments for Fig. 11F
CA 02786315 2012-08-24
0 Z
CA 02786315 2012-08-24
The holes in the piston rod 805 within the container piston 810 have not been
shown
in the container piston 810 - these however have been shown already in Figs.
2B, 2C, reference
201, and should be present in the Fig. 11F.
Addition to the description of preferred embodiments for Fig. 13F
The holes in the piston rod 805 within the container piston 810 have not been
shown
in the container piston 810 - these however have been shown already in Figs.
1B, 1C, reference
201, and should be present in the Fig. 13F.
20
- CA 02786315 2012-08-24
Regarding the pressure management system for Figs. 11A, 115, 11C
When an actuator piston, which is connected to the main axle by. a crankshaft,
where
the fluid within said actuator piston is depressurized, and thereafter
pressurized by a system,
where the space within the piston is sequentially connected and disconnected
with a
repressuration pump and a pressure storage vessel, respectively, (Figs. IIA,
11B, I ID), the
following remarks are being made.
Just when having reached the turning point at the farthest second longitudinal
position, when an actuator piston - depressurized - is moving from a first to
a said second
longitudinal position, a communication is made between the pressure vessel
(e.g. Fig. 11B - ref.
314) and actuator piston, so that the piston is being pressurized immediately
when having been at
the farthest second longitudinal position. At that moment, there is (shortly)
an open connection
through two holes, one in the crankshaft and one in the connection rod,
between said pressure
storage vessel through the second enclosed space of said crankshaft and the
enclosed space of the
piston rod, and the holes in said piston rod within the container, which
contineously communicate
between the space within said container and the enclosed space.
This means that during the stroke from a second to a first longitudinal
position the
enclosed space of said piston has temporary a constant volume, which means
that due to the
increasing volume of said container (from etlipsoide with a smaller
circumference to an ellipsoids
with a bigger circumference I etlipsoide - sphere / sphere with a small
diameter to a sphere with a
bigger diameter), when moving, that the internal pressure within said
container is being reduced
contineously.
And when arriving to the farthest first longitudinal position, the internal
pressure of
said container may have been reduced, but may not have become to atmospheric
level. lust before
or just at the returning point at the farthest first longitudinal position,
when returning to a second
longitudinal position, a communication may take place between the space within
the container, the
holes between said space and the enclosed space of said container within the
piston rod and the
connection rod, with the third enclosed space in the crankshaft through two
holes, which at that
point of time have corresponding centre axles, one in said connection rod, the
other in the
crankshaft.
CA 02786315 2012-08-24
24f
The pump; which communicates with said third enclosed space and is, at that
moment, sucking for fluid from said container, so that the container is
depressurized.
The second enclosed space may be pressurized constantly by a constant open
communication with the pressure storage vessel. It may also that this
connection is controlled by a
valve.
Addition to the description of preferred embodiments for Fig. I IA, 11B, 11C.
The holes in the piston rod 805 within the container piston 810 have not been
shown
in the container piston 810 - these however have been shown already in Fig. 2B
and 2C,
reference 201, and should be present in the Figs. 11A, 11B and tIC
CA 02786315 2012-08-24
Regarding a pressure management system for Figs. 12A, 12B, 12C, 13A, 13B
In the case of a circular chamber, which is a chamber having a central axis
which is
circleround, with the same pressurization system as earlier mentioned for a
crankshaft solutions
(Figs. I IA, 11B, I ID), similar solutions may be valid in said circular
chambers, but in a bit
adapted way.
In case df a moving piston and a non-moving chamber (Figs. 12A, 12B, 12C) the
sphere piston may be comprising an enclosed space which may be communicating
trough a hole in
the piston rod, with the space inside the container, and at the other end may
the enclosed space
communicating with a second enclosed space, which may be positioned in the
main axle. The last
mentioned may be communicating with a two way valve in a housing, which may be
build around
the main axle. A separator valve may be a T-valve, of which the shared portion
is communicating
with said second enclosed space. One of the non-shared portions may be
communicating with a
pressure storage vessel (e.g. reference 814) (high pressure) and the other
(lower pressure) with
the pump (e.g. reference 818). The control of which way said separator valve
is opening and
closing may be done by a computer, which is monitoring the position of the
main ache in
comparison with the opening of the enclosed space and the opening of the
second enclosed space
in said main axle. It may also be done by a camshaft, which is communicating
with the main axle.
Because the number of single chambers is 4 in Figs. 12A and 12B, there ought
to be 4
outlet/inlets to the second enclosed spaces be in the main axle, and also 4
inlets/outlets to the T-
valve, Or there may exist 4x T-valves. Between the T-valve (low pressure end)
and the pressure
storage vessel (e.g. reference 814) a pump (e.g. references 818, 826) may be
added, so that the
pressure is liftet up to a bit over the pressure in said pressure storage
vessel. All this makes this
solution be non-optimized, e.g. the transitions from and to the second
enclosed space in the main
axle may cause leakages.
In case a piston is non-moving and a chamber is moving (Figs. 13A, 13B), there
may be e.g. 5 pistons, each in a sobchamber, which all have the same central
circleround axis,
while all subchamber are positioned in continuation of each other, and are
communcating with
each other. Each piston is communicating with a T-valve in the same way as
mentioned above in
case the piston was moving and the chamber non-moving. Also the pressurization
system may be
CA 02786315 2012-08-24 rLG1 250
alike - the only difference is that there are 5 T-valves, which may be
opening/closing at different
point of times, as the position of each piston may be different in identical
subchambers.
Instead of piston pumps may centrifugal pumps be used (Fig. B). The efficiency
of
centrifugal pumps may be lower than that of the piston pumps with a conaicat
shaped chamber..
Addition to the description of preferred embodiments for Figs. 12A-C, 13A-F
The holes in the piston rod 805 within the container piston 810 have not been
shown
in the container piston 810 - these however have been shown already in Figs.
IB, 1C, reference
201, and should be present in the Figs. 12A C, 13A-F.
Addition to the description of preferred embodiments for Fig. 12C.
The return channel 1150 from the 1074 to the pump 1151, of which exit is
connected by channel 1152 to the storage pressure vessel 1075. The pump 1151
may be connected
(not shown) to the main axle 966 and/or to an external sustainable energy
source, such as solar
power (not shown).
Addition to the description of preferred embodiments for Figs. 12A-C (incl.),
13A-F (incl.).
The holes in the piston rod 805 within the container piston 810 have not been
shown
in the container piston 810 - these however have been shown already in Figs.
IB, 1C, reference
201, and should be present in the Figs_ 12A-C, 13A-F-
Addition to the description of preferred embodiments for Figs. 13A,13B, 13E.
The valve box 1160 is comprising 5x T-valves 1161 - 1165 (incl.) which are
opening up for either the communication [829] from the pressure storage vessel
814 to each of the
pistons 868, 869, 870, 871, 872 (see Fig. 13C) drough piston rods 873, 874,
875, 876, 877, or
to channel [817] to a repressuration pump 818, and indirectly to 826-The
pressurized return
channel [825] and/or [828] from said pumps to the pressure storage vessel 889.
CA 02786315 2012-08-24
The remm chancel 1150 from the 1074 to the pump 1151, of which exit is
connected by
channel 1152 to the storage pressure vessel 1075. The pump 1151 may be
connected (not shown)
to the main axle 966 and/or to an external sustainable energy source, such as
solar power (not
shown).
10
~JS 2
CA 02786315 2012-08-24
19618 - updated Figs 11A-Z based on 19617 (in main document 19601)
Fig. I1A shows schematically the overall system for a ('green') motor, which
is complying to all
demands, as stated in the Background of this invention chapter. On a
schematically drawn crankshaft 800
with a U-shaped axle 801, with axle bearings 802 and 803, contraweights 804,
is a piston rod 805
assembled, which is on the other side of said piston rod 805, connected to an
expandable piston 806, which
is shown Left "U' in a movement (arrowed) from first to second longitudinal
positions, and Right "R" in a
movement (arrowed) from second to first longitudinal positions. Said piston
806 is engagingly movable in
a chamber 807 with an internal wall 808. Said chamber 807 has cross-sections
with contineously differing
cross-sectional area's and differing circumferences, and of which the internal
wall 808 has a circumference
which is at second longitudinal positions smaller than at first longitudinal
positions. The piston 806 has
been produced, so that its unstressed production size of the circumference is
approximately the size of the
circumference of the wall 808 of said chamber 807 at a second longitudinal
position. Said piston 806 is
connected to the piston rod 805 by a cap 809, while the flexible wall 810 of
said piston 806, is comprising
reinforcement means 811, and is connected to the piston rod 805 by a slidable
cap 812, which can slide
over the piston rod 805. When said piston 806 being positioned at a second
longitudinal position, and is
communicating through its enclosed space 813 with a pressure source, e.g. a
pressure vessel 814, through
a second enclosed space 815 in said crankshaft 800 (axel 801), so that said
piston 806 is being pressurized
by a fluid 822, said piston 806 will begin to move from a second longitudinal
position to a first
longitudinal piston position, thereby rotating said U-shaped met 801 around
the bearings 802 and 803.
Said movement will change the direction of the movement of said piston 806
into an opposite direction,
namely from a first to a second longitudinal piston position. The enclosed
space 813 of said piston 806
may then be communicating with a third enclosed space 816 in said crankshaft
800 (axel 801), which is
connected through a channel [817] to a piston pump 818 (which may also be
instead a rotation pump, e.g.
a centrifugal pomp), which is connected by a piston and 819 to a crankshaft
820, with the U-shape axel
821. The crankshaft 820 may be connected to crankshaft 800, so that the
rotation of the U-shaped axle 801
results in a rotation of said U-shaped axle 821. Due to said communication is
the pressure of the fluid 823
inside said piston 806 be reduced, thus is the circumference of the wall 808
decreased, so that said piston
806 is being able to move from first to second longitudinal piston positions.
The fluid 823 is at a reduced
pressure (in relation to the pressure of the fluid 822 it had, when the piston
was pressurized at a fast
cLc
CA 02786315 2012-08-24
longitudinal position) is thereafter pressurized by said pump 818 to fluid 827
(of which pressure is of
course still less than the pressure of fluid 822) and which is optionally
directly transported to said pressure
vessel 814 through channel [824], dr is preferably transported by channel
[825] to another piston pump
826, whereafter said fluid 827 is being pressurized in said pump 826 into
fluid 822, and thereafter
transported through channel [828] to pressure vessel 814. From pressure vessel
814 is fluid 822
transported to the second enclosed space 815, through channel [829]. Piston
pump 826 is electrically
driven by motor 830 through another crankshaft 831. Said motor 830 may be
connected with an electrical
storage, e.g. an accumulator (or a condensator ('capacitatur') storage type)
832, which is connected to a
solar cell 833. The electric motor 830 is capable of being used as as a
starting motor for the rotation of said
crankshaft 800. This may be done by a clutch 836 (not shown). The crankshaft
800 may be connected to a
flywheel 835 (not shown), and a gearbox 837 (not shown) - mid gearbox 837 may
be using Fluid
Dynamic Bearings in order to reduce friction. The bearings 833 for the
crankshaft 821 of the piston pump
818. The alternator 850 is communicating with the main axle 852, and is
charging the battery 832 through
connection ..........The configuration 851 of auxilliarly power sources is
shown in Figs. 15A, 15B, 15C or
15E.
Fig. 11B shows schematically the control devices for the motor of Fig. 11 A.
The electric starter
motor 830 is comprising a clutch (not shown), connecting the axle 803 with the
anker of the electric motor,
when the motor needs to be started. An electric switch 838 can turn said
starter motor 830 on and off, by
connecting it to the battery ('accumulator') 832, which is being loaded by the
solar cells 832. Said motor
830 will also he able to be stopped, when the pressure in the pressure vessel
814 meets a certain maximum
limit, and said pressure measurement is being done by a pressure sensor 839.
The motor may also start without using the starter motor 830, but just by
opening up the reduction valve
840, in the channel 829. Opening this reduction valve 838 more up causes the
crankshaft 801 to rotate
more quickly, screwhsg the reduction valve 838 down causes the crankshaft 801
to rotate slower. Closing
the reduction valve 838 completely will stop the motor. The speeder 841 is
communicating with the
reduction valve 838. The alternator 850 is communicating with the main axle
852, and is charging the
battery 832 through connection 842. The configuration 851 of anxilliarly power
sources is shown in Figs.
15A, 15B, 15C or 15E.
25`1
CA 02786315 2012-08-24
Figs. IlA-F (incl.) concern motor with an elongate cylinder and a piston
communicating with a
crankshaft, according to the Consumption Technology.
Fig. 11C shows the actuator piston pressure management of Figs. 11A and 11 B.
At the point of
time when the piston has arrived from a 1st longitudinal position at the final
2na longitudinal position of
the chamber - that just after having reversed the direction of its motion -
there starts a communication
between the high pressurized second enclosed space 822 of said crankshaft,
through a hole in said
crankshaft and a hole at the end of said piston rod with the enclosed space of
said piston rod and thereby
also with the internal volume of the piston through holes...., so that the
piston pressurizes to the maximum
pressure rate. Due to its pressumtion will the piston beginning to move to a
In longitudinal position,
thereby turning the crankshaft and closing said holes, so that said
communication stops. Said movement is
reducing its internal pressure due to its increased inside volume, due to the
fact that the ellipsoids shaped
piston is beginning to transform itself into the shape of a sphere. When
having arrived at the In
longitudinal position there is still a medium rate of pressure left in said
piston and the enclosed space
within the piston red. When said piston has arrived at the prima In
longitudinal position on its way back to
a 2"a longitudinal position - thus just after ]raving reversed the direction
of its motion, the enclosed space
within the piston rod will begin to communicate through a hole at the end of
the piston rod, and with the
third enclosed space 823 within the crankshaft which is comprising a hole. The
pressure inside the piston
and the enclosed space drops to a certain minimum (e.g. atmospheric level), so
that the shape of the piston
is changing from a sphere to an ellipsoide. Due to the enertia of the
crankshaft (or the driving force of
another piston-chamber combination using the same crankshaft) the deflated
piston will move to a second
longitudinal position, and the process starts all over again.
The communications between the enclosed space of said actuator piston and the
second and third
enclosed spaces, respectively in the crankshaft may make that said piston may
have to stop at a certain
longitudinal position, in order to be able to move again, just by opening up
the reduction valve, as the
pressurized fluid needs to be able to mach the piston. That may only be a
problem, when there is only one
actuator piston-chamber combination on a crankshaft on one axle, where the
piston may stop at a 1"
longitudinal position, and may be returning a bit on its way to a second
longitudinal position due to
Inertia. Said holes of said enclosed spaces may than not be able to
communicate with each other - starting
may than only be possible by using a starter motor.
CA 02786315 2012-08-24
2cc
The pressure drop in the piston may be caused by a suction in the third
enclosed space 823,
caused by the piston pump 818, being taking in fluid from channel [817]. The
pressure drop in channel
[817] may begin to happen a bit before the actuator piston is reversing its
direction of motion from being
approaching a 1" longitudinal position to a second longitudinal position, so
that when said holes of the
enclosed space and the third enclosed space open up, the fluid may be sucked
out of said enclosed space of
the actuator piston. That means that the default angle between the crankshaft
801 of the actuator piston
810 and the crankshaft 821 of the piston pump 818 may be different from zero.
The main axle 852.
Details of the assembly of the piston rod 805 and the the U-bend axle 801 are
shown in Fig. 11 D. Details
of the joint of the piston rod 805 and the connecting rod 925 are shown in
Fig. I1E. Details of the
assembly of the piston rod 819 of the pump 817 with the crankshaft 821 are
shown in Fig. 1 IT. Details of
the guidance of the connecting rod 925 and the piston rod 819 may be seen in
section 19597 of this patent
application.
As another preferred detail: there may he a combined assembly comprising two
check valves with each a
valve actuator according to preferably Fig. 210F or optionally Fig. 210E from
the 2"d enlosed space 822 of
the crankshaft 821 to the space 813 of the piston rod 805 and the same
assembly comprising a check valve
with a valve actuator according to preferably Fig. 210F Or optionally Fig.
210E from the space 813 of the
piston rod 805 to the third enclosed space 823. It may also be two separate
assemblies, each comprising a
check valve 522 with a sub-assembly 520 comprising a valve actuator according
to Figs. 304 and 301: one
from the 2"d enlosed space 822 of the crankshaft 821 to the space 813 of the
piston rod 805 and the same
assembly in opposite direction comprising a check valve 522 with a sub-
assembly 520 comprising a valve
actuator according to Figs. 304 and 301 from the space 813 of the piston red
805 to the third enclosed
space 823.
Fig. 11D shows the assembly of the piston rod 805 and the U-bend axle 801 of
Fig. 11C, and is
shown on a certain point of time, where the piston rod 805 and the U-bend axle
801 are turning over each
other. The U-bend axle 801 on which the piston rod 805 has been assembled with
a bearing 1100, 1100'
and 1100", and the 0-rings 1104,1104', 1104" and 1104"' between the piston rod
805 and the axle 801.
The enclosed space 813 is communicating with the third enclosed space 816
(with fluid 823) through
(currently) hole 1102. The second enclosed space 815 with fluid 822 is
communicating with current blind
hole 1101, and is thus currently not communicating with the enclosed space
813. The separator 1103,
CA 02786315 2012-08-24
which is separating the second enclosed space 815 and the third enclosed space
816. At another point of
time is the current hole 1 102 becomes a blind hole, while the current blind
hole 1101 has become a hale.
Said holes 1101 and 1102 are never commnicating with the enclosed space 813 at
the same time. The base
926 of the piston red 805 is comprising two parts 927 and 928, where the
centre axis 929 of the channels
822 and 823 are lying in the separation surface (not shown) of said base 926.
Two bolts 830 and rings 831
on each side of the piston rod 805 are holding the two parts 927 and 928
together.
Fig. I1E shows a detail of the joint of the piston rod 805 and the connecting
rod 925 (8051),
shown in Fig. I I C. Piston rod 805 is having an end 932, which is comprising
a channel 933 which is
communicating with the 2"a enclosed space 822 and the 3rd enclosed space 823
on one side, and the other
side to the enclosed space 813 of the piston 810. Both enclosed spaces are
communicating with each other
through a space 941, between the hole 945 in the outer wall 943 of the end 932
of the piston rod 805, and
the hole 946 in the inner wall 944 of the connecting rod 925. The end 942 of
the connecting rod 925 is
comprising an O-ring 939, which is sealing said end 942 to the end 932 of said
end 932 of said piston rod
925. Said axle 940 is firmly connected (not moving) into said end 932. The end
932 of the piston rod 805
is comprising of two parts 934 and 935, which are bolted together by bolt 936
and washer 937 one on each
side of the center line 938 of the assembly. The connecting rod 925 can turn
over the end 947 of said axle
940. Said end 947 has a increased diameter in relation to the diameter of the
axle 940, in order to create a
shoulder 953. The parts 934 and 935 of the end 925 have a 90 bearing 948
which is also the bearing for
the movement of the end 942 over the end 932. The 0-ring 950 is sealing the
axle 940 on the hole 947 of
said connecting rod 925.
Fig. IIF shows a detail of the crankshaft 801, and a channel (e.g. 823) inside
said crankshaft,
which is shown in Figs. I IA-C. The channel 823 may be drilled out, after a
preliminary hole has been
made by forgery, during the production process of the crankshaft 801. This
drilling leaves holes in the
outer walls 953 of the crankshaft 801, and these holes may be closed by any
means, such as welded rods,
sealed threads etc. Shown in the drawing is a pin 954 with a head 955, the pin
having a very fine fit to the
hole in the wall of the crankshaft, where the in between space is being filled
by hard soldering. Important
is the proper balancing of the crankshaft 801 at the end of the production
process.
CA 02786315 2012-08-24
Figs. 1IG-W (incl.) concern a motor with at least one elongate cylinder and a
piston
communicating with a crankshaft, according to the Enclosed Space Volume
Technology (abbreviated by
'ESVT').
Figs. 11G and 11H show the basic ESVT in two variants, regarding the
pressurizing of a storage
pressure vessel, where the pumps which are controlling the volume of the
enclosed space, are driven by a
2-way actuator. Clearly are the different power lines shown, separating the
use of the power, generated by
the auxilliarly power sources.
Fig. 11G shows schematically a configuration of Fig.11A, adapted to the ESV-
Technology, with
the U-shaped axle 801' comprsing two counterweights 804, the piston rod 805
and the inflatable actuator
piston 806. One end of said axle 801' may be connected to an electric starter
motor 830, which may get its
energy from an accumulator 832 - the last mentioned may be loaded by a solar
cell 833, and/or any other
preferably sustainable (or optionally non-sustainable) power source (please
see Figs. 15A-F). At the other
end may the axle 801' be connected to a flywheel 835 (not shown), a clutch 836
(not shown), and
optionally a gearbox 837 (not shown).
Inside said U-shaped axle 801' is a channel 1050 which is communicating
constantly with an
ESVT pump1055, comprising a piston 1061 (e.g. shown according to Figs. 50-52
(incl.)), and an conical
chamber 1062, which is regulating the extra pressure upon the overall pressure
in said channel 1050. Said
extra pressure is controlling the speed of the motor. The motion of said ESVT-
pump 1055 is generated by
a 2-way actuator 1053, which is controlled by two reduction valves 1057 and
1058, respectively, where
each reduction valve is regulating the pressure at one side of the piston (not
shown) inside said 2-way
regulator 1053. Said reduction valves 1057 and 1058 are interconnected
preferably electrically (and
optionally mechanically - other solutions exist but are not schown), so that
an increase of the pressure of
one (side of said piston) will result in a simultaneously decrease of pressure
of the other (side of said
piston) and vice versa. Reduction valve 1057 is controlled by a speeder 841,
through a control device 840.
Said reduction valves 1057 and 1058 are communicating with a pressure storage
vessel 890, through a
feeder line [829]. Said pressure storage vessel 890 may have been pressurized
with a fluid 1063 when this
motor was produced.
D,l
CA 02786315 2012-08-24
Said channel 1050 is additionally constantly communicating with the piston rod
805 of an FSVT-
pump 1056 -please see Fig. 1IT for details of the assembly of said connection
rod with the axle 801'.
Thus, a change in the volume/pressure of said ESVT-pump may be resulting in a
change of the
volume/pressure in the actuator piston 806 and thus in the motion of said
actuator piston 806.
The ESVT pump 1056, comprising a piston 1059 (e.g. shown according to Figs. 50-
52 (incl.)),
and an conical chamber 1060 is driven by a 2-way actuator 1056 regulates the
pressure of the channel by
changing the volume of said channel, so that the actuator piston 806 is
changing volume at a certain
longitudinal position, according to Figs. I OA-F. Said 2-way actuator 1072 is
driven by the reduction valves
1051 and 1052 in the same way as the ESVT-pump 1055, by 2-way actuator 1072.
However, the reduction
valve 1051 is being controled by a sensor 1064 and communicates [1054] the
rotational position of the
axle 801 to said reduction valve 1051, so that the piston 806 may be expanding
and contracting at the right
point of time, due to the pressure change. The reduction valves 1051 and 1052
may be communicating
[829] with a pressure source, e.g. said pressure storage vessel 890. The other
side of the enclosed space
may be communicating constantly with the enclosed space 813 of the piston 806.
Said reduction valves
and related equipment are electrically communicating through wire [1064] with
the battery 832.
Fig. I Ill shows the configuration of Fig. 1IG (with components with
references for which is
refered to Fig. 11G), where the pump 826 for repressuration of the pressure
storage vessel 890 has been
added - the repressuration cascade is identical with that shown in Fig. 11A,
however, the pump 820 may
be redundant, because it may be needed for the 'Consumption Technology',
providing a low pressure in
the 3`a enclosed space, at the right point of time, enabling depressurization
of the actuator piston 806, but
may not needed for the currently used FSV Technology. The outlet [1070] of the
2-way actuator 1072 is
communicating with the pump 820, but can be connected to the outlet [1071] of
the 2-way actuator 1072,
when the pump 820 is not present, by connection [1073]. The necessary check
valves are not shown. In
this ('consumption') configuration of the 2-way actuators 1053 and 1072 are
the spaces at both sides of the
piston inside the chamber of the 2-way actuators, directly communicating with
the pump 826, which is
communicating with the presume storage vessel 890, and with the reduction
valves 1051, 1052, 1057 and
1058 respectively, which then are communicating with the inlets of said 2-way
actuators 1053 and 1072,
respectively, to the spaces at both sides of said piston (please see Fig. 11
fora schematic view inside the 2-
way actuator 1053'). The necessary check valves are not shown. Said reduction
valves 1057-1058 and
CA 02786315 2012-08-24
2Se
1051-1052, respectively, are related to each other, in such a way that if one
valve is being openened more,
the other valve is simultaneously closing more. The valve means 841 of the
reduction valve 1057 is being
activated by a speeder 841, while the reduction valve 1051 is activated by
sensor 1064. The reduction
valves are being electrically activated.
The alternator 850 is communicating with the main axle 852, and is charging
the battery 832
through connection [1075]. The configuration 851 of other auxilliarly power
sources is shown in Figs.
15A, 15B , 15C, 15E or 15F. The pump 826 may also communicating with a
flywheel (not shown) and/or
a regenerative breaking system (not shown). The use of other auxilliarly power
sources is possible, as
stated in the drawing: preferably according to Figs. 15A, 15B, 15C, 15 E, 15F
and obtionally non-
sustainable power sources.
Figs. 111 - 1lN (incl.) show a one (Figs. 111, 11K, 1 1M) and a two cylinder
motor (Fig. 11J,
1 IL, I1N), respectively, where said motors have been partially worked out for
the main construction
elements (e.g. axles and e.g. wheels and belts / gears), which are
communicating with each other. The
ESVT pump, which is controlling the volume of the enclosed space is powered by
a 2-way actuator (Figs.
111, 11J) according to the configuration shown in Fig. 11 H, a crankshaft
(Figs. 11K, I1 L) or a camshaft
(Figs. IIM, I IN), respectively. Due to the different sizes of the loops of
said power types, the conical
cylinders may have different sizes per each power type. The auxiliarly power
sources are only referred to
by reference number. The use of other auxilliarly power sources is possible,
as stated in the drawing:
preferably according to Figs. 15A, 158, 15C, 15 E, 15F and obtionally non-
sustainable power sources.
Each drawing which is comprising a two cylinder motor is consisting of a
"left" and a "right" sealed up
drawing.
Figs. 111 - 11R (incl.) show several configurations of a one cylinder motor,
and a two cylinder
motor. One of the aims is to show the clear updividing of the power delivered,
and the power used - this
has been also disclosed schematically in Figs.15. Another aim is to show the
differences between
controlling the pressure rebuild of the actuator piston(s) by either wires, by
a camshaft br by a crankshaft
which may be communicating to the power delivered. In order to enhance the
efficiency of the power
delivered, Figs. ]to - 11R show a small combustion motor, using preferably H2
as power source
(preferably derived from hydrolyses of H20), which is directly communicating
wills a camshaft or a
26o
CA 02786315 2012-08-24
crankshaft. Several configurations are being shown of this combustion motor.
Another aim is to show how
the controlling means of the pressure per cylinder, may be combined or not in
a more than one cylinder
motor - it showed to be necessary to find out firstly how the subsequent
cylinders would be working in
relation to each other, under condition of a combined crankshaft: please see
Figs. 17A,B-H (inct.) where
the power strokes of one of the two cylinders of the same motor is done
simultaneously with the return
stroke of the other cylinder (serial power), while in Figs. 18A-G (met.) the
power strokes of the two
cylinders of the same motor are funetionning at the same time (parallel
power). Thereafter, it is concluded
which pressure controlling means (e.g. ESTV pumps) may be combined for said 2
cylinders or not, and
whether or not the power lines (e.g. camshaft crankshaft) maybe combined.
in
Fig. III is showing a partially worked out one piston-chamber combination 800'
motor, which is
mainly based on the concept shown in Fig. 11H, using a 2-way actuator 1072 to
drive the ES VT-pump
1056, which is controlling the size of the enclosed space 1050 + 813, and is
functioning as described in
Fig. 11H. The actuator 1055 (piston 1061, chamber 1062) is controlling the
speed of said motor. All
remarks regaring the presence or not of the pump 820 made in the description
of Fig. 11H are also valid
here.
Only new issues will be treated here.
Please see Fig. 11S for the details of the assembly of said actuator 1055 onto
said axle 852. The
top 1130 of the chamber 1062 of the actuator 1055 has been mounted on the
motor mainframe 5000. The
arrangement of the communication between the enclosed space 1150 of the axle
852 and the chamber
1062 canbe seen in Fig.11S as well.
The actuator 1053' which is changing the speed of said motor has been
partially worked out, and
is working in a bit different way than the actuator 1053 shown in Fig. 11 H,
because said actuators 1053
and 1072 have different functions. In the configuration shown in this drawing
of the actuator 1053 are the
spaces 1075 and 1076, respectively on both sides of the piston 1078, within
said chamber 1079,
communicating with each other through a number of check valves (not shown
here) - please see Figs.
16A-C (incl.) for details. Thus, there is no return flow from said spaces 1075
and 1076 through a pump
826 to the pressure storage vessel 890. This may reduce energy.
Said spaces 1075 and 1076, respectively arc communicating with said reduction
valves 1057 and
1058, respectively. Said chambers are additionally communicating with each
other through valve actuator
CA 02786315 2012-08-24
2,61
arrangements 1121 and 1122, respectively, shown in Fig. 304, and when
necessary may these additionally
be controlled according to Figs. 211E or 211F. Said valve actuator
arrangements 1121 and 1122 are being
positioned in opposite direction to each other. The chamber 1079 of the
actuator 1053 has been mounted
on the motor mainframe 5000. More details are shown in Figs. 16A-C.
The ESVT-pump 1056 is comprising a chamber 1060 and a piston 1059, has been
mounted on
the main axle 852 - please see Fig. I IU for suspension details. Said 2-way
actuators 1053 and 1072 are
driven by a compressed fluid 1063, which has been stored in a pressure storage
vessel 890.
The pump 926 of Fig. 11H has been worked out in detail in Fig. 11V. It gets
its energy from an
electric motor 831, which receive electricity through an electric
communication [1080] from a battery 832.
The circular movement of the axle of said motor 831, is being conversed by a
kind of crankshaft 1217 to a
translation, and partially a rotation. When the pump 820 is not present, will
the flow from the 2-way
actuator 1072 be communicating by channel [1083] to said pump 926. Compressed
fluid is coming from
said pump 926 through channel [828] to the pressure storage vessel 890. The
alternator 850 is
communicating with the main axle 852 through a tooth belt 1073 and wheels 1074
and 1075. It delivers
electric power to the battery 832, through the electric communication [1086].
, aid reduction valves 1051 and 1052, with controlling eomsection [1054] to
the cylinder (800), a separate
crankshaft 1128 is being used to power said actuator 1050. The timing is
controlled through a timebelt
1129. Said timebelt 1129 is connecting the axle 852 through a crankshaft
pulley 1130 which has been
mounted on axle 852, with the crankshaft pulley 1131 which has been mounted on
the axle 1132 which is
comprising said crankshaft 1128. Said timebelt 1129 is comprising tooth
(preferably Bad), in order to
avoid slip (and thus changing the timing). Said axle 1132 is rotationally
mounted in the motor mainframe
5000 (not shown).
Fig. 1IJ is showing an overview of a two cylinder motor, while particulars are
shown in the
scaled up Figs. I It left and 11J right
266
CA 02786315 2012-08-24
Fig. 112 is showing a partially worked out two cylinder motor, based on the
concept shown in
Fig. 111. Particulars are shown when combining two crankshafts, and having the
benefit of one
construction element for multiple similar tasks. In a two cylinder motor are
there not many of the last
mentioned, because of showing here an example, where the two actuator pistons
may not be in the same
longitudinal position, at the same moment (asyncrone crankshaft design)
according to Fig. 17B. Each
"cylinder", better designated as 'chamber' has an enclosed space comprised in
its crankshaft, herinafter
designated as 'sub-crankshaft', which have been separated from each other by
e.g. a tightening rod 1270
(Fig.11X) i between the channels of each sub-crankshaft.
Thus each actuator piston has an ESVT-pump controlling the volume of each
enclosed space,
while each ESVT-pump is driven by a 2-way actuator. As the actuator pistons
have to bemoving
(a)synchrone, may it be necessary that the pressure reduction valves of each 2-
way-actuator are
communicating with each other, e.g. electrically. However, it may also be that
said pressure reduction
valves are commincating through the sub-crankshafts, each by its sensor
measuring the rotation of each
sub-crankshaft. Whether or not the two ESVT-pumps may be combined into one,
cannot be concluded
without substantial investigations: please see Fig. 17C-17H (incl.).
And, thus there are two speeder-actuators, which have to be communicating with
each other. This
may be done through the speeder 841 - one speeder, which is controlling e..g.
electrically both pressure
reduction valves of each 2-way actuator. Whether or not the two 2-way
actuators may be combined into
one, cannot be concluded without substantial investigations: please see Fig.
17C-17H (!net.).
There may be two or only one pressure storage vessel, which has been
pressurized Ex. Works, and
which is being repressurized during operation by a pump. It may possible that
there is one pump, which
may be driven by electricity from a battery, which has been charged Ex.Works,
may be recharged during
operation by an alternator, communicating with the main motor axle. It may
also be possible that this
battery is charged by an external electrical power source through e.g. a
cable. It may be possible to
repressurize said pressure storage vessel through a hose, which is
communicating with a pressure source,
such as preferably a medium pressure canister or optionally a high pressure
canister, bran external pump
(e.g. driven by a windmill - most efficient). Auxilliarly power sources are
according Figs. 15A,B,C,E,F.
Firstly when there are 3, or better 4 and even pairs over 4 cylinders in one
motor, will there be a
chance to combine the inlet/outlet of 2-way actuators for speed control, and
the inlet/outlet of ESTV-
CA 02786315 2012-08-24
pumps, so that the total number of said 2-way actuators and pumps may be
reduced. Please see Figs. 17C-
17H (incl.).
The pump 820 may be redundant.
The two sub-crankshafts on the main motor axle are connected to each other, by
a connector of
which details are shown in Figs. I1W, 11W', 11X, which may be a little bit
flexible in a plane
perpendicular that of the centre axis of said crankshaft, in order to
compensate for a possible timing
difference of the changes of shapes of said actuator pistons, due to elastic
characteristics of the wall of said
actuator pistons during repressuration.
Fig. 113 left shows a scaled up left part of Fig. 1I3. Only new issues will be
treated here.
Fig. I IJ right shows a scaled up right part of Fig. 113.Only new issues will
be treated here.
Fig. 113 is showing an overview of a one cylinder motor, while particulars are
shown in the
scaled up Figs. 11J left and 11J right.
Fig. 11K is showing a one cylinder motor, which is based on the concept shown
in Fig. 11 H,
where instead of a 2-way actuator, an auxilliarly crankshaft is used to drive
the ESVT-pump. Said
auxilliarly crankshaft is driven by an electric motor, which is powered by
said battery. Said battery is
recharged during operation by an alternator, which is communicating with the
main motor axle. Due to the
used for co-ordinating the speed of the speed-actuator with the speed of said
ESVT-pump, the controls of
both: the speeder 841 / pressure reduction valve 1057 and said electric motor
3500 are communicating
with each other by wire [3501] through an electric/electronis regulator 3502.
Wire [3547] is connecting the
speeder 841 with a regulator 3509, controlling the production level of H2 and
O2 through electrolyses. The
motor 3500 is driving the crankshaft 3503 through e.g. a toothbelt 3505 and
wheels 3506 and 3507., which
is driving the ESVT pump 1056. Said electric motor 3500 is connected to the
battery 832 by wire [3504],
through said regulator 3502.
26li
CA 02786315 2012-08-24
The fact that a (auxilliaeiy) crankshaft is used for driving the ESVT-pump,
which is mounted on a
fixed crankshaft axle, there may be a connecting rod, which connects the
piston rod of the ESVT-pump
with the crankshaft (as we have seen in Figs. IIC for the actuator piston) or
that said connecting rod is
missing, and that a similar the oscillation construction of the pump shown in
Fig. 11 V is being used, where
the chamber 1060 of said ESVT-pump, incl. the top 1130 and the piston rod are
turning around said
crankshaft which is communicating with said main axle 852. The assembly of the
ESVT-pump on the
main axle is as such the same as if the pump was not oscillating (e.g. see
Fig. 11U, but the fits of the
bottom of said pump to the axle may be slightly bigger.
Because the 2-way actuator 1072 of the ESVT-pump has been exchanged by an
auxilharly
crankshaft, and the fact that the 2-way actuator 1053 may not need
repressuration, rather than keeping the
pressure storage vessel pressurized, which may demand a limited
repressuration, the pump 826 may be
smaller than the one shown in Fig 111. This is a preferred solution, while a
solution of having a pump 820,
while pump 826 has been redundant is an optional solution.
Fig. I IL is showing an overview of a two cylinder motor, while particulars
are shown in the
scaled up Figs. 11 L left and 111, right.
Fig. IIL is showing a two cylinder motor, based on the concept shown in Fig.
I1K, where each
cylinder has an enclosed space, and than an ESVT- pump controlling its volume
each, which both are
driven by the same auxilliarly crankshaft axle.
Due to the need for co-ordinating the speed of the speed-actuators with the
speed of said ESVT-
pumps, the controls of both: the speeders 841 / pressure reductions valve 1057
and the electric motor
.......me communicating with each other, when both ESVT-pumps are using the
same axle comprising both
crankshafts.
Because the 2-way actuator 1072 of the ESVT-pump has been exchanged by an
auxilliarly
crankshaft - this maybe made as one piece due to the fact that the assembly of
the connection rod and the
crankshaft is simple (no channel) - and the fact that the 2-way actuator 1053
may not need repressuration,
rather than keeping the pressure storage vessel pressurized, which may demand
a limited repressuration,
the pump 826 may be smaller than the one shown in Fig 1 IJ. This is a
preferred solution for a two cylinder
motor, while a solution of having a pump 826, while pump 820 may be no option.
CA 02786315 2012-08-24
Fig. i lL left shows
Fig. 1 IL right shows
Fig. 11M is showing a one cylinder motor, which is based on the concept shown
in Fig. 11H,
using a camshaft to drive the ESVT-pump, instead of the 2-way actuator.
Said camshaft is driven by an electric motor, which is powered by said
battery. Said battery is
recharged during operation by an alternator, which is communicating with the
main motor axle. Due to the
need for co-ordinating the speed of the speed-actuator with the speed of said
ESVT-pump, the controls of
both: the speeder 841 / pressure reduction valve 1057 and said electric motor
3500 are communicating
with each other, in the same way as shown in Fig. 11K.
The camshaft 3515 has a limited Night of the cam 3516 to lift the piston rod
of the ESVT-pump,
and that means that the ESVT-pump has a decreased stroke length, and an
increased widt of said chamber
than that of Figs. 11K and I 1L, in order to obtain the necessary change of
volume. Additionally may a
spring be needed, to let the piston reverse its motion, which had been
initiated by a cam.
Because the 2-way actuator 1072 of the ESVT-pump has been exchanged by an
auxilliarly
camshaft, and the fact that the 2-way actuator 1053 may not need
repressumtion, rather than keeping the
pressure storage vessel pressurized, which may demand a limited
repressuration, the pump 826 may be
smaller than the one shown in Fig 11I. This is a preferred solution, while a
solution of having a pump 820,
while pump 826 has been redundant is an optional solution.
Fig. I 1N is showing an overview of a two cylinder motor, while particulars
are shown in the
scaled up Figs. I1N left and 11N right.
Fig. IIN is showing a two cylinder motor, based on the concept shown in Fig.
11M, where each
cylinder has an enclosed space, and thus a pump controlling its volume, which
both are driven by the same
camshaft.
Due to the need for co-ordinating the speed of the speed-actuators with the
speed of said ESVT-
pumps, the controls of both: the speeders 841 / pressure reductions valve 1057
and the electric motor
26d
CA 02786315 2012-08-24
.......are communicating with each other, when both ESVT-pumps are using the
same camshaft axle.
SHOW THIS
Because the 2-way actuator 1072 of the ESVT-pumps have been exchanged by a
camshaft, and
the fact that the 2-way actuator 1053 may not need repressuration, rather than
keeping the pressure storage
vessel pressurized, which may demand a limited repressuration, the pomp 826
may be smaller than the one
shown in Fig I IJ. This is a preferred solution for a two cylinder motor,
while a solution of having a pump
826, while pump 820 may be no option.
Fig. 1IN left shows
Fig. I IN right shows
Figs. I10,P and II Q,R (incl.), respectively concern the configurations of
Figs. 11K,L
(crankshaft) and Figs. 1 IM,N (camshaft), respectively, where the auxilliarly
power source is, besides the
solar cells 833, a configuration according to Fig.15C, where a combustion
motor 3525 , preferably using
H2 (and optionally any other combustible power source), which has been
preferably generated by
electrolyses from conductive H2O (and from a canister under pressure - coole
and liquified or not), is
directly communicating with the F.SVT pump which is controlling the volume of
the enclosed space. The
fact that said combustion motor directly drives the power lines (ESVT-pump(s),
cmnkshaft/camshaft,
instead of first generating electricity, which drives an electric motor, means
that it is approximately 4 x
more efficient. Each drawing shows a different type of cooling for said
combustion motor. The by said
combustion motor heated fluid (e.g. air) may be used for heating purposes,
e.g. for heating the
compartment of a car.
Fig. 110 is showing a one cylinder motor, based on the above mentioned
concepts, using a
crankshaft for driving the ESVT pump. Only new issues are treated here.
In order to get said motor running properly it is necessary to synchronize the
several parts in said
motor:
26~
CA 02786315 2012-08-24
= the electrolyses of Hzo which results in a certain volume of Ha and Oi to be
used for the combustion
motor, driving the crankshaft, driving the ESVT-pump,
= the communication between the ESVT-pump and the 2-way actuator for the speed
actuator has been
treated in the description of Figs. 11K, 1IL, 1IM and 1 IN.
= the motor is also driving the pump 826 shown in Fig. I IV, for repressumtion
of the pressure storage
vessee 890, through a tooth belt and wheels
The configuration (according Fig. 15C) of the auxilliarly Hz combustion motor
is comprising a
storage tank for conductive Ha2O (which may be H2O from the tap and a
conductor, e.g salt, or just sea
water), with a filler opening and an outlet channel to the vessel wherein the
electrolyses of said water is
taking place. No check valves have been shown. The electric power line from
the battery 832 to the vessel
wherein the elctrolyses is taking place. The resulting Hi is transported
[3545] by a pump to said motor -
the very necessary check valves have not been shown. The resulting Oz is being
transported [3546] to said
motor as well by channel + pump -the very necessary check valves are not shown
- it is used as a kind of
turbo. Said HZ motor 3525 is shown in this drawing as being air cooled, where
the warm air is being
transported through a channel [3538], directly or indirectly by a liquid to a
heat exchanger 3539, e.g. for
warming up (arrows 3540) purposes of the cabin of a car.
Fig. 11P is showing an overview of a two cylinder motor, while particulars are
shown in the
scaled up Figs. I1P left and I IT right.
Fig. I IP is showing a two cylinder motor, based on the concept shown in Fig.
l lo, where each
cylinder has an enclosed space, and thus an ESVT- pump, which both are driven
by the same crankshaft.
and two speeder actuators., but one auxilliarly motor. The crankshaft is
directly driven through gear
wheels by a liquid cooled combustion motor, using Hz. Said crankshaft is
driving the ESVT-pumps, and
the pump which is repressruating the pressure storage vessel 890. The shown
toothed belt may be
exchanged by gear wheels.
There is a water pump for circulation of the cooling water from the air cooled
radiator , and to another
radiator, which may warm up air from the surroundings for warming up e.g. the
cabin of a car. Said water
CA 02786315 2012-08-24
pump is communicating with the main axle 852 of said motor, as well as the
alternator 850, which is
recharging the battery 832.
Fig. 11P left shows
Fig. 11P right shows
Fig. IIQ is showing a one cylinder motor, based on the above mentioned
concepts,
using a camshaft for driving the ESVT pump.
Fig. 1 1R is showing an overview of a two cylinder motor, while particulars
are shown in the
scaled up Figs. 11R left and 11R right.
Fig. I1R is showing a two cylinder motor, based on the concept shown in Fig.
I1Q, where cash
cylinder has an enclosed space, and each an ESVT-pump controlling its volume,
which both are driven by
the same camshaft.'the whole concept is know from earlier drawings.
Fig. 11Q left shows
Fig. 11Q right shows
CA 02786315 2012-08-24
Figs. 1IS-W (met.) show specifics of several construction elements, which has
been used in the
Figs. I1A-R (inci.).
Fig. 11S shows a detail of the joint of the pump 1061 of the piston-chamber
combination
according to Figs. III - 11R with the main axle 852 of the motor, using the
ESV Technology. The base
1140 of the pump 1061 is comprising two base parts 1141 and 1142, which have
been bolted together by
two bolts 1143 and washer 1144, around the main axle with an appropriate tine
fit. Said base part 1 141 is
bolted on the motor housing 1145, which has a bearing 1146 around the main
axle 852, which is taming
around. Said motor housing is shown as a hatch 1147. The base parts 1141 and
1142 have an 0-ring 1148,
which is sealing the sliding connection between the main axle 852 and the base
parts 1141 and 1142. The
pump chamber 1149 is communicating with the 3`d enclosed space 1150. The bolt
1151 and the washer
1152.
Fig. 1IT shows a detail of the joint of the connecting rod 805' of the
actuator piston 806 and the
crankshaft 801'on the main axle 852 of the motor according to Figs. 11G -
1118, using a contineous
communication between the enclosed space 813 of the actuator piston 806 and
the channel 1050 of the
crankshaft 801', due to the use of the ESV Technology.
The assembly of the connecting rod 805' and the U-bend axle 801' of Figs. 1 IG
- 1IR is shown,
on a certain point of time. The connecting rod 805' and the U-bend axle 801'
are turning over each other.
The U-bend axle 801' on which the connecting rod 805' has been assembled with
a bearing 1100, 1100'
and 1100", and the O-rings 1104 and 1104"' between the connecting rod 805' and
the axle 801'. The
enclosed space 813 is communicating with the channel 1050, through the holes
1106, 1107 and 1108.
CA 02786315 2012-08-24
21.0
There are a few holes, on a certain distance from each other, on different
circular places on the
circumference of said axle 801', in order to avoid stress in the axle 801'.
The channel 1050 is constantly
communicating with the holes 1106, 1106 and 1107 through the open space 1105
and 1105'.with the
enclosed space 813. It results in a constant communication between the channel
1050 and the enclosed
space 813 of the actuator piston 806. The base 926' of the connecting rod 805'
is comprising two parts 927
and 928, where the centre axis 929 of the channel 1050 is lying in the
separation surface (not shown) of
said base 926. Two bolts 830 and rings 831 on each side of the piston rod 805
are holding the two parts
927 and 928 together.
Fig. 1IU shows a detail of the joint of the pump 1060 of the piston-chamber
combination
according to Figs. 11I - 11R with the main axle 852 of the motor, using the
ESV Technology. The base
1180 of the pump 1060 is comprising two base parts 1181 and 1182, which have
been bolted together by
two bolts 1183 and washer 1184, around the main axle with an appropriate fine
fit. Said base part 1181 is
bolted on the motor housing 1185, which has a bearing 1186 around the main
axle 852, which is turning
around. Said motor housing is shown as a hatch 1187. The base parts 1181 and
1182 have an O-ring 1188,
which is sealing the sliding connection between the main axle 852 and the base
parts 1181 and 1182. 'the
pump chamber 1189 is communicating with the 2nd enclosed space 1190. The bolt
1191 and the washer
1192.
Fig. 11V shows the mechanismen driving a pump of Figs. I IA - I1R, and its
base.
The pump 1200 is comprising a chamber 1201, a wall 1206, a base 1202, and a
top 1203 of the
chamber 1201. The piston 1204 is of a type described in section 19640 of this
patent application, as well as
the pressure measuring sensor 1205 at the end of the piston rod 1214. The
bearing 1207 in the top 1203 of
the pump 1200 is preferably made according section 19597 of this patent
application - it means that the
bearing 1207 can withstand big side forces from the piston rod 1214. The base
1202 of the pump 1200 can
rotate around an axle 1208, within the boundaries 1222 of another base 1209,
which is part of the motor
housing 1210 - shown as a hatch 1211. On said base 1202, at the opposite side
of said axle 1208 than said
chamber 1201 of said pump 1200, is a contra weight 1212 assembled, so as to
balance the pump 1200 in
the centre point 1213 of said axle 1208. The pump 1200 is comprising a piston
rod 1214, which is guided
by said bearing 1207 in the top 1203 of said pump 1200. At one end of said
piston rod 1214 is piston 1204
L~-1
CA 02786315 2012-08-24
assembled, while at the other end of said piston rod 1214 is an axle 1216
assembled. Said axle 1216 is
positioned perpendicular to the piston rod 1214, and said piston rod 1214 is
mounted on said axle 1216.
The disk 1217 is comprising a bearing 1218, in which said axle 1216 can
rotate, and which is a-centrically
positioned on said disk 1217, preferably near the side 1219 of said disk 1217.
Said disk 1217 is rotating
around a disk axle 1220, which is communicating with an electric motor 1221.
The rotation of said axle
1220 is rotating the disk 1217, by that the axle 1216 is a-centrically
rotating in a plane perpendiclar to said
disk 1217, around said axle 1220. This means that the piston rod 1214 is in a
translational motion to and
from the top 1203 of the pump 1200, while the piston rod 1214 is rotating the
chamber 1201 of the pump
1200 from one boundary 1222 to the other and vice versa, within the angles s
and t in relation to the centre
axis 1223 of said pump 1200. This makes the piston 1204 move in the chamber
1201. The inlet 1224 (not
shown) and the outlet 1225 (not shown) of said pump 1200 are part of the base
1202 of said pump 1200,
by using said type of piston 1215, and said inlet 1224 and said outlet 1225
may comprise a check valve.
The medium 1226 of said pump 1200. The position of the inlet 1224 and outlet
1225 may be different
from said positions, when another type of piston is used.
Fig. 11 W shows the connecting joint between the two crankshafts of the 2-
cylinder motor
according to Figs. I IJ, I IL, I IN, I11', 11R. The shown connecting joint is
an improved version of the
version shown in the drawings Figs. 11J, IIL, IIN, IIP, I1R. In this drawing
is the version of this
connectiong joint shown, where the adjacent enclosed spaces are communicating
with each other. The
crankshaft 1250 of the cylinder left (not shown) is comprising a channel 1251.
which is funetiormmg as
(2u ) enclosed space. It is assembled such that the end 1253 of the crankshaft
1251 is faced to the end
1254 of the crankshaft 1252 of the cylinder right (not shown), wherein between
said ends 1253 and 1254 a
gasket 1255 is positioned ("embedded") under compression in 3 directions, wh
ithin the flanges 1256 and
1257, resp. of both crankshaft ends 1253 and 1254, resp. The last mentioned
crankshaft 1252 is
comprising a channel 1253, which is functioning as (3` ) enclosed space, and
is communicating with the
cylinder right (not shown). Each flanges 1256 and 1257 have preferably an
uneven number of holes,
shown is hole 1258. In said hole is a thin flexible cylinder 1259 mounted with
a tight fit with said hole
1258. In said cylinder 1259 is the bolt 1260 positioned with a pass fit. This
thin fexible cylinder 1259
enables a very small difference in angle position of the two assembled
crankshafts 1250 and 1252, which
2~)
CA 02786315 2012-08-24
assembled, while at the other end of said piston rod 1214 is an axle 1216
assembled. Said axle 1216 is
positioned perpendicular to the piston rod 1214, and said piston rod 1214 is
mounted on said axle 1216.
The disk 1217 is comprising a bearing 1218, in which said axle 1216 can
rotate, and which is a-centrically
positioned on said disk 1217, preferably near the side 1219 of said disk 1217.
Said disk 1217 is rotating
around a disk axle 1220, which is communicating with an electric motor 1221.
The rotation of said axle
1220 is rotating the disk 1217, by that the axle 1216 is acentrically rotating
in a plane perpendiclar to said
disk 1217, around said axle 1220. This means that the piston rod 1214 is in a
translational motion to and
from the rap 1203 of the pump 1200, while the piston rod 1214 is rotating the
chamber 1201 of the pump
1200 from one boundary 1222 to the other and vice versa, within the angles s
and tin relation to the centre
axis 1223 of said pump 1200. This makes the piston 1204 move in the chamber
1201. The inlet 1224 (not
shown) and the outlet 1225 (not shown) of said pump 1200 are part of the base
1202 of said pump 1200,
by using said type of piston 1215, and said inlet 1224 and said outlet 1225
may comprise a check valve.
The medium 1226 of said pump 1200. The position of the inlet 1224 and outlet
1225 may be different
from said positions, when another type of piston is used.
Fig. 11 W shows the connecting joint between the two crankshafts of the 2-
cylinder motor
according to Figs. I IJ, I IL, I IN, 1 IF, 11R. The shown connecting joint is
an improved version of the
version shown in the drawings Figs. IIJ, 1IL, 11N, 11P, 11R. In this drawing
is the version of this
connectiong joint shown, where the adjacent enclosed spaces are communicating
with each other. The
crankshaft 1250 of the cylinder left (not shown) is comprising a channel 1251,
which is functionning as
(2" ) enclosed space. It is assembled such that the end 1253 of the
crankshaft 1251 is faced to the end
1254 of the crankshaft 1252 of the cylinder right (not shown), wherein between
said ends 1253 and 1254 a
gasket 1255 is positioned ("embedded") under compression in 3 directions, whit
in the flanges 1256 and
1257, resp. of both crankshaft ends 1253 and 1254, resp. The last mentioned
crankshaft 1252 is
comprising a channel 1253, which is fanctionning as (3r ) enclosed space, and
is communicating with the
cylinder right (not shown). Each flanges 1256 and 1257 have preferably an
uneven number of holes,
shown is hole 1258. In said hole is a thin flexible cylinder 1259 mounted with
a tight fit with said hole
1258. In said cylinder 1259 is the bolt 1260 positioned with a pass fit. This
thin fexible cylinder 1259
enables a very small difference in angle position of the two assembled
crankshafts 1250 and 1252, which
T~ 7-
CA 02786315 2012-08-24
may arise from dis-synchronisation, due to asynchrone motion of the actuator
pistons (not shown). The
washer 1261 and the not 1262.
Fig. 11 W' shows an improved (in relation to said gasket 1255) sealing of
gasket 1263. The flange
1256 has a cavity 1264, while the flange 1257 has a hump 1265 (not shown),
fitting in the cavity 1264.
An alternative for the tightening, while the connection is flexible., is
shown, where the flange 1257 is flad.
Fig. 1IX shows the same as Fig. I1 W, with the exception that the
communication between the
channels is not possible, because a tightening rod 1270 has been positioned in
the channels 1271 and 1272,
of which the commcn parts 1273 and 1274, resp. of each have a larger diameter,
in order to obtain a
t6 shoulder 1275 and 1276. The thighmess of said thightening rod 1270 in one
of the channels 1273 or 1274
has been obtained by e.g. an appropriate fit and soldering in one of the ends.
The improved sealing of the
gasket 1263 -this construction is identical with the one shown in Fig. 11 W'.
Instead of toothed belts at the power side of the motor according to the
Figs.11D-W, there where the
pump(s) are being driven, may very well be exchanged by gear.
25
35
CA 02786315 2012-08-24
Fig. 12A shows the configuration 800 of the motor according to Fig. 113, where
the piston-
chamber combination was communicating through a crankshaft with the main axle,
and in this figure has
been replaced by a configuration 800', which is comprising a fixed chamber
wherein a piston is rotating
clockwise according to Fig. 10A or Fig. 12B, and, where the suspension of said
piston is shown in Fig.
12C. A 'black box' is shown which is for the entry communicating with a
reduction valve 840 through
channel L.... 1, ........and for the exit communicating with the pump 818
through channel [817]. The
reduction valve 840 is being controlled by a speeder 841.
Fig. 12B shows the motor where the piston of an actuator piston-chamber
combination is moving,
while the chamber is not moving. The motor comprising a chamber 960, which is
comprising 4 sub-
chambers 961, 962, 963 and 964, respectively, which lie around the same centre
axis 965 in continuation
of each other, which has an axle 966 through the center 967 of said chamber
960. Within said sub-
chambers 961, 962, 963 and 964, respectively is 1 piston 968 positioned, shown
on two important
positions, namely position 968' when at a 1n rotational position of the sub-
chamber 964, having the largest
diameter, and position 968" when at a 2" rotational position of the sub-
chamber 961, which is lying in
continuation with sub-chamber 964, so that the I n rotational position of sub-
chamber 964 lies closest to the
2" rotational position of sub-chamber 961, where it has its smallest diameter.
Said actuator piston 968 is
rotating clockwise around said axle 966 -there are shown 4 boles 967 for
assembling said chamber 960 on
axle 966.
Fig. l2C (consumption) shows the A-A section of Fig. 12B, with the non-movable
chamber 960,
and movable the piston 968' and 968". The enclosed space 1070 of said piston
968', 968" (the same
piston in two different sizes) is ending at the axle 966, when it is sealed
with two O-rings 1071, positioned
on each side of said enclosed space 1070. The enclosed space 1070 is
communicating with a second
enclosed space 1072 in the axle 966, where it ends in a housing 1073, where a
T-valve 1074' is present,
which is controlling the entry of fluid 822 from the pressure storage vessel
814 through channel [829] and
reduction valve 840. Said fluid 822 is controlling the presssure inside the
piston 968' and 968". The exit
from said pistons 968' and 968" is through channel [817] to the cascade of
pumps (translational of
rotational).
The electrical signal 1076 is communicating with an electrical/elertronical
control unit 1077, which is
controling the T-valve 1074' within the housing 1073 through signal [1078].
The rotation of the axle 966
is thereby controlling said T-valve 1074', and than the pressure in the piston
968',968". The signal [891]
from the pressure source 1075 to the control unit 1077. The flange 1079 is
connecting the chamber 960 to
1 2~y
CA 02786315 2012-08-24
the suspension 1080, which is mounted on the axle 966. The belt 1081. A pump
as e.g.references 821'
and/or 826' of Fig. 13B may be present, but has not yet been showing in this
drawing - said pump is
communicating with pressure source 1075. Said pump may be communicating with
axle 966. It may also
be communicating with a flywheel and/or a regenerative breaking system 1082.
Fig. 12D (enclosed space) shows the A-A section of Fig. 12B, with the non-
movable chamber
960, and movable the piston 968' and 968". The enclosed space 1070 of said
piston 968', 968" is ending
at the axle 966, where it is sealed with two O-rings. The enclosed space 1070
is communicating with a
second enclosed space 1072 in the axle 966, where it ends in a housing 1073,
where a piston-chamber
combination 1074 is present, which is controlling the pressure inside the
piston 968' and 968"
(the same piston in two different sizes). Said piston-chamber combination may
be in connectrion with the
fluid 889 of the power source 1075, through channel 890.
The electrical signal [1076] is communicating with an electeical/eleetronical
control unit 1077, which is
controling the piston-chamber combination 1074 within the housing 1073 through
signal [1078]. The
rotation of the axle 966 is thereby controlling said piston-chamber
combination 1074, and thus the pressure
in the piston 968',968". The signal [891] from the pressure source 1075 to the
control unit 1077. A return
channel 1050 with fluid with decreased pressure (to said fluid 889) is
returning to the power source 1075,
through a cascade repressuration system (translational and/or rotational
pumps) (see Fig. 12A). The
1151.
The flange 1079 is connecting the chamber 960 to the suspension 1080, which is
mounted on the axle 966.
The belt 1081. A pump as e.g.references 821' and/or 826' of Fig. 13B may be
present, but has not yet been
showing in this drawing - said pump is communicating with pressure source
1075. Said pump may be
communicating with axle 966. It may also be communicating with a flywheel
and/or a regenerative
breaking system 1082.
The motor according to Figs. 12A and 12B may comprise a chamber 960 of which,
at least a part, may be
parallel to the centre axis of said chamber (not shown).
Fig. 13A shows the motor as shown in Fig. I1A, where the crankshaft
arrangement 800 has been
exchanged by the rotational motor of Fig. 105.
Fig. 13B shows the motor of Fig. 13A, wherein the piston pumps 818 and 826
have been
exchanged by rotational pumps, e.g. centrifugal pumps: 821' and 826'.
CA 02786315 2012-08-24
Fig. 13C shows the B-B cross-section of Fig. 13B, and the motor is of a type
where the chamber
of an actuator piston-chamber combination is moving, and the piston is not
moving.
The motor comprising a chamber 860, which is comprising 4 sub-chambers 861,
862, 863 and 864,
respectively, which lie around the same centre axis 865 in continuation of
each other, which has an axle
866 through the center 867 of said chamber 860. Within said sub-chambers 861,
862, 863 and 864,
respectively are 5 pistons 868, 869, 870, 871 and 872, respectively
positioned, each at a different rotational
position said sub-chambers 861, 862, 863 and 864, on an angle a = 72 from
each other. Each piston
comprising a piston rod 873, 874, 875, 876 and 877, respectively. The pistons
868, 869, 870, 871 and 872
are of a "sphere-sphere" type, and are shown all having different diameters.
Said chamber 860 is rotating
anti-clockwise around said axle 866 and the sub-chambers 861, 862, 863 and 864
having a second
rotational position and a first rotational position in the clockwise
rotational direction - there are shown 4
holes 878 for assembling said chamber 860 on axle 866.
Fig. 13D shows the A-A cross-section of Fig. 13C. The chamber 860 having an
incision 879
around the flange 861 of said chamber 860, where a belt 883 can be mounted.
The chamber 860 has been
assembled on said axle 866 which has a flange 880 by a recession. Said piston
rods 873, 874, 875, 876 and
877 are assembled inside a housing 882.
Fig. 13E shows cross-section C-C of Fig. 13A, and another cross-section of
said housing 882 in
view A-A. The piston rods 872, 873, 874, 875, 876 are being connected to a
pressure distribution center
884, where each piston is connected to a computer 885 steered reduction valve
system 886, that is giving
each of the piston rods the necessary pressure - a signal 887 giving the
rotational position of said axle 866
to the computer 885 determines by signal 888 the pressures for each of the
pistons. The pressure to said
piston rods 872, 873, 874, 875, 876 comes through a channel 890 from a
pressure
vessel 889, and is controlled by a signal 891 to the computer 885. Both the
fluctual pressure change in the
enclosed space of each piston is being dealt with separately, but also is the
adjustment electronically dealt
with for each piston by the same computer 885. A pump (as e.g.references 821'
and/or 826' of Fig. 13B
may be present, but has not yet been showing in this drawing - said pump is
communicating with pressure
source 1075. Said pump may be communicating with axle 966. It may also he
communicating with a
flywheel and/or a regenerative breaking system.
Fig. 13F shows schematically an alternative solution for the motor
repressurization system, which
is now alike that of Fig. I IF. Each enclosed space (e.g.t090) of each pistons
is communicating with a
piston-chamber combination 873, 872,874,876,875, while 873 is comprising an
actuator piston 1091 of
jA q6
CA 02786315 2012-08-24
which its position in the chamber 1092 is controlled by the position of a
cartwheel 1093, which can turn
over a cam 1094, while the cam 1093 is assembled on axle 866. NB: the cam and
wheel are shown
schematically, as each wheel should have a different distance to its related
piston, while the wheel should
be shown (partly) sideways. The pressure inside the enclosed space 1090 can be
adjusted by another piston
chamber combination 1055', which is an analogus of 1055 from Fig. 1 IF, and
another controlling actuator
1056' (as 1056) and reduction valves 1057' and 1058' (as 1057, 1058), while
addilonally the speeder
841' (as 841). The pressure vessel 889 ic commincation [1095] with said
reduction valves 1057' and
1058'. A pump (as e.g.references 821' and/or 826' of Fig. 13B may be present,
but has not yet been
showing in this drawing - said pump is communicating with pressure source
1075. Said pump may be
communicating with axle 966. It may also be communicating with a flywheel
and/or a regenerative
breaking system.
The motor according to Figs. 13A, 13B and 13C may comprise a chamber 860 of
which, at least a part,
may be parallel to the centre axis of said chamber (not shown).
CA 02786315 2012-08-24
2T3
Fig. 14A shows the change in pressure and size of the actuator piston 1700
positioned
in a chamber 1701, having a centre axis 1702, and a piston 1703, mounted on a
piston rod 1704
when moving from a 2nd longitudinal /2"d circular position 1705 to a 1"
longitudinal / 1" circular
position 1706. The actuator piston 1700 has been pressurized to e.g. 3% Bar at
said 2"d longitudinal
/ 2"d circular position 1705. Said piston 1700 is comprising an enclosed space
1707, which is
comprising a pump part 1708. The pump part 1708 of said enclosed space 1707
separated from the
rest of said enclosed space 1707 by said piston 1703, when the actuator piston
1700 has been
pressurized to the above mentioned 31', Bar at a second a 2" longitudinal /
2"d circular position
1705 until depressurized to e.g. '/z Bar when moving from said I' longitudinal
/ 1" circular position
1706 - the actuator piston 1709 at said 1" longitudinal / 1" circular position
has now a much
bigger diameter that said piston at said 2"d longitudinal / 2" circular
position 1705. In order to
deflate said actuator piston 1705 to atmospheric pressure - position 1713,
where in case of a
crankshaft the return takes place toward a 2"d longitudinal postion - the %
Bar overpressure is being
released in said enclosed space 1707 by retracting said piston 1703 away from
the actuator piston
1709: movement 1710. Said actuator piston 1711 is increasing in diameter to
its production size,
which is slightly smatter than the diameter of said actuator piston 1700,
which had been pressurized
to 3'h Bar at said 2"d longitudinal positoion 1705, within the wall of the
chamber (not shown in this
figure). Said piston 1703 is being retracted further away - movement 1712 -
from said actuator
piston 1711, so that a pump stroke 1716 toward said 2d longitudinal postion
1714 can take place,
pressurizing said actuator piston to 3% Bar, when, in case of a crankshaft,
the actuator piston has
returned toward (1715) a first longitudinal position.
Fig. 14B shows schematically the process of Fig. 14A in time, and this process
is
shown in a sub-chamber 1720 positioned around a circleround centre axis 1721,
which has been
stretched out as a straight line, which is additionally the time line. Said
sub-chamber 1720 is
normally moving in the direction of the arrow 1740, while said actuator piston
1722 is non-moving.
However, in this drawing is the sub-chamber non-moving while the piston 1720
is moving. Th
piston 1722 is positioned at a 2"d longitudinal / circular position and the
fluid 1723 inside said
actuator piston has been pressurized to e.g. 314 Bar. The pump 1724 is
comprising a piston 1725, a
piston rod 1726, a chamber 1727 and a cam wheel 1728. Said cam wheel 1728 is
resting on a cam
surface 1729. Said piston 1725 is positioned at a 2"d longitudinal piston
(1730) of said pump 1724.
The position of said piston 1725 remains unchanged when the actuator piston
1722 is moving from
a 2"d longitudinal / circular position to a I" longitudinal / circular
position in said sub-chamber
2~g
CA 02786315 2012-08-24
1720, where the fluid 1723 is reducing its pressure to % Bar - actuator piston
1732. The cam wheel
surface 1728 remains at its position, as the cam surface 1729 remains its
height. Retracting the
piston 1725 from position (1730) to position (1731) gives the actuator piston
1733 an internal
pressure of 0 Bar (overpressure), and reduces its diameter to its production
size. This is a result of
the cam surface 1729 being sloped cam surface 1734 with a angle or in relation
to the cam surface
1729, so that the cam wheel 1728 is becoming further away from said actuator
piston 1733: cam
wheel 1738. Directly thereafter returns the translation of cam wheel 1738 at
end point 1735, and
returns to said actuator piston 1733, which has been turning further to
actuator piston 1736. When
the cam wheel 1738 has come back to the original surface 1729, over the sloped
cam surface 1739,
which has an angle p (>90 ) with said cam surface 1729. The actuator piston
1737 belongs to said
position of said cam wheel 1728. It has to be emphasized that the reduction of
size of the diameter
of the actuator piston may be done gradually during a very small period of
time. so that the actuate
piston remaims a contact with the wall 1740 of said chamber 1720.
Fig. 14C shows the configuration of Fig. 14B which enables an injection of
fluid into
the actuator piston, when it is at a 2 a circular position. The cam wheel 1740
is now turning over a
hose 1741, of which the chamber 1744 is comprising a wall 1742, and a fluid or
a mixture of fluids
1743. Said hose 1741 has an exit 1745 to the enclosed space 1746 of the
actuator piston 1747 which
temporary closed, and only opened to said enclosed space 1746 of said actuator
piston 1747, when
the actuator piston 1747 is at a 2 a position (Fig. 14B ref. no. 1737) where
it may be repressurized
from the fluid in the hose 1741.
The description of Fig. 14D1 is showing classic (straight cylinder) pumps,
which are
communicating with the enclosed space of said actuator pistons, running in the
same circular
chamber. The chamber 1749, with a centre axis 1750 in a wheel 1751 - which is
turning anti-
clockwise around an axle 1752, which is mounted with roll bearings 1753. Said
chamber is
comprising 4 identical sub-chambers 1754, 1755, 1756 and 1757. Said channel
1750 is comprising
5 fixed identical pistons 1758, 1759, 1760, 1761 and 1762, each at a different
circular position to
each other, thus having different diameters and internal pressures. Each
piston has a pump part
1763, 1764, 1765, 1766 and 1767, which is fixed in the centre of each of said
pistons 1758, 1759,
1760, 1761 and 1762. Each of said pumps has a piston rod 1768, 1769, 1770,
1771 and 1772, which
is comprising a cam wheel 1773, 1774, 1775, 1776 and 1777, running over a cam
shaft 1778. This
cam shaft 1778 is comprising 4x identical lowered portions 1779, 1780, 1781,
and 1782, there
where a piston 1758, 1759, 1760, 1761 and 1762 need to be repressurized, and
just before a piston
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CA 02786315 2012-08-24
need to be pressurized again. The actuator piston 1761 shows the use of the
lowered portion for said
pump to dashed 1761'. The arrow 1783 shows the direction wherein said chamber
1749 is turning
around said axle 1752.
Fig. 14D2 is identical with Fig. 14D1, with the exception that the pump parts
(comprising
straight cylinders) 1763, 1764, 1765, 1766 and 1767 have been exchanged by
pumps parts
(comprising elongate conical cylinders) 1786, 1787, 1788, 1789 and 1789. The
2n longitudinal
position of said pumps parts 1786, 1787, 1788, 1789 and 1790 are positioned
closest to the actuator
pistons 1791, 1792, 1793, 1794 and 1795.
Fig. 14E shows the section A-A of the motor according to Fig. 14D2 of this
invention,
comprising a circular chamber, mounted directly on a wheel of a vehicle. A
section of a rim 1900, with
a centre axis 1901, and its suspension on a brake disk 1902, having a centre
axis 1903 and a brake pad
1904, which is mounted by bolts 1905 on a chamber housing 1905, in which a
circular chamber 1906
is present, having a centre axis 1907, said chamber 1906 is shown in a section
where a sphere type
piston 1908 is in a first circular position according to the configuration of
Fig 14D2. The inside of said
piston 1908 is communicating with an enclosed space 1909, which is mounted in
a housing 1910,
which itself is mounted by bolts 1922 on apart 1911 of a vehicle frame 1912
(not shown). The size of
said enclosed space 1909 is regulated by a pump 1913 with a conical chamber
1914, of which end of
its conical chamber 1914 and is running by rollers 1915 over a cam profile
1916. Said cam profile
1916 is driven by an auxilliarly electric motor 1917 which is turning said cam
1916, and turning
independantly of said motor (comprising said circular chamber 1906 and said
sphere piston 1908) by
roller bearings 1924 around said main motor axle 1918. Shown are roller
bearings 1919 for the
chamber 1906 suspension on said main motor axle 1918, and a ball bearing 1920
for the cam profile
1916 on said main motor axle 1918. The main motor axle 1918 is mounted by
bolts 1923 on said
vehicle frame 1912 (not shown) as well. A pressure controller 1925 according
to the configuration of
Fig. 16 ("drive by wire"), which is communicating with a remotely positioned
speeder 1927 (not
shown). The pump 1928 of said pressure controller 1925 is communicating with a
channel 1926 which
is comprising the enclosed space 1909 of said actuator piston 1908. The
electric motor 1917 is shown
scemutically as e.g. rotor 1928 which is fastened on the outside motor wall
1929, which is comprising
said can 1926. The anker 1930 is fastened in said mobs motor axle 1918, such
that said anker 1930 is
within said rotor 1928. 'the chamber housing 1905 is fastened to the main
motor axle 1918 by nut
1931, and washer 1932. The extended axle end 1933 of said roller 1915 of said
pump 1913 is guided
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CA 02786315 2012-08-24
in a groove, which is parallel with the centre axis 1934 of said pump 1913,
such that a translational
movement of the chamber 1914 of said pump 1913 is generated.
Fig. 14F is showing a scaled up detail of said circular chamber 1916 the
section shown
in Fig.14E, when at a 10 circular position, with a centre axis 1907 and
chamber housing 1905,
bolted together by bolt 1955. The sphere piston 1908 is shown in section. The
wall 1939 of said
sphere piston 1908 is comprising a reinforcement (not shown) according to
Figs. 208E,F or Figs.
209A-C, and is at the end 1940, positioned opposite to the end 1941 closest to
said pump 1913,
mounted (e.g.vulcanized) on a closed end 1943 of a piston rod 1942. Said
piston rod 1942 has a
channel 1944, which is communicating through hole 1945 with the cavity 1946 of
said sphere
piston 1908. At the other end 1941 of the wail 1939 of said sphere piston
1908, is said channel 1944
communicating with the conical chamber 1914 of said pump 1913, and with said
channel 1926 of
the pressure controller (1925) (not shown). Said end 1941 is comprising a
movable cab 1947, which
is sealed on said piston rod 1942 by an 0-ring 1948. The sphere piston 1908 is
mounted (e.g.
vulcanized) on said movable cab 1947, and this movable cab 1047 can slide over
said piston rod
1942. For making it easier this drawing to comprehend, the wall 1941 of the
piston 1908 is not
drawn through the section wherein the contact between the wall 1941 of said
piston 1908 and the
wall 1948 of said circular chamber 1916 is taking place. The centre axis 1949
of the channel 1944
of said piston rod 1942. The entre axis 1934 of the chamber 1914 of said pump
1913. Said piston
and 1942 can translate within the cylinder 1950, and is sealed by two 0-rings
1951 and 1952,
respectively. The distance as between the centre axis 1953 of said hole 1945
and said centre axis
1907 of said circular chamber 1916. The distance cc between the end 1954 of
the movable cab 1947
and said centre axis 1907.
When a vehicle is comprising more than one wheel, it may be necessary to
synchronize the motion
of each wheel with the motion of each other wheel, if said wheels are rolling
over the some surface.
This may preferably be done by a computer, which is co-ordinating the pressure
in each actuator
piston in each sub-chamber per wheel, with that of each other wheel. This is
shown by reference
1960, which is communicating with a computer (not shown) (1961).
Fig. 14G shows the same as Fig. 14H, with the exception that said actuator
piston 1908 is
shown in a 2"a circular postition of said chamber 1916. Said movable cab 1947
has been sliding over
said piston rod 1942 towards said closed end 1940, while additionally said
piston rod 1942 has been
sliding in said cylinder 1950, towards the pressure controller (not shown)
(1925). Said hole 1945 is
now positioned between said closed end 1940 and said movable cab 1947. Said
distance as (Fig. 14F)
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CA 02786315 2012-08-24
has been reduced to distance bb, while said distance cc (Fig. 14F) has been
reduced to distance dd.
Said slidings make it possible to adapt the position of said actuator piston
1908 to be in the center of
the cross-section of said chamber 1916, at all circular positions of said
actuator piston 1908
Fig. 14H shows the configuration of Fig. 14E, wherein between the rim 1900 of
the
wheel and the brake plate 1902, and said circular chamber housing 1916 has
been built-on gearbox
1956, e.g. of the type of a planet gear.
Besides the computerized controlling of the pressure of each actuator piston,
as described in Fig, 14E,
it may be necessary to synchronize the change of gear of said gearboxes 1956,
for each one wheel. This
may preferrably done again by a computer, e.g. the computer 1961, which is
already controlling the
pressure in each actuator piston (Fig. 14E).
20
30
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CA 02786315 2012-08-24
Figs. 15A-E show several auxilliarly power sources working together with the
motor.
The shown electric power lines have been carefully chosen.
Fig. 15A shows a H2-fuel cell which deliveres electricity to a motor, which is
driving
a ESVT-pump. Today (February 2011) is this solution very costly, but just on
the web site of the
Carbon Trust was a message, that there was a technical breakthrough, which
made it possible to use
in the future a H2-fuel cell in a car motor. The other difficulty is, that the
storage of H2 is a difficult,
and energy unfriendly.
Fig. 15B shows a solution which is a solution for the H2 storage problem,
because H2
is stored as H2O, and is coming free through electrolyses. Because the
feasibility study showed that
less than 10% of the current energy is necessary for driving e.g. a our, is
this way of generating and
using H2 in a combustible motor, which may resulting in rotation. An
alternator is generating
electricity, which is driving an electric motor for driving an ESVT-pump. The
problem here is that
the last mentioned process has an efficiency of only 25%.
The 02 which comes free at the electrrolyses of conductive H2O, may be used in
the combustible
motor, so that the burning of He is still more efficient (turbo-effect). The
1120 which comes free
from the bunting process in the combustible motor, may be re-used for deriving
H2 by electrolyses.
Fig. 15C shows a solution where the ESVT pump is directly driven by the axle
of said
combustible motor through a crankshaft, which now may be much smaller because
the process of
powering said pump is 100% efficient.
Fig. 15D shows a comparable solution as Fig. 15C, where the crankshaft has
been
exchanged bu a rotational ESVT-pump, which makes the process still more
efficient. The I12 comes
here from both electrolyses and from the solar voltaic cells.
Fig. 15E shows a solution where a big capacitator is used as the power source
for the
ESVT-pumps. The big advantage is that this capacitator can be charged in a few
minites, and a car
may drive say 500 km, when the capacitator has a size of a suitcase.
Fig. 15A shows schematically a storage tank 1630 for 02 (1631), which may be
pressurized, and which has been filled up through channel 1632, which is
connecting said storage
tank 1630 with the outside (1633) of said motor.. Said storage tank 1630 is
communicating through
a channel [1634] to a Ht-fuel cell 1606. Another storage tank 1600 for H2
(1601), which may be
cooled, and may be pressurized, using electricity through a electric
communication [1602], and
which has been filled up through a channel [1603], which is connecting said
storage tank 1600 with
02-
CA 02786315 2012-08-24
Figs. 15A-E show several auxilliarly power sources working together with the
motor.
The shown electric power lines have been carefully chosen.
Fig. 15A shows a HZ-fuel cell which deliverer electricity to a motor, which is
driving
a ESVT-pump. Today (February 2011) is this solution very costly, but just on
the web site of the
Carbon Trust was a message, that there was a technical breakthrough, which
made it possible to use
in the future a H2-fuel cell in a car motor. The other difficulty is, that the
storage of H2 is a difficult,
and energy unfriendly.
Fig. 15B shows a solution which is a solution for the H2 storage problem,
became H2
is stored as H2O, and is coming free through electrolyses. Because the
feasibility study showed that
less than 10% of the current energy is necessary for driving e.g. a car, is
this way of generating and
using H2 in a combustible motor, which may resulting in rotation. An
alternator is generating
electricity, which is driving an electric motor for driving an ESVT-pump. The
problem here is that
the last mentioned process has an efficiency of only 25%.
The 02 which comes free at the elecytrolyses of conductive H2O, may be used in
the combustible
motor, so that the burning of H2 is still more efficient (turbo-effect). The
H2O which comes free
from the burning process in the combustible motor, may be re-used for deriving
H2 by electrolyses.
Fig. 15C shows a solution where the ESVT pump is directly driven by the axle
of said
combustible motor through a crankshaft, which now may be much smaller because
the process of
powering said pump is 100% efficient.
Fig. 15D shows a comparable solution as Fig. 15C, where the crankshaft has
been
exchanged bu a rotational ESVT-pump, which makes the process still more
efficient. The H2 comes
here from both electrolyses and from the solar voltaic cells.
Fig. 15E shows a solution where a big capacitator is used as the power source
for the
ESVT-pumps. The big advantage is that this capacitator can be charged in a few
miniles, and a car
may drive say 500 km, when the capacitator has a size of a suitcase.
Fig. 15A shows schematically a storage tank 1630 for 02 (1631), which may be
pressurized, and which has been filled up through channel 1632, which is
connecting said storage
tank 1630 with the outside (1633) of said motor. . Said storage tank 1630 is
communicating through
a charuiel [1634] to a Ft2-fuel cell 1606. Another storage tank 1600 for H2
(1601), which may be
cooled, and may be pressurized, using electricity through a electric
communication [1602], and
which has been filled up through a channel [1603], which is connecting said
storage tank 1600 with
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CA 02786315 2012-08-24
the outside (1604) of said motor. Said storage tank 1600 is communicating
through a channel
[1605] to a HZ-fuel cell 1606 wherein Hz and 02 are being transformed into
electricity, which is
charging through electric communication [1607] either start battery 832B
(short term, high current),
or service 832C (longduring, medium current). Said channel [1605] is
comprising a non-return
valve 1608 (not shown). The start battery 832B is electrically communicating
[1609] with the
starter 830 of the motor, while the service battery 832C is electrically
communicating [1610] with a
pump 826 of said motor. Said motor is further comprising a pressure vessel
814, which is
communicating with pump 826 and with piston actuator arrangement 800. The main
axle 852 of
said motor is communicating with alternator 850, which is charging through an
electrically
communication [1611] the service battery 832A (longduring, medium current).
Said battery is
electrically communicating [1602] with the cooling of tank 1600. The batteries
832A-C (incl.) are
referred as one piece in other drawings of this patent application, with
reference number 832, and
have been charged ab works. The photo solar voltaic cell 833, which is
additionally charging
battery 832. The pressure storage vessel 814, which are being charged by a
pump 820/826. The
piston actuator module 800 of the motor.
Fig. 15B shows schematically a tank 1612 for (conductive) H2O (1613),
which has been filled up through a ehamrel [16141, which is connecting said
tank 1612 with the
outside (1604) of said motor. Said tank 1612 is communicating through a
channel [1615] to a vessel
1616 in which electrolyses 1617 of said water (1613) is taking place. The exit
[1622] of said vessel
1616 is communicating with a combustion motor 1620, which is communicating
with its main axle
1621. Said channel [1622] is comprising a non-return valve 1618 (not shown).
Said motor 1620 is
burning the in vessel 1605 generated H2, so that motion occurs - here,
rotation of said axle 1621.
Said axle 1621 is communicating with an electric start motor 1623, and with an
alternator 1624.
Said alternator 1624 is charging battery 832B (for high current, short time)
for said start motor
1623, or battery 832C (medium current, longduring). The battery 832A (medium-
high current,
longduring) is being charged by an alternator 850 through electric
communication 1625, which is
communicating with the main axle 852 of the motor of the motor. Said battery
832A is giving
power through electric communication [1626] for the electrolyses 1617 in
vessel 1616. The battery
832C is giving power through electric communication [1627] to a pump 826 of
the motor, while the
battery 832B gives power to the start motor 1623 and 830, respectively through
electric
communication [1628]. Said batteries (832) have been charged ab works. The
photo solar voltaic
2,8
CA 02786315 2012-08-24
cell 833, which is additionally charging battery 832. The pressure storage
vessel 814, which is being
charged by a pump 820/826. The battery. The piston actuator module 800 of the
motor.
The battery has an output electric communication [1614] to other functions of
the motor in Figs. 11
A,B,C,F,G and Fig.12A and Figs. 13A,B according to function 851 in said
drawings. The bypass
[1616] from the fuel cell 1607 to the output electric communication [1614],
directly giving power to
said functions.
Fig. 15C shows schematically the process according to Fig. 15B, where
additionally a
piston pump 1625 of the repressuration cascade 826 or 831, respectively is
directly communicating
with the main axle 1623 of said combustible motor 1620 through a crankshaft
1624 and piston rod
1626. The photo voltaic solar cell 833 which is charging the battery 832,
besides the alternator 850,
which is communicating with the main axle 1623. The battery 832 is
electrically connected to the
motor through an electric communication [ 1614]. The exit of the pump 1625 of
motor function 826
is communicating with the motor according to Figs. 1IA,B,C,F,G or Figs. 12A,
13A,B. The inlet
1623 of said pump 1625. The start motor 830.
Fig. 15D shows schematically in principle a comparable process of that of Fig.
15C,
where the piston pump 1625 has been exchanged by a rotational pump 1627, which
is
communcating with said motor 1620 by axle 1628. Said rotational pump 1627 is
communicating
with motor functions 800", 820' by channel [825] and with pressure storage
vessel 814 of Fig. 13B
by channel [828]. The start motor 830 is communicating with axle 1628 and gets
its power from
battery 832 through wires [1642] The battery 832 is being charged by photo
solar cells 833' and
alternator 850 through wires [1641], and is communicating with axle 1628. The
battery 832 is
connected to the motor functions 800" and 820 by wires [1629]. The photo solar
cells 833' are
providing directly Hz to to motor 1620 by channel [1640]. This system may
preferably be used
together with the configurations shown in Figs.13F,14B,C,D. The motor type
according to Fig. 14D
may be a specifically preferred embodiment.
Fig. 15E shows schematically a capacitator 1630 for instant storage of
electricity
1631, which has been filled up through an electric wire [1632], which is
connecting said capacitator
1630 with the outside (1603) of said motor. Said capacitator 1630 is
communicating through a
channel [1633] to to other functions of the motor in Figs. 11A,B,C,F,G and
Fig.12A and Figs.
13A,B according to function 851 in said drawings. Said functions are
comprising an axle 852, 866,
28K
CA 02786315 2012-08-24
1621, respectively which is communicating with an alternator 850. Said battery
832 is electrically
connected by wires [1613] with said alternator 850 (not shown in Fig. 15E).
The battery 832 is
additionally charged by a photo voltaic solar cell 833. Additionally is said
capacitator 1630
connected to said battery 832 by wires [1634] for charging purposes.
Fig. 16A shows a scaled up 2-way actuator of the Figs. 11G-R. The 2-way
actuator is
comprising two channels 3300 and 3301, which are communicating from the
outside to the inside of
the cylinder 3302, each communicating with a regulator (reduction valve) 3303,
3304, respectively
l0 which are controlled through valve means 3305 by a speeder 3306 - both
regulators 3303 and 3304
are communicating to each other, so that one speeder 3306 can control both
regulators 3303 and
3304.. There are two overflow channels 3307 and 3308, which communicate to
each of the two
spaces 3309 and 3310 on each side of the internal piston.3311. The O-rings
3312 and 3313,
between said piston 3311 and the wall 3314 of said actuator.
15 Fig. 16B shows a pre-study of the 2-way actuator of Fig. 16A. It is
concluded that a
more quickly reacting system is that the piston is comprising the overflow
channels. Additionally it
is concluded that the regulators need to have each a stop function for its
flow. And, that the
overflow channels need to have each (1) an automatic contra valve function
(e.g. according to Fig.
210E) and (2) a check valve.
25
2- Sb
CA 02786315 2012-08-24
ESTV - ASYNCHRONE CRANKSHAFT DESIGN - COMBINED USE OF COMPONENTS
Fig. 17A shows a complete cycle of an actuator piston in a conical chamber,
using the
ESVT. This is identical with Fig. IOA,C. Even only the ellipsoide-
ellipsoide/sphere type piston is
shown, any type of inflatable actuator piston may be used.
Fig. 17B-H show a multiple cylinder motor, which is based on the 2-cylinder
configuration of Fig. 17B. Fig. 17B is based on the one cylinder configuration
of Fig. 17A, where
said configuration has been used twice, in such a way that simultaneously the
power stroke of one
chamber and the return stroke (which is not powered) of the other chamber are
being performed.
Because the power stroke of an actuator piston is only performed from a 2nd to
a 1" longitudinal
position, said two chambers are pointing in opposite directions. The
consequence is that the
crankshaft configuration is such, that the connecting rods to these actuator
pistons are positioned
180 in relation to each other (`asyynchrone'). The result is that the motor
deliveres power at all
times, and this configuration may be used in a stand alone 2 cylinder motor,
tie in a multiple (>2,
and preferably even number) cylinder motor. A flywheel may be redundant, which
may reduce the
weight of the vehicle.
Both actuator pistons may or may not be communicating with each other through
the
enclosed spaces of said crankshaft (which may be comprising two connected sub-
crankshafts, one
for each actuator piston), each belonging to a different actuator piston. The
communication between
the enclosed spaces may be through the channels in the sub-crankshafts and/or
through a channel
outside said crankshaft.
When said enclosed spaces maybe separated, e.g. at the connection point of
said sub-
crankshafts (together comprising said crankshaft) by e.g. a tightening rod
1270 (Fig. I1X), which
may be posiioned between said enclosed spaces.
In this configuration of the actuator pistons may it very well be possible to
combine
said two ESVT pumps into one pump, as the pressure increase and decrease,
respectively to each of
the actuator pistons, is reversed, at the same point of time, while the total
volume of the enclosed
spaces may be remained. An ESVT-pump is e.g. directly communicating with one
of the enclosed
spaces, while said ESVT-pump is communicating indirectly through an external
channel is
communication with the other enclosed space.
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CA 02786315 2012-08-24
There may be valves functions in both flow directions, to and from each
enclosed
space per actuator piston (e.g. by the use of valve actuators according to
Fig. 210E or Fig. 210F),
which are opening and closing the connection between said ESVT-pump and said
enclosed spaces.
Said valves may be controlled by either the pressure of said ESVT-pump and/or
by tappets, which
may be communicating with a camshaft (which may be communicating with the main
auxilliarly
power line, e.g. an auxilliarly He combustion motor) dr may be communicating
with a computer
(not shown).
The change of inside pressure in the actuator pistons is when said actuator
pistons are
in the t"/2 d longitudinal positions, respectively and in the 2"d/1"
longitudinal positions,
respectively. When the camshaft maybe regulating the opening and closing of
the actuator piston +
check valve assemblies, than said camshaft may have twice the speed of the
axle, where the
crankshaft of the ESVT-pump is communicating with.
The piston-chamber combinations for each of the enclosed spaces in a sub-
crankshaft,
which are changing the speed/pressure in a cylinder may only be used for one
cylinder. These
piston-chamber combinations are communicating with each other through the
electric pressure
regulator of the 2-way actuators, which is moving the piston rod of each of
said piston-chamber
combinations, and than communicating with the external speeder. However, it
may be possible that
one of the two piston chamber combinations may be deleted, and exchanged by
the same
configuration which has been used to cut one of the GS VT-pumps. The many
valves may be making
the configuration vulnerable for miss-function.
Instead of toothed belts at the power side of the motor, there where the
pump(s) are
being driven, may very well be exchanged by gear wheels.
When said second and third enclosed spaces may be communicating with each
other,
e.g. at the connection point of said sub-crankshafts (Fig I1 W, W'), e.g.
through a movable piston
(Fig. 171), which may be mounted in the channel which is comprising said
enclosed spaces. Said
piston is a double functioning type, so that when it is moving, e.g. towards
said second enclosed
space, thereby increasing the pressure in said second enclosed space of one of
the actuator pistons,
it simultaneously is decreasing the pressure in said third enclosed space of
the other actuator piston.
Said double working piston is actually the ESVT-pomp of that configuration of
the motor. It is
additionally possible that said double working piston is positioned outside
said crankshaft.
28
CA 02786315 2012-08-24
A motor, further comprising two cylinders, wherein the 2nd longitudinal
position of one cylinder is
at the same geometrical level of the 1st longitudinal position of a second
cylinder, both actuator
pistons are communicating with each other through a crankshaft, said
crankshaft is comprising two
connected sub-crankshafts, one for each actuator piston, where the connection
rods to these actuator
pistons are positioned 180 from each other.
A motor, further comprsing ESVT pumps for each of the cylinders, wherein said
pumps are
combined for said two cylinders into one pump, through communication of the
enclosed space of
one of the actuator pistons with the enclosed space of the other of the
actuator pistons, said enclosed
spaces being comprised in said crankshaft, said enclosed spaces are
communicating with each other
at the connection point of said sub-crankshafts.
A motor, further comprising valves, which are opening and closing the
connection between said
ESVT-pump and said second or third enclosed spaces, while each connection has
a check valve or
check valve function, said valves are controlled by either the pressure of
said ESVT-pump and/or
by tappets, said tappets are communicating with a camshaft, which is
communicating with the main
axle of an auxiIliarly motor.
A motor, further comprising more than two cylinders, where each added cylinder
is communicating
through the enclosed spaces of the connected sub-crankshafts of the existing
sub-crankshafts.
Add description of preferred embodiments with reference numbers for Figs. 17A-
I (incl.).
In Figs. 17A - 17H (incl.) has a 2-cylinder motor been disclosed, where the
enclosed
spaces of each chamber in each sub-crankshaft have been separated by a
tightening rod 1270.
In Fig. 171 is a 2-cylinder motor been disclosed, where the enclosed spaces of
each
chamber in each sub-crankshaft have been separated by a straight channel in
which a two-way
piston is moving, and which is communicating with each enclosed space.
99
CA 02786315 2012-08-24
ESTV - SYNCHRONE CRANKSHAFT DESIGN - COMBINED USE OF COMPONENTS
Fig. 18A-G (incl.) show multiple cylinder motors, based on a two cylinder
configuration, which is based on the 2-cylinder configuration of Fig. 18A,
which is based on the
one cylinder configuration of Fig. 17A, which refers to Figs. 10A,B. However,
any inflatable
actuator piston type may be used.
In Fig. 18A are two cylinders shown, which have simultaneously combined in
time
the power stroke of each cylinder. Both actuator pistons are communicating
with each other through
a crankshaft (which may be comprising two sub- crankshafts), where the
connection rods to these
actuator pistons are positioned 00 from each other.
This is done by a configuration of two identical piston-chamber combinations,
where
the 2"d longitudinal position of one cylinder is at the some geometrical level
of the 2"a longitudinal
position of the second cylinder. The return stroke is thus not powered, and
such a configuration
may be combined with other configurations (motor comprising > 2 cylinders) in
order to fill the
power gab at the return stroke. Another solution may be the use of a flywheel.
The ESVT pumps may be combined to one pump for said two cylinders into one
pump, through connecting the enclosed spaces of the actuator pistons, e.g. at
the connection point of
the sub-crankshafts.
If another group of actuator pistons is added to said motor, and the strokes
of the
added piston-chamber combinations are identical with those of said motor, than
the configuration of
Fig. 18 can be used for the total group - preferably one ESVT-pump may be used
for the whole
group of piston-chamber combinations, as well as one piston-chamber
combination for the
pressure/speed control.
If another group of actuator pistons is added to said motor, and the strokes
of the
added piston-chamber combinations are opposite to those of said motor, than
the configuration of
Fig. 17 can be used for the total group - one ESVT-pump may be used for the
whole group of
piston-chamber combinations in combination with an external channel, and non-
return valves and
valve actuators in both flow directions (please see Figs. 17C-17H (incl.). The
two cranksafts of both
groups of piston-chamber combinations may be communicating with each other,
whereby the
channel inside each crankshafts may preferably be separated, e.g. by a filler
(e.g. a tightening rod
1270 of Fig. 1IX). A power balance may arise in said motor.
CA 02786315 2012-08-24
2/1 O
Instead of toothed belts at the power side of the motor, there where the
pump(s) are
being driven, may very well be exchanged by gear wheels.
A motor further comprising two cylinders, wherein the lot longitudinal
position of one cylinder is at
the same geometrical level of the 1st longitudinal position of a second
cylinder, both actuator
pistons are communicating with each other through a crankshaft, said
crankshaft is comprising two
connected sub-crankshafts, one for each actuator piston, where the connection
rods to these actuator
pistons are positioned 0 from each other.
A motor further comprising ESVT pumps for each of the cylinders, wherein said
pumps are
combined for said two cylinders into one pump, through communication of the
enclosed space of
one of the actuator pistons with the enclosed space of the other of the
actuator pistons, said enclosed
spaces being comprised in said crankshaft, said enclosed spaces are
communicating with each other
at the connection point of said sub-crankshafts.
A motor further comprising valves, which are opening and closing the
connection between said
ESVT-pump and said second or third enclosed spaces, while each connection has
a check valve or
check valve function, said valves are controlled by either the pressure of
said ESVT-pump and/or
by tappets, said tappets are communicating with a camshaft, which is
communicating with the main
axle of m auxilliarly motor.
A motor further comprising more than two cylinders, where the enclosed
space(s) of each added
(couple) cylinder(s) is(are) separated through a filler in the connection with
said existing sub-
crankshafts, and where the power strokes of the added cylinders are
simultaneously the return
strokes of the existing cylinders.
A motor further comprising 2 cylinders wherein the connection rods are in a
position of 180 from
each other, while the chambers have an identical geometrical position of their
151 and 2d
longitudinal positions.
Add description of preferred embodiments with reference numbers for Figs. 18A-
G (incl.)
24 1
CA 02786315 2012-08-24
CT - CRANKSHAFT DESIGN - COMBINED USE OF COMPONENTS
Fig. 19A shows a one cylinder motor, based on Figs. 11B, 11C, where some parts
have been worked out further - the auxilliarly power source is e.g. chosen as
a combustion motor,
which is burning Hz, derived from electrolyses of H20.
Fig. 19B shows a two cylinder motor, based on Fig. 19A, where the two
cylinders have
been mirrowedly positioned to the center line of the connection of the sub-
crankshafts, so that the 30
enclosed spaces (exits) are communicating with each other through the
connection of the two sub-
crankshafts, while the 2nd enclosed spaces (inlets) are communicating
externally with each other
(with a check valve), and where the crankshaft (comprising of two sub-
crankshafts) is designed, so
that the power strokes of each actuator piston are moving in the same (0 )
direction (synchrone),
according to the principle of Fig. i SA.
When more than two cylinders are needed in a motor according this synchrone
principle, more
cylinders may be added, so that e.g. another 2d enclosed space may be
connected to the not yet used
end for a connection to the 2"d enclosed space of the added cylinder, so that
a 3-cylinder motor occurs.
The then still free 3" enclosed space of the added cylinder may be connected
to a 3' enclosed space of
another added cylinder, so that the motor may functions with 4 cylinders. The
now shown closed ends
of the channels of the sub-crankshafts may need than to open up.
Fig. 19B 1. shows an enlargement of Fig. 19B left.
Fig. 19B r. shows an enlargement of Fig. 19B right.
Fig. 19C shows a two cylinder motor, based on Fig. 19A, where the comparable
enclosed spaces (here the 3`d enclosed spaces) have been connected to each
other through the sub-
crankshafts, while the 2"d enclosed spaces have been brought externally
together (with a check valve),
and where the whereby the crankshaft (comprising of two sub-crankshafts) is
designed, so that the
power strokes of each actuator pistons are moving in the same (180 ) direction
(asynchrone), according
to the principle of Fig. i 8A.
Fig. 19C 1. shows an enlargement of Fig. 19C left.
Fig. 19C r. shows an enlargement of Fig. 19C right.
CA 02786315 2012-08-24
Z~j
A motor further comprising two cylinders, wherein the third enclosed space of
each cylinder are
communicating with each other through the connection of the two sub-
crankshafts which are
comprised in the crankshaft of said motor, and the second enclosed spaces of
each cylinder are
communicating with each other outside said crankshaft.
A motor wherein the crankshaft configuration of two piston-chamber
combinations the connector
rods are positioned 180 from each other.
A motor further comprising more than two cylinders, wherein a second enclosed
space is connected
through the connection of said sub-crankshafts of the existing two cylinders,
with the second
enclosed space of the sub-crankshaft of the cylinder to be added.
Instead of toothed belts at the power side of the motor, there where the
pump(s) are being driven,
may very well be exchanged by gear.
CA 02786315 2012-08-24
19620 DESCRIPTION OF PREFERRED EMBODBVVIENTS
Fig. 21A shows a so-called constant maximum force chamber 1, with a wall part
2
of the longitudinal cross-section, at a first longitudinal position of the
piston (not shown),
which is parallel with the centre axis 3. A part 4 of the chamber wall has a
convex formed
wall of the longitudinal cross-section of the chamber 1. A transition 5 of the
longitudinal
cross-section of the outside wall of the chamber. from convex wall parts 4 to
concave wall
parts 7. The wall part 6, which is positioned at a second longitudinal
position of the piston
(not shown), is not parallel to the centre axis 3 of the chamber I. Common
border 9 of a
longitudinal cross-sectional cross-section 10 of the chamber 1 at a
longitudinal position where
1 Bar overpressure has been reached by the piston (not shown), when moving
from a first to a
second longitudinal position. The common borders 11 1 13 1 15 1 17 1 19 1 21 1
23 125 and
27, respectively, between the longitudinal cross-sectional sections 12 1 14 /
16 / 18 / 20 / 22 /
24 / 26.128 / 30 of the chamber I at a longitudinal position where I / 2 / 3 /
4 / 5 / 6 / 7 / 8 /
9 / 10 Bar, overpressure over atmospheric pressure, respectively in e.g. an
advanced bicycle
pump has been reached by the piston (not shown). The internal walls of
longitudinal cross-
sectional sections 28, 29, 30, 31, 32, 33, 34, 35 and 6 are convex shaped,
while the internal
wall of longitudinal cross-sectional section 7 is concave shaped (between 6
and 7 Bar
overpressure) for a 10 Bar (overpressure) pump. Dashed is shown the outside
shape (36-37-
38) of the chamber if slavishly the mathematical equasion had been followed -
this is done for
design purposes, to as to avoid that the chamber is looking rap heavy. This
adaptation as such-
has no influence on the max. working force, because it has been done in the
beginning of the
hyperbolic function (working force no the piston as a result of the shape of
the chamber in a
lomgitudinal direction, measured from a first to a second longitinal piition).
Due to the small
and constant size of the wall thickness over the total length of the chamber
is this also the case
for the external -walls of said longitudinal cross-sections (not numbered):
please see
WO/2008/025391.
The longitidinal positioning of said common borders may be mathematically
determined as a result of the rest volume of the stroke volume of a conical
chamber under the
piston, and its maximum value of the pressure, which is in this figure: 10
Bar. Characteristic
CA 02786315 2012-08-24
zap
J
is that the distances between said common borders which follow each other
counted from a
first longitudinal position of the piston to a second piston positions are
decreasing the higher
the overpressure rate is. That is than also the case for the heights of the
respective walls of
said longitudinal.cross-sections sections 28, 29, 30, 31, 32, 33, 34, 35, 6
and 7. The positions
of the wall at said common borders is based on a chosen value of maximum
working force -
which is in this case 25 kgf. The result is the characteristic shape of the
chamber
(WO/2008/025391).
Fig. 21B shows the shape (coetineous line) of the 10 Bar (overpressure)
chamber of
Fig. 21 and the shape of a 16 Bar (overpressure) chamber (dashed) for the same
length of the
chamber. If the transitional size of the internal diameter of the part 30
would give problems
for the size of the piston, may a recalculation of the sizes of the chamber
may be done, by
enhancing the maximum value of the working force, by an unchanged maximum
value of the
overpressure. This will make the diameter of e.g. reference number 30 bigger.
The wall
thickness is approximately even over the length of the chamber, although at
said concave part
7 the thickness might be a bit bigger than the wall thickness of the rest of
the wall. Another
recalculation may be done, if to maximum overpressure should be bigger than 10
Bar, e.g. 16
Bar. This may be accomplished by chosing a higher maximum work force, so that
the
circumference of a tranversal cross-section may become bigger. This means that
the conical
shaped outer wall of the chamber can go nearer 2 ' longitudinal positions,
before the
circumference reaches its minimum value in order to ensure, that a pistea
would not jamm,
which is defined by the piston type. Near first longitudinal positions would
following
verbatim the calculations, the size of the chamber would become too big, and
that is why, one
may define its shape there, so that the cire mterence becomes smaller - this
may also be the
case for other common borders as well.
A task to optimize the chamber to demands toward bandpumps can be done in
similar ways, as those described above. The problem there to be solved is a
good compromise
between the the minimum size of the circumference of the inner chamber wall
(depending on
what a piston can perform) and the max. circumference of the outside of said
chamber at first
longitudinal positions, which is where a user is holding the handle, and the
designated max.
working force.
Fig. .22A shows a bottom part of a chamber of an advanced bicycle floor pump
where also the bottom part of the chamber 1 of Fig. 21 can be seen: The
chamber 1 is
mounted on a foot 41. A flexible manchet 42 assembles thechamber 1 on the foot
41. The
hose 43, which is connected to the exit 44 of the pressure expansion vessel 49
- this exit is
CA 02786315 2012-08-24
without a check valve- The (schematically drawn) piston 45 is comprising a
piston rod 46. At
the bottom of the piston rod is a check valve 47 positioned, which is
communicating with the
external at tosphere(4&)rand-is._opening-tawards-the-chamberlrso_asl fin thw
uh ,nbe* t
when the piston 45 is moving from a second longitudinal position to a first
longitudinal -
position. An expansion pressure vessel-49 with a chamber 56 is shown,
comprising an inlet
check valve 50, when open, the chamber I is communicating with the hose 43,
through an
exit 44. The cross-section of the external wall 51 of the expansion pressure
vessel 49, with an
internal wall 52 The expansion pressure vessel 49 is assembled between a top
end 53 and a
bottom end 54 of said vessel 49. The top end 53 of the expansion pressure
vessel 49 is sealed
to the wall of the chamber 1 by an O-ring 55, while the top end 53 and the
bottom end 54 are
sealed to the all 52 of the expansive pert sore vessel 49 by gas sealing
dseead 58 and 59
respectively: -
This is a preferred embodiment for very high pressures (e.g. 16 Bar), sod if
the piston has
difficulties in sealing to the internal chamber wall. This construction avoids
the sealing on the
transition from a longitudinal cross-sectional section with a convex wall to a
longitudinal
cross-section section with a concave wall - please see Fig. 1.
Fig. 23 shows another constant force chamber 80 for a maximum pressure of 10
Bar
with the same specification as the chamber of Fig. 1, with the exception that
it has to secure
that a pressurized container type piston has to be non-moving on a second
longitudinal piston
position - the internal wall 81 of the chamber at said second longimdinal
piston positions
should be chosen and shown being parallel to the centre axis of the chamber.
The transition from said convex walls 82 of longitudinal cross-sectional
sections between
common borders 83 and 84, corresponding to 0 Bar and 7 Bar overpressure,
respectively to
said wall 81 parallel to the centre axis 85 of the chamber 80 has a special
internal concave
shape 86, comprising smaller concave shaped subsections 86.1, 86.2 and 86.3
respectively,
between a common border 84, which corresponds to 7 Bar overpressure until the
common
border 88 for 10 Bar overpressure. The shape of the inside wall ofsaid chamber
and its
outside wall may not anymore correspond to each other: between the common
border 84 for
7 Bar overpressure and the common border 88 for 10 Bar overpressure is the
outside wall is
still convex, while the inside wall is concavely shaped. This difference in
shape, makes it
possible to increase the wall thickness in relation to that of the rest of the
wall thickness of the
chamber, there where the chamber has its weakest spot: the transition from
concave internal
wall sections to the inside wall parallel to the centre axis of said chamber.
The external wall
89 of the chamber, which is positioned there where the internal wall of said
chamber is
ler
parallel to the centre axis of said chamber may be-chosen as a straight line,
but not nessesarily
parallel to said centre axis- This may be done for a good looking purpose, as
curved shapes
give some visual tension.
The transition from concave inside walls to said inside wall of said chamber
which is
parallel to the centre axis of the chamber may be made smoothly, in order to
be able to let a _
piston pass this transition, without jamming.
Fig. 24 shows the foot 70 of an advanced floor pump for e.g. tyre inflation.
The
flexible marcher 71 keeps the cone formed chamber 80 of Fig. 3 in place. The
inside wall 81
of chamber 80 is parallel to the centre axis 85 of the chamber 80. The
inflatable piston 73.
The enclosed space 66. The rube 65. The inlet check valve 75. The outlet check
valve 76. The
hose 77. The measuring space 78, 79 (inside the hose). The valve connector 67
(not shown).
The space 68 inside the valve connector 67 is also part of the measuring space
(not shown).
Fig. 25 shows chamber 100, which is a 10 B. overpressure chamber of the
chamber
I of Fig- 21- it's second longitudinal positions end with commons border 27.
This bottom of
this chamber is screwed on a bottom part 101 which is corresponding the
longitudinal cross-
sectional section 30 of Fig. 21. The thread connecting both parts of the
chamber is gasthread
102., which makes a thighs connection. In the bottom 103 of chamber part 100
is an exit 104,
in which a hose nipple 105 has been screwed. The chamber pan 100 is comprising
a piston
106, which has been schematically drawn. The piston 106 is comprising a hollow
piston red
107, which is comprising a check valve 108, which opens the space 109 between
the piston
and the bottom 103, and thereby let air in from the atmosphere (48) into said
space 109 On
the hose nipple 105. is a base 110 assembled with a hose clamp Ill. The hose
is at its other
end connected to e.g. a valve connector 67. The hole 112 in hose 110.
30
CA 02786315 2012-08-24
244-, 21T
19630 circular chamber design
DESCRIPTION OF PREFERRED EMBODIMENTS
Fig. 30A shows the circular chamber of Fig. 12B, where a piston is moving in a
non-
moving chamber. A circular sub-chamber 961 is having a centerpoint 980 for the
circleround
section line 981 closest to the centerpoint 967 of the circular chamber 960,
in an earlier quadrant
982 than the quadrant 983 wherein said line 981 is lying. The radius line 987
between the circle
centre 980 and the circle section line 981. The circleround section line 984
of the circular sub-
chamber 961 farthest to the centerpoint 967 of the circular chamber 960 is
having a centerpoint 985
in a later quadrant 986 than wherein the line 984 is lying. The radius line
988 between the circle
centre 985 and the circle section line 984. This may be valid for all the
other sub-chambers 962, 963
and 964. The said circleround section lines may be circular section lines in
other preferred
embodiments.
Fig. 30B shows the circular chamber of Figs. 13C and 14D where the piston is
not
moving, but the chamber. Here is the design of the circular chamber and the
sub-chambers identical
with the design of Fig. 30A.
pig.31A shows the Fig. 14D, where the section X-X has shown, of said chamber
1749,
and through the center axis 1750.
Fig. 31B shows an scaled up detail of section X-X of chamber 1749 of Fig. 31A.
T he
chamber wall 1785 is shown in the section X-X. The wall 1785 is comprising
ducts 1786, 1787,
1788, 1789, 1790, 1791, 1792, 1793, 1794, 1795, 1796, and 1797, respectively
which have an
opening towards the chamber 1749, Preferably there is no duct approximately
where the section X-
X is hitting the cross-section ._........_farthest from the center 1750 of the
circular chamber 1749.
From them, around the circumference of the chamber 1749, from both sides
(1786/7/819/90/91, and
1796/5/4/3/2/1) of the line of section X-X are ducts with increased width: the
duct 1791 has the
biggest width. Said ducts are meant to reduce the size of the contact area of
the wall 1785 of the
chamber 1749 with the piston, so as to steer the piston through the circular
chamber, in the direction
of the circular chamber, and to get an adequate propulsion force, which may be
equal around the
circumference of the contact area of a piston inside said chamber 1749 and the
wall 1785, due to
said ducts.
Fig. 32A shows the wall of the chamber and the orthogonal plane to the base
circle
intersects in a circle whose center is at the base circle.
Fig. 32B shows a section of the boundary of the piston.
CA 02786315 2012-08-24
2c8
CA 02786315 2012-08-24
Fig. 32C shows the cap geometri - for area and internal volume of the cap we
need need values of a and h only - are formulas (2.1) and 2.2) -the radius of
the virtual sphere is
given in (2.3).
Fig. 32D shows the piston with end caps-
Fig. 325 shows the piston with end caps inside a transparent Fermi tube
hander.
Fig. 32F shows the pure contact area between the piston and the chamber,
visible inside the transparent chamber wall.
Fig. 32G shows the contact area between the piston and the chamber.
Figg. 32D shows a section of the chamber wall. The chamber reaction force is
(
] 0 marked by gray.
. The total force on the section is orthogonal to the chamber wall. For the
section is
the value of the force proportional to the (variable) longitudinal length of
the shown section, and to
the internal pressure of the piston.
The local reaction force from the chamber wall is proportunal to the
longitudinal width of the
section, which again is lineair in the distance to the center of the center
circle, i.e. the origin.
To first order the length varies around the section as in a tube of constant
radius. Said length
depends linearly on the distance to the origin. The local force varies
correspondingly and hence it is
coordinated to drive the full wall and hence the piston as a pure rotation
around the origin.
The Fermi construction. The generator circle has at each point an orthogonal
plane as shown. The
chamber wall intersects every such orthogonal plane in a circle which has its
center at the generator
circle. The chamber wall is `conical' when choosing the radius of said circle
in the orthogonal pone
to have a linear (or just increasing) value as function of are length along
the generator circle.
Fig. 321 shows the section of Fig. 32H, with an additional section in order to
provide an open view. (1801)
Fig. 32J shows Fig. 32H, and the ector is the component of the gray force ((?U-
)
in the longitudinal direction.
Fig. 32K shows Fig. 32J, with an additional section in order to provide an
open
view.
`Icy Fig. 32L shows Fig. 32J, where the actual sliding force along the wall is
shown
8ei
in blue - it is obtained by projecting the re~ ector orthogonally to the
chamber wall.
Fig. 32M hows Fig. 32L, with an additional section in order to provide an open
view.
-t=om" (A 2 f 29
CA 02786315 2012-08-24
19640 DESCRIPTION OF PREFERRED EMBODIMENTS
Fig. 40A shows a longitudinal crass-section of a pump 1500 with a piston 1501
comprising U-formed support means 1502, an 0-ring 1503 and a flexible
impervious layer 1504,
the last mentioned supported by a foam 1505, at a first longitudinal position
of a chamber 1506-
The support means 1502 are being rotatably fastened to the piston rod 1507
with the suspension
1508, comprising an axle 1510. The pulling spring 1509 is being fastened to
the pistin rod 1507
above the axle 1510, and at the other end on the supper means 1502 closer to
the 0-ring 1503.
The horizontally positioned spring 1511 is supporting the 0-ring 1503. The
impervious flexible
sheet 1504 is comprising a layer 1512 with reinforcements 1514 (only shown in
Fig. 408, 41D,
41E), which has been vulcanized on a layer without reinforcements 1513. The
centre axis 1518 of
the chamber 1506. The angle(,(between a line which is connecting the centre of
the axle 1510
with the centre of the 0-ring 1503, with the centre axis 1518. The impervious
flexible sheet is,
unstressed by a loading from the fluid in the chamber 1506, perpendicular the
centre axis 1518 of
the chamber 1506.
Fig. 40B shows the impervious flexibel sheet 1504 is vulcanized in the 0-ring
1503.
The layer 1513 without reinforecements and the layer 1512 with reinforcements
1515, vulcanized
on each other. The support means 1502 and the horizontal spring 1511 have been
vulcanized on
the O-ring 1503, and the impervious sheet 1504's layer 1513. The end of the
support means 1502
has a small bended flat surface 1516, which fits the shape of the O-ring 1503
when produced. The
0-ring 1503 is being squeezed on the wall 1517 of the chamber 1506.
Fig. 40C shows a longitudinal cross-section of the piston of Fig. 40A at a
second
longitudinal position. The piston rod 1507, the centre axis 1518 of the
chamber 1506, with the
wall 1517. The support means 1502 have been rotated around the axis 1510. the
foam 1505' has
been squeezed. The spring 1509' has been pulled longer. The O-ring 1503 has
been increase in
size, and is still squeezed to the wall 1517 of the chamber 1506. The
impervious sheet 1504' has
been increased in thickness, while the horizontal spring 1511' has been
squeezed toghether. The
angle1 between a line which is connecting the centre of the axle 1510 with the
centre of the 0-
ring 1503, with the centre axis 1518.
Fig. 41A shows top view of the piston 1501 of Fig. 40A and a cross-section of
the
o 49
/ti so y,,, (&( d J- h TIP 0117c.raat.1
!# 1 a.v n-7 cam.-n5z s1v -eana3, wfõ~A tuna1 a.c. -c r<raS"i .~a.chn,~t ,A,
t1~
pisln.'tuf(.
CA 02786315 2012-08-24
pit 0 ax- 3V
chamber 1506 from a first longitudinal position. The wall 1517 of the chamber
1506. The piston
rod 1507. The suspension 1508 of the support means 1502. The axle 1510. The
pulling spring
1509 of the support means 1502.
Fig. 41B shows a detail of the suspension of the support means 1502 on the 0-
ring
1503 and the lying spring 1511 of the piston 1501 of Fig. 40A. The small
beaded flat surface
1516 at the end of the support means 1502, which is vulcanized on the O-ring
1503. The end
1519 of the support means 1502 has a notch 1521, which fits with its size and
shape of the
horizontal lying spring 1511. The boundary 1520 of the lying spring 1511 -
said spring is only
partailly shown, at the end of the support means 1502.
Fig. 41C shows a cross section of the chamber 1506 with the piston 1501 of
Fig.
40A at a second longitudinal position. The suspension 1508 of the support
means 1502.
Fig. 41D shows a spiral reinformcements 1522, 1523, 1524 of the flexible
impervious sheet 1504 - the material is tlcxble. These spirals are drawn
approximately
concentrically to each other, on a certain distance, around the centre axis
1518 of the chamber
1506. Other configurations, e.g. two layers with reinforcements which may
cross each other with
a small angle, may be possible, but not shown.
Fig. 41E shows another reinforcement configuration, namely more or less
classical
reinforcement members 1525, lying concentrically around the centre axis 1518
of the chamber
1506.
Fig. 42A shows a longitudinal cross-section of a piston 1530 comprising
support
means 1502, an 0-ring 1503 and a flexible impervious sheet 1531, the last
mentioned at a certain
angle with the centre axis 1518 of The chamber 1506, at a first longitudinal
position. Said sheet
1531 is being vulcanized (1532) on the piston rod 1507. The angled between a
line which is
connecting the centre of the axle 1510 with the centre of the 0-ring 1503,
with the centre axis
1518. The flexible impervious sheet 1531 has an angle'jwith the centre axis
1518 of the chamber
1506.
Fig. 42B shows a detail of the suspension of the support means 1507, 0-ring
1503 and the
flexible impervious layer 1531, vulcanised together. The top layer 1533 is
comprising the
reinforcements (as those of Figs. 41D-B), while the bottom layer 1534 has no
reinforcements.
The angle between a. line which is connecting the centre of the axle 1510 with
the centre of the
0-ring 1503, with the centre axis 1518.
430- 110' (7qa )
CA 02786315 2012-08-24
Fig. 42C shows a longitudinal cross-section of the piston 1530 of Fig. 42A at
a
second longitudinal position. The angle I between the flexible impervious
sheet 1531 and the
centre axis 1518 of the chamber 1506.
10
CA 02786315 2012-08-24
19650 DESCRIPTION OF PREFERRED EMBODIMENTS
Fig. 50 shows a top view of the holder 1224, and the suspension in the three
rows of
holes 1240, 1241 and 1242, respectively of the stiffeners 1208, 1209 and 1210,
respectively in
said holder 1224. The small beaded ends 1220, 1221 and 1222, respectively.
Please note that the
longer the stiffener 1208, 1209 and 1210, respectively, the longer said small
bended ends 1220,
1221 and 1222, respectively are, the longer the stiffeners are. The hole 1243
of the piston rod
(not shown). The centre axis 1244. The foam 1245 of said piston 1200-
Fig. 51 shows a piston 1200 of Fig. 50 build in a pump 1201 with a chamber
1202
and a top 1203 and shown ata first longitudinal position 1204 of said chamber
1202. In the top
1205 is a bearing 1206, in which a piston rod 1207 is moving. The bearing 1206
is assembled in
said top 1203. The chamber 1202 is of a type where the force is independent of
the pressure (see
19620). The wall 1207 of said shamber 1202. All stiffeners 1205, (1209 dashed)
and 1210,
respectively have a free end of increased diameter 1211, (1212) and 1213,
respectively. The
impervious layer 1214, which is closed by a clamp 1215 to the piston rod 1207,
while at the top
1216 of the piston 1200, the foam can communicate with the fluid in the
chamber 1202, at the
non-pressurized side 1202'. The stiffeners 1208, (1209) and 1210 having a bond
1217, (1218),
1219, repectively and a small berated end 1220, (1221) and 1222, respectively.
Said small bonded
ends 1220, (1221) and 1222, respectively may be pressed by an adjustment
member 1223, which
can turn within a holder 1224, which is sealed by an O-ring 1227 to the piston
rod 1207. Said
adjustment member 1223 is rotatable in said holder 1224, and sealingly
connected to said
impervious layer 1214. The piston 1200 is assembled onto the piston rod 1207
by the holder 1224
being mounted withinxa spring ring 1225 while the clamp 1215 being mounted to
the spring ring
1226. The centre axis 1243 of the chamber 1202.
Fig. 52 shows the bend 1218 of the stifener 1209. The increased diameter 1212
of
stiffener 1209. The chamber 1202. The end 1221.
5o3
CA 02786315 2012-08-24
19650-1 DESCRIPTION OF PREFERRED EMBODIMENTS
Fig. 55A shows a piston 1300 at a 1 n longitudinal position of an advanced
pump, said
piston 1300 is comprising a foam 1301 with metal reinforcement pins 1302,
1303, 1304 positioned
in three circular rows around the piston rod 1306, in a direction towards the
pressurized side of said
piston 1300, which are fastened by magnetic force to a magnetic holder plate
1307 of a holder 1308,
which is mounted on the piston rod 1306, and an impervious layer 1305 around
said foam 1301.
Said holder plate 1307 has been mounted on a holder 1308, glued or by other
means. Said holder
1308 may be able to rotate around the piston rod 1306, and is fastened in the
longitudinal direction
to said piston rod 1306 by two spring plates 1310 and 1311, which fit in
notches 1312 and 1313,
respectively of said piston red 1306. The metal of said pins may be
magnetized. The foam 1301
may made of open cells, preferably PU foam (as discussed in section 19650 of
this patent
aplicafion) - the venting of said open cells is being discussed in Fig. 55B.
The holder 1308 has a
gland 1317 for an O-ring 1318, which is sealing said holder 1308 to the piston
rod 1306. The centre
axis 1319 of the piston 1300. The impervious layer 1305 may be made of natural
rubber (NR), and
the production size and shape is that of the size and shape of the outside of
said piston 1300', when
positioned at a 2"d longitudinal position of the chamber (not shown). That is
to say, that said
impervious layer 1305 is expanding when the piston 1300' is running towards a
1s9 longitudinal
position, by the forces of the expanding foam 1301, Said reinforcement pins
1302, 1303, 1304 may
have a thin layer of PU (not shown), which makes that the PU foam better hold
on said pins 1302,
1303, 1304. This surface treatment may be done by e.g. dipping said pins 1302,
1303, 1304 in PU
foam fluid. The arrow 1335 shows how the foam is being squeezed towards the
piston rod 1306
when the piston 1300 is running towards the 2nd longitudinale position where
the piston has the
reference 1300'. The low pressure side 1315 of the piston 1300, and the
atmpsphere 1316.
Fig. 55B shows an enlargement longitudinal cross-section P-P of the holder
plate
1307, mounted on said holder 1308. The centre axis 1325 of said holder 1308.
The holder plate
1307 has been made of magnetic material, e.g. by compressing metal powder, and
backing it
thereafter. On top of the holder 1308 are venting channels 1314 with centre
axis 1321 (see also Fig.
55C), through channel 1320 the holder plate 1307 (please see Fig,55C),
enabling a communication
of a fluid within the open cells to and from the non-pressurized side 1315 of
said piston 1300 to the
atmosphere 1316 near said non-pressurized side 1315. This construction is also
used in Figs. 55E-H
(incl.).
ao9
CA 02786315 2012-08-24
Fig. 55C shows an enlargement of the holder plate 1307 on the holder 1308. The
underside of said holder plate is comprising three rows 1326, 1327, 1328 of
small closed, rounded
off end holes 1329, 1330, 1331, respectively, in which the ends of the metal
pins pins 1302, 1303,
1304 of Fig. 55A are being hold. Said ends may be rounded off, so that these
fit better in said end
holes 1329, 1330, 1331, respectively. The rounding off of said end holes, and
the sides of the 'log'
holes - the radius is a little bit bigger than the diameter of said pins 1302,
1303 and 1304,
respectively (not shown in this drawing) - enables said pins 1302, 1303, 1304
to rotate in a plane
which is comprising the centre axis of the holder 1308. The centres of rounded
offend holes lay all
in a plane perpendicular the centre axis of the holder 1308. The left side of
said end holes 1329,
1330 and 1331 is not as deep as the right side of each hole, in order to guide
the top of the
respective pins 1302, 1303 and 1304, respectively to the rounded off sides of
said end holes 1329,
1330 and 1331, respectively. Between the bolder 1308 and the holder plate 1307
is a small circular
reces 1332 of the holder 1308, which enables the impervious layer 1305 to be
squeezed between the
holder 1308 and the holder plate 1307, when the holder plate 1307 is fastened
by e.g. screws (not
shown) to the holder 1308.
Fig, 55D is showing an enlargement of the protuberance 1333 in said reces
1332, for
an improved squeezing of the impervious layer 1305 (not shown). This
construction is also used in
the embodiments of Figs. 55E and Fig 55G, enlarged shown in Figs. 55F and 55H,
respectively.
Fig. 55E shows an alternative solution to the one shown in Figs. 55A-D. The
new
reinforcement and the fastening of the foam 1351 (not shown) of the piston
1350 (not shown) to the
holder 1359 have been shown in detail in Fig. 55F. Said piston 1350 is
positioned at a 1"
longitudinal position of an advanced pump. The venting channels 1314 are
indentical with those
described in Figs 55B and 55C.
Fig. 55F shows an enlargement of the holder plate 1358 and the holder 1359.
Said
piston 1350 is comprising plastic pins 1352, 1353 and 1354, respectively, as
reinforcement of said
foam, preferably made of the same material as the foam - preferably PU as
described in Fig. 55A -
which are rotatably fastened with their sphere shaped ends 1355, 1356 and 1357
into sphere cavities
1360, 1361 and 1362, respectively of said holder plate 1358, which is mounted
on a holder 1359,
the last mentioned is mounted on a piston rod 1306, as discussed in the
description of Fig. 55A-
Said holder plate 1358 is additionally comprising further openings 1363, 1364
and 1365,
respectively for guiding said pins 1352, 1353 and 1354, respectively. Said
pins 1352, 1353 and
1354 may have an uneven thickness in order to better hold said foam, An
optimized configuration
3os
CA 02786315 2012-08-24
may be that the thickness uneveness firstly begin a bit further from the
sphere shaped ends 1355,
1356 and 1357 than shown in the drawings, in order not to squeeze the foam
between said pins
1352, 1353 and 1354 near said sphere shaped ends too much, when said pins
1352, 1353 and 1354
turn anti-clockwise, and come nearer each other, when the piston 1300 is
running to a second
longitudinal position. Please see Figs. 55C and 55D for the description of the
fastening of the
impervious layer 1305 between the holder 1359 and the holder plate 1358.
Fig. 55G shows an alternative solution to the one shown in Figs. 55E and 55F
with
holder 1365 and reinforcement pins 1366, 1367 and 1368.
Fig.56H shows an enlargement of said holder 1365 which is comprising a holder
plate
1369 and a circular disk 1370 which is made of flexible material. The
reinforcement pins 1366,
1367 and 1368 are similar with the pins shown in Fig. 56E and 56F, with the
exception, that the
pins 1366 and 1367 (and possibly also 1368 - but not shown here) are
comprising each a pin 1371,
1372 (and 1373 - not shown) which each are connected to the sphere ends 1355,
1356 (and 1357).
Said pins 1372 and 1372 are sticking into the elastic disk 1370, and make the
pins 1352, 1353 and
1354 to automatically ten clockwise, when the piston is running to a I n
longitudinal position.
CA 02786315 2012-08-24
19660 DFSCRIPTION OF PREFERRED EMBODIMENTS
Fig. 60 shows the enlarged container type piston 1400, in a chamber 1401,
which has a centre
axis 1402, at the start and end of a stroke. The chamber is of a type where
the force oa the piston rod is
approx. even dureing the stroke. The shape of the piston at a second
longitudinal position is that of a
`starting' ellipsoids 1403 after having been pressurized from a non stressed
production model, where the
shape is approximately cylinder like shaped (see Figs. 61 and 62). The shape
of the piston near a first
longitudinal position is an ultimate ellipsoids 1404, which is almost a sphere
1404 (dashed). In between has
the piston 1400 the shape of ao ellipsoids. The details of an ellipsoids
instead of al sphere at a F A
longitudinal position are identical with these of a sphere.
Fig. 61 shows an unstressed produced container type piston 1400, which,
stressed may have
the shape of an ellipsoids or a sphere. At the bottom of the figure the non-
movable cap 1420, with a gland
1421 fora O-ring(not shown), which tightens on the piston rod (not shown). A
recess 1422 which is more or
less a gland for an 0-ring (not shown), which tightens the bottom ofthe piston
1400 on a bolt (not shown)
which locks the bottom of the piston rod (not shown), through the hole 1432
0,top of the figure the
movable cap 1423, which is movable on the piston rod (not shown). The gland
1424 for an O-ring (not
shown), which makes the piston tight in the top of sand piston 1400. Both caps
1420 and 1423 having a
recess 1425 and 1426, respectively, which is used to vulcanize the flexible
wall 1427 of the container piston
1400 on said cabs 1420 and 1423, respectivcly. Said wall 1427 is shown in the
figure with two layers: a
reinforced layer 1428 and a layer which functions as a cover 1429 for the
reinforced layer 1428. The dashed
lines show a possible third layer 1430 and 1431, on top ofthc other layers
1428 and 1429, rrspectively,
which is only present on the position where said two layers 1428 and 1429,
respectively have been
vulcanized on the cabs 1420 and 1423.'1he centre axis 1433. The wall 1427 of
the piston 1400 is
approximately parallel with the centre axis 1433. The reinforcement strenge
1440 lie in a parallel pattern,
parallel to the centre axis 1433. The reinforcement pattern 1441 when there
are two layers.
Fig- 61 shows both cabs 1420 and 1423, respectively of Fig. 61. At the outer
side the rounded
off transition 1434 and 1435, respectively, from the flexible wall 1427 to the
portions of said wall 1427
which has been vulcanized on the portions 1425 and 1426 of said cabs 1420 and
1423, respectively. At the
inner sides of the flexible wall 1427, just before said flexible wall 1427
meet the portions 1425 and 1426 of
said cabs 1420 and 1423, respectively is a rounded offtransition 1436 and 1437
These transitions 1436 and
1437 provide a stable transition ofthe wall, when the piston is being stressed
by inflation.
CA 02786315 2012-08-24
3q
19660-2 DESCRIPTION OF PREFERRED EMBODIMENTS
Fig. 63 shows the forces from the wall of an actuator piston (not shown) to
the wall
2275 of a chamber 2276 with differing cross-sectional area's and differing or
equal circumferences,
and having a centre axis 2277. The reaction force 2278 perpendicular to the
wall 2275 to the
expansion force of the wall of the actuator piston (not shown - please see
Fig.64A). The friction
force 2281 from the actuator piston, during rolling, and specifically when
sliding of teh wall of said
actuator piston (not shown - please see Fig. 64A) over the wall 2275 of the
chamber. The reaction
force 2279 of the wall 2275 of the chamber 2276 of teh wall of the actuator
piston (not shown -
It please see Fig. 64A). The component 2280 of said along the wall 2275 of
said chamber 2276. Said
component 2280 has been shown bigger that the friction force 2281. The angle
is between the wall
2275 of the chmaber 2276 and the centre axis 2277 of said chamber 2276.
Fig. 64A shows an ellipsoide type actuator piston 2285 in a chamber 2286 with
a
longitudinal centre axis 2287, of which the wall 2287 of said chamber 2286 has
an angle P with the
centre axis 2288 and is drawn at a 20 angle. The wall 2289 of said actuator
piston 2285 is
engagingly connected to the wall 2287 of said chamber 2287.
Fig. 64B shows an ellipsoide type actuator piston 2290 in a chamber 2291 with
a
longitudinal centre axis 2292, of which the wail 2293 of said chamber 2291 has
an angle y with the
centre axis 2292 and is drawn of 10 . The wall 2295 of said actuator piston
2290 is engagingly
connected to the wall 2293 of said chamber 2291. Said actuator piston 2290 is
shown on three
positions 2296, 2297 and 2298 in said chamber 2291, evidencing that it is
possible to use said angle
in a e.g. a car motor according this invention, having a stroke length of 86.4
mm (as a 1595cc petrol
motor of a Golf Mark II), of comparable dimensions as said current petrol
motor.
30
CA 02786315 2012-08-24
19680-2 DESCRIPTION OF PREFERRED EMBODIMENTS
Fig. 80A shows a chamber 2101 of a pump according to section 19620 (however
any
other chamber configuration may be used), with a central axis 2102, and a wall
2103 of said
chamber 2101, with a piston 2104, 2104' and 2104" according to section 19660,
which may e.g. be
inflatable, on three different longitudinal positions (I", middle and 2nd,
reap.), the wall 2105 of said
piston 2104 is comprising o separate part 2106, of which the cross-section is
circle segment shaped,
which adapts its position to the slope a of the wall 2103 of said chamber 2101
and the centre line
2102.
Fig. 80B shows a sealed up (5:1) detail of the contact surfaces 2107 of the
wall 2103
of the chamber 2101, and 2108 of the wall 2105 of the piston 2104,
respectively, when said piston
2104 is in a first longitudinal position, over which last mentioned surface
2109 said surface 2108 of
the separate wall wall part 2106 can roll and slide. Said contact surfaces
2107 and 2108,
respectively are sealingly connected to the wall 2103 of the chamber 2101 and
to an inclined wall
part 2109 of the said piston wall 2105, said inclined wall part 2109 has a
smaller minimum
circumference than that of the adjacent piston wall 2105, closest to the wall
2103 of said chamber
2101. Clearly is shown that the surface 2105 of said piston 2104 is clear from
the wall 2103 of the
chamber 2101. The contact surface 2107 of said separate wall part 2106 with
the wall 2103 of said
chamber 2101 is comprising parts two surfaces 2110 and 2111, which have an
angle b and angle c
with the wall of said chamber, which at the contact surface 2108 of the wall
2103 are tightly
squeezed to the wall 2103 of said chamber 2101, having the angle f of the
chamber wall 2103 with
the centre axis 2102. When the circumference of the piston 2104 is becoming
bigger, the separate
wall part 2106 may be squeezed towards the wall 2103 of said chamber 2101,
while the rest of the
wall 2105 of said piston 2104 is on tension, thereby retracting from its
original (Fig. 80F) position.
The transversal centre line 2115 of said piston 2104. The centre line 2114 of
the separate wall part
2106 through the middle 2116 of the contact point of the separate wall part
2106 and the wall 2105
of said piston 2104. The angle d between said transversal centre line 2114 and
a line perpendicular
the central axis 2102 of said chamber 2101.
The contact surface 2127, e.g. by vulcanisation of the circle part of the
longitudinal cross-section of
said separate wall part 2106 with the wall of said piston 2104, may be just a
part of said circle
segment near its transversal centre line 2114 of said separate wall part
2106.. The adjacent wall
2105 will than be able to bond more, which enables said seperate wall part to
rernaiuing sticking out
of the wall 2105, and arranging thereby a clearance with the wall 2103 of said
chamber 2101 with
301
CA 02786315 2012-08-24
the adjacent wall 2105 of said piston 2104,2104', 2104". This may also be the
case for the separate
wall part 2123 shown in Figs. 80H, and the toroids 2207, 2244 of Figs. 84B and
84F, respectively.
The circumference of said separate wall part 2106 will also be much bigger
when the piston 2104 is
on a 1' longitudinal position than when said piston is on a 2vd longitiudinal
position.
Fig. 80C shows the separate wall part 2106 when the piston is in a second
longitudinal
position. Here is the wall 2105 of said piston 2104' still clear from the wall
2103 of the chamber
2101, but less than in the case of when the piston 2104' is in the first
longitudinal position (Fig.
805). The angle e between the transversal centre line 2114 and a line
perpendicular the central axis
2102 of said chamber 2101. The transversal centre line 2115 of said piston
2104'.
Fig. 80D shows separate wall part 2106 of which the cross-section is circle
segment
shaped of the wall 2105 of said piston 2104", when the piston 2104 is in a
second longitudinal
position - its position within the circumference of said wall 2105 enables the
piston 2104 to be in
that part of a 2nd longitudinal position of the chamber 2101, where its wall
(not shown) 2103 is
approximately parallel to the centre axis 2102 of said chamber 2101.
Fig. 80E shows an alternative sphere shaped separate wall part 2112 of that
shown in
Figs. 80A-C. The advantage may be, that there may be relatively more clearance
between the
separate wall part 2112 of said piston 2104" and the wall (not shown) 2103 of
said chamber 2101,
than in case of the circle segment shape of the separate wall part 2106 of
Figs. 80A-C. The
transversal centre line 2117 of the separate wall part 2112.
Fig. 80F shows an alternative halfround shape of the separate wall part 2113
with a
centre line 2114, which is identical with the transversal centre line 2115 of
said piston, shown in
Figs. 80A-C. Said separate wall part has been vulcanized on a (scaled up)
piston according to
section 19660, when said piston 2104" is in a second longitudinal position, as
produced.
Fig. 80G shows an improved version of the embodiment of Fig. 80F, where the
transversal centre line 2120 of separate wall part 2113 is positioned under a
line 2121 through the
longitudinal midpoint of the flexible wall of said piston 2104", so to ensure
a proper contact area
with the conical chamber, where the smallest cross-sectional area is at a
second longitudinal
position, i.e. nearest the part of said piston 2104" nearest the 2"d
longitudinal position.. Other
chamber configurations may give another positioning of said separate wall part
2113 and its
transversal centre line 2120.
Fig. 80H shows a longer piston 2126 (than the one shown in Fig. 80G) at a
first
longitudinal position, where the piston 2126 has been inflated. The centre
line 2122 of the separate
310
CA 02786315 2012-08-24
wall part 2123 is positioned under a transversal centre line 2124 through the
longitudinal midpoint
of the flexible wall 2125 of said piston 2126, so to ensure a proper contact
area with the chamber
(not shown). Other chamber configurations may give another positioning of said
separate wall part
2106 on the wall 2125 of said piston 2126
Figs. 801 and 80J show a piston 2130 which has a decreased circumference at
its
transversal centre line 2131, as produced (thus at a second longitudinal
position). The centre line
2132 of the separate wall part 2133, as produced, This enables a better
avoidance of contact of other
parts of the wall 2134 of said piston 2130 than that of the separate wall part
2133, to the wall 2134
of the chamber 2136, specifcically when said piston is moving from an
extrimite 2"d longitudinal
position 2137 of the chamber as shown in Fig. 801 (according section 19620 of
this patent
application - however any other chamber configuration may be used), in the
direction of a IS`
longitudinal position 2139 , when the wall 2134 of the chamber 2136 is
changing from being
parallel to the centre axis 2138 of said chamber 2136 to become non-parallel.
The longitudinal
centre line 2135 of said piston 2130.
Fig. 81 A shows a chamber 2101 of a pump according to section 19620 (however
any
other chamber configuration may be used), with a central axis 2102, and a wall
2103 of said
chamber 2101, with an enlarged piston 2140 according to section 19660 e.g.
according to Fig. 61,
which may be inflatable, on three different longitudinal positions 2140, 2140'
and 2140", the wall
2141 of said piston 2140, 2140', 2140" is comprising more than one, e.g. two
separate wall parts
2142 and 2143, of which each longitudinal cross-section is circle segment
shaped, which adapt its
positions to the parallel- (extremite 2"d longitudinal position), concave-
(transition from extremite
2"d longitudinal position to a position nearer a 1" longitudinal position),
and convex wall (from said
transition to a I" longitudinal position), respectively of the wall 2103 of
said chamber 2101.
Fig. 81B shows scaled up contact surfaces 2144 / 2145 and 2146 / 2147 for the
separate wall parts 2142 and 2143, respectively, which are sealingly connected
to the wall 2103 of
the chamber 2101 at a 1" longitudinal position and to the inclined parts 2148
and 2149, respectively
of the said piston wall 2141, said inclined parts 2148 and 2149 have a smaller
minimum
circumference than that of the adjacent piston walls, which are positioned
closest to the wall 2103
of said chamber 2101. The separate wall parts 2142 and 2143 are postioned at a
certain distance g
from each other, in order to avoid that the wall 2141 of said piston 2140 is
engaging and/or
sealingly engaging with the wall 2103 of said chamber 2101. Depending on the
slope e of the wall
311
CA 02786315 2012-08-24
2103 of the chamber 2101, is the separate wall part 2143 positioned closest to
a first longitudinal
position closer to the transversal centre line 2130 of said piston 2141 than
the separate wall part
2142 positioned closest to a second longitudinal position. The position of the
separate wall parts
may different from the above mentioned, and depends on the shape of the piston
2140, 2140' and
the slope(s) of the wall 2103 of the chamber 2101, wit lithe goal to avoid a
contineous curved wall
of the piston, so as to avoid that the piston 2140, 2140' can roll over the
surface 2103 of the
chamber 2101.
Fig. 81C shows a scaled up detail of said contact surfaces when said piston
2121 is
positioned between a first and a second longitudinal position. Also here is
there no contact between
the wall 2136 of said piston 2140' and the wal12103 of said chamber 2101.
Please remark that the angles between a line perpendicular the wall 2103 of
said chamber and the
centre axis 2137 and 2138 of said separate parts - with a sloped wall 2103 of
said chamber 2101,
are said angles not identical, and bigger than those of Fig. 81 B.
Fig. 81D shows said (scaled up 12.5:1) piston, which is positioned in an
extremite
second longitudinal position, as produced. As it is in Fig. 80D may the piston
2140" comprising the
separate wall parts 2142 and 2143 be in said chamber 2101 (not shown), there
where its wall 2103
(not shown) is parallel to the centre axis 2102 of said chamber 2101 (not
shown). The avow shows
the transversal centre line 2130 of the piston 2140".
Fig. 82A shows a chamber 2101 of a pump according to section 19620 (however
any
other chamber configuration maybe used) with a longitidinal center line 2102,
with a piston 2145 which
may be inflatable, said piston 2145, 2145' and 2145"is shown on three
different longitudinal
positions, respectively, the piston well 2146 is comprising two parts 2147 and
2148, respectively,
having different circumferences in a transversal plane, where the part 2147
closest to the first
longitudinal position is having the biggest circumference, and is comprising
the contact area's 2149,
2149' and 2149", respectively between the wall 2103 of the chamber 2101 and
the piston wall
2146. The size of said contact area's may be different on each of the three
longitudinal positions.
Fig. 82B shows a scaled up (5:1) detail of said contact area 2149 when said
piston
2145 is in a first longitudinal position. The two piston wall parts 2147 and
2148. The piston wall
part 2147 is comprising an outer skin part 2150, which is ending just under
the contact area 2149,
3It
CA 02786315 2012-08-24
with a stepped transition 2199 of the wall 2146 from wall part 2147 to wall
part 2148, where the
piston wall part 2147 nearest a 1" longitudinal position is closest to the
wall 2103 of the chamber
2101, that the wall part 2148, which is nearest a 2"d longitudinal position.
Under said skin part 2150
may be another skin part 2151, preferably a layer, optionally a reinforcement
layer. This skin part
2151 is preferably present in the whole piston wall 2146. Approximately (an
overlap would be
preferable) there where the outer skin part 2150 of the piston wall part 2147
ends, begins an inner
skin part 2152, which is part of the piston wall part 2148, and which is
positioned behind the outer
skin part 2151. The content of said piston may be a fluid, a mixture of fluids
or a foam (not shown).
There is no contact between the skin part 2148 of the wall 2146 of said piston
2145 and the wall
2103 of said chamber 2101. The transversal centre line 2153 of said piston
2145, which is nearer a
first longitudinal position than the stepped transition 2199 of the wall 2146
from wall part 2147 to
wall part 2148.
Fig. 82C shows a scaled up detail of said contact area 2149'when said piston
2145'
is positioned between a first and a second longitudinal position. Also here is
there no contact
between the skin part 2151 of the wall part 2148' of said piston 2145' and the
wall 2103 of said
chamber 2101. Shown is that the contact area 2149' of the wall part 2147'wit
hthe wall 2103 of said
chamber 2101 may be different from the contact area 2149 of Fig. 82B. The
transversal centre line
2153' of said piston 2145'. This centre line 2153' may be positioned closer to
a 1" longitudinal
position that said stepped transition 2199 of the wall 2146 from wall part
2147 to wall part 2148.
Fig. 82D shows said (scaled up 12.5:1) piston 2145" of which the wall 2146 of
said
piston 2145" , which is positioned at a second longitudinal position - the
chamber is not shown.
The wall part 2147 has a diameter e z, while the wall part 2148 has a wall
part 0 z-z: (zp0). The
transversal centre line 2153" of the piston 2145".
Fig. 93A shows the piston 2121" of Figs. 82A-D (incl.), as produced in a 2'd
longitudinal position, and the piston rod 2151.
Fig. 83B shows the piston 2121 of Fig. 83A at a 1" longitudinal position,
where said
piston 2121 is being inflated - arrow 2152 - through its piston rod 2151.
Fig. 83C shows the piston 2121 of Fig. 83B in a 1" longitudinal position,
where said
piston 2121 is beying deflated - arrow 2153 - through its piston rod 2151,
after the postien of the
movable cab 2154 has been secured on the piston rod 2151, by a clamp 2155.
313
CA 02786315 2012-08-24
Fig. 83D shows the piston 2121 of Fig. 83C in a 1" longitudinal position,
where the
cavity (not shown) (2156) of said piston 2121 is beying filled - avow 2157 -
through the enclosed
space (2159) its piston rod 2151, with a foam (not shown) (2158). This foam
may be of a PU foam
(Polyurethan), preferably as a mixture of a Memory PU foam type (please see
section 19640 of this
patent application), and a standard PU foam type - this is a good compressible
foam with an open
cell structure.
Fig. 83E shows the piston 2121 of Fig. 83D in a 1" longitudinal position,
where the
cavity (not shown) (2156) of said piston 2121 has been filled with said foam
(not shown) (2158),
after said clamp 2155 has been removed. It is now possible to compress the
wall 2146 of said piston
2121, e.g. by moving said piston rod 2151 incl. said piston 2121 from a 1"
longitudinal position to a
2"tl longitudinal position, without much force.
It may be necessary to add a compressed fluid, such as a gaseous medium,
through
said foam's open cells, in order to achieve the proper sealing force and/or a
proper compression
force for said piston.
Fig. 83F shows said piston 2121" with inserted and now compressed foam (not
shown) (2158) of Figs. 83D and its piston rod 2151, and a combined pressure
sensor 2160 and
inflation valve 2161 according Fig. 3B of W02109/083274, for the enclosed
space (2159) (not
shown) + cavity (2156) (not shown) of said piston 2121". Said piston rod 2151
may preferably he
of the type where its enclosed space (not shown) (2159) has a constant volume
(W02110/094317),
optionally a type with a variable volume according to WO 2100/070227.
Fig 83G shows an enlargement of the combined sensor - inflation valve
arrangement
of Fig. 83F. the inflation valve 2161 with the inlet 2196 for the enclosed
space 2159 of the piston
rod 2151. The inlet 2194 of the pressure sensor 2160 and its outlet 2195
according to
WO2111/000578.
Fig. 83H shows said piston 2121" with inserted foam (not shown) (2158) of
Figs.
83D and its piston rod 2151, and a combined pressure sensor 2162 and inflation
valve 2161
according Fig. 5 of W02111/000578, for the enclosed space (2159) (not shown) +
cavity (2156)
(not shown) of said piston 2121". Said piston rod 2151 may preferably be of
the type where its
enclosed space (not shown) (2159) has a constant volume (W02110/094317),
optionally a type with
a variable volume according to WO 2100/070227.
3(y
CA 02786315 2012-08-24
Fig. 831 shows an enlargement of the combined sensor - inflation valve
arrangement
of Fig. 83H. The inflation valve 2161 with the inlet 2196 for the enclosed
space 2159 of the piston
rod 2151. The inlet 2194 of the pressure sensor 2162 and its outlet 2197
according to
W02111/000578.
Fig. 83J shows said piston 2121" with inserted foam (not shown) (2158) of
Figs. 83D
and its piston rod 2151, and a combined pressure sensor 2164 and inflation
valve 2165 according
Fig. 9 of WO2111/000578, for the enclosed space (2163) (not shown) + cavity
(2156) (not shown)
of said piston 2121". Said piston rod 2151 may preferably be of the type where
its enclosed space
(not shown) (2163) has a constant volume (W02110/094317), optionally a type
with a variable
volume according to WO 2100/070227.
Fig. 83K shows an enlargement of the combined sensor - inflation valve
arrangement
of Fig. 83J. The inflation valve 2165 with the inlet 2198 for the enclosed
space 2163 of the piston
rod 2151. The inlet 2194 of the pressure sensor 2164 and its outlet 2199
according to
W02111/000578.
The expansion to its default size of said PU foam cited in Fig. 83D, to blow
up said
wall 2146 of said piston 2121 - a spring 2166, which is pulling said movable
cab 2154 towards the
fixed cab 2167, is adding force for said expansion. Said spring 2166 is
positioned over said piston
rod 2151, and is attached to said movable cab 2154 and a fix 2168, which is
positioned in a
construction 2168 of said piston rod 2151.
In order to solve the problem that the volume of an inflated ellpsoide is much
bigger
than the volume of an small enclosed space, e.g. that of a piston rod, the
inflated volume has been
substantially reduced e.g. to an inflatable torotd, while the expansion of the
wall of the piston has
been remained. This means that when an inflated piston is pushed from a 1"
longitudinal position to
a 2 longitudinal position the rize of the internal pressure is small,
enabling the piston to be
depressed in size (without jamming).
Fig. 84A shows an ellipsoide shaped type of piston 2170 at a 1" longitudinal
position
(chamber not shown) having a centre axis 2171, and a piston rod 2172, a fixed
cab 2173 and a
movable cab 2174, on which both the elastically flexible wall 2175 of said
piston 2170 has been
mounted, e.g. by vulcanizing, said wall 2175 has a reinforcement layer 2176.
Said piston 2170 has a
wall of the type shown and discussed in Figs. 82A-D (incl). Said wall 2175 is
has on the inside a U-
3t'
CA 02786315 2012-08-24
shaped vault 2177, in which an inflatable toroid 2178 is positioned, which has
a wall 2179 with an
reinforcement 2180, so that the circumferential size of said toroid 2178 is
increased by a higher
inside pressure, whithout change of its outer cross-sectional diameter d, and
decreased by a lower
pressure. This means that when said piston 2170 is at a 2nd longitudinal
position of a chamber (not
shown), the wall 2175' of said piston 2170 is approximately parallel to the
centre axis 2171, and
said toroid 2178' is positioned adjacent said wall 2175 and said piston rod
2172, which has a
constriction 2181, for giving space to said toroid 2178'. The wall 2179 of
said toroid 2178 is much
ticker than that when said piston 2170 is at a 1" logitudinal position, having
a reinforcement 2180
which having an angle more than 541 44'.(The flexible hose 2182 is through its
channel 2190
communicating with the enclosed space 2183 of said piston rod 2172, and at the
other end of said
channel 2182 communicating with the channel 2184 within said toroid 2178. The
U-shaped vault
2177 is guiding said toroid 2178 when said piston is moving between 1" and 2nd
longitudinal
positions. in order to lower the force which is necessary for the expansion of
the wall 2175 of said
piston 2170, when the piston 2170 is moving from a 2"d to a 1" longitudinal
position, a pulling
spring 2185 is postioned over said piston rod 2172, and attached to said
moving cab 2174 and a
hook 2186 which is fastened in said constriction 2181 of the piston rod 2172.
Observe the small
diameter of the channel 2184' inside said toroid 2178', when said piston 2170
is at a 21d
longitudinal position of a chamber. The cross-section of the flexible hose
2182 with its channel
2190. Said channel 2190 is at one end conunonicating with the enclosed space
2183, and at the
other end communicating with the channel 2184 and 2184'. The high pressure
side 2187 of the wall
2175 of said piston 2170 is supported by a foam 2193 (e.g. PU foam of the kind
disclosed in section
19630 of this patent application, and used in a foam piston) within the inside
2192 of the wall 2175
- 2187 of said piston 2170. Because said foam 2193 has open cells, it is
communicating either with
the enclosed space 2183 (not shown) or preferably with the low pressure side
2188 (not shown - or
refer to Fig. 84B), optionally the high pressure side 2191 of said piston (not
shown). Said braid
2178, 2178' is shown having a centre axis 2194 which is converging with the
transversal centre axis
2195 of said piston 2170, in order to gain an optimal ellipsoide shaped wall
2175. At the high
pressure end of said piston rod 2172 is a pressure sensor shown which has been
discussed in Figs.
83FU1.
Fig 84B shows a piston 2200 of an ellipsoide shaped type, which is an,
improved and
simplified version of the piston 2170 of Fig. 84A, where the whole inside 2201
within the wall 2202
of the piston 2200 is comprising said PU foam 2203, discussed its Fig. 84A.
Inside the yF (] 2202 of
3(6
CA 02786315 2012-08-24
said piston 2200 is a channel 2205, mounted (e.g. by vulcanisation) on th
inside of said wall 2202.
Said channel 2205 is communicating with the channel 2206 of the toroid 2207 at
one end , and at
the other end the enclosed space 2208 of said piston 2200 in the piston rod
2209. The foam 2203 is
communicating with the either the enclosed space 2208 through a channel (not
shown), or it is
communicating with preferably the low pressure side 2210 of said piston 2200
through a channel
2211 in the movable cab 2212, or optionally with the high pressure side 2211
of said piston 2200
(not shown). Said toroid 2207 is shown having a centre axis 2213 which is
converging with the
transversal centre axis 2214 of said piston 2200, in order to gain an optimal
ellipsoide shaped wall
2202. However, as disclosed in Figs. 80A-C, H, where the contact surfaces 2107
and 2108 of said
separate part 2106, with a centre axis 2114, were positioned closer to a
second longitudinal position
of the chamber, due to the shape of said chamber, than the the transversal
centre axis 2115 of said
piston 2104, 2104', 2104", so that said centre axis' 2114 and 2115 are not
converging with each
other. This may also be the case with the contact area of said toroid 2207
with the wall of the
chamber (not shown), as it may also be positioned lower than the transversal
centre axis 2214 of
said piston 2200 (not shown here). At the high pressure end of said piston rod
2209 is a pressure
sensor shown which has been discussed in Figs. 831I/I.
Fig. 84C shows the piston 2220 having the same construction of the piston 2170
of
Fig. 84A, with the exception of the wall 2221 on the low pressure side of said
piston 2220. Said
wall part 2221 is not a part of an ellipsoide as shown in Fig. 84A, but that
of a cone, shown in
tension.
Fig. 84D shows a sphere shaped piston 2230 at a I" longitudinal position and
2230"
at a 2nd longitudinal position, having a longitudinal centre axis 2231, and a
transversal centre axis
2232, 2232". Said piston 2230", 2230 is comprising a separate part 2231, 2231"
respectively with
a transversal centre axis 2233, 2233". Said transversal centre axis 2233,
2233" is positioned under
said a transversal centre axis 2232, 2232" and the first mentioned is
positioned nearest a 2nd
longitudinal position. Other configurations of a separate part shown in Figs.
80A-E are also here
possible.
Fig. 84E shows a sphere shaped piston 2235 at a 1" longitudinal position and
2235" at
a 2"d longitudinal position, having a longitudinal centre axis 2236, and a
transversal centre axis
2237, 2237", respectively. The stepped transition 2238 of the wall 2234 from
wall part 2239 to wall
part 2240.
311
CA 02786315 2012-08-24
Fig. 84F shows a sphere shaped piston 2241 at a le longitudinal position and
2241" at
a 2"d longitudinal position, having a longitudinal centre axis 2241, and a
transversal centre axis
2243, 2243", respectively. Said piston 2241 is comprising a separate part
2244, 2244" with a
transversal centre line 2245, 2245", respectively, the last mentioned is
positioned under the
transversal centre axis 2243, 2243" of said piston 2241, 2241". respectively,
thus nearest a 2"a
longitudinal position. The inflation of the toroid 2244 may be done as shown
in Figs. 84A or 84B.
201 DESCRIPTION OF PREFERRED EMBODIMENTS
Fig-1-0O~hows-the-sesalled-indicator--diagrast-his-diagrazo--se~Ã~afica}}y-
shows-Fhs-
adiabatic relation between the pressure p and the pump stroke volume V of a
traditional single-stage one- -
way working piston pump with a cylinder with a fixed diameter: The iueoease in
the operating force to
be applied per stroke can be read directly from the diagram and is quadratic
to the diameter of the
cylinder. The pressure p, and thus the operating force F, increases during the
stroke normally until the
valve of the body to be inflated has been opened.
Fig. 102A shows the indicator diagram of a piston pump according the
iuvenfion. It shows that
the diagram for pressure p is simular to that of traditional pumps, but that
the operating force is different
and depends entirely on the chosen area of the transversal cross-section of
the pressurizing chamber.
Thus depends entirely on the specification, e.g. that the operating force
should not exceed a certain
maximum or that the size of the operating force is fluctuating according to
ergonomic demands. This is
specifically demanded in the case when a manually operated pomp is only
transporting the media
without significant change in the pressure as it is e.g. the case with water
pumps. The shape of the
longitudinal and/or transversal cross-section of the pressurizing chamber may
be any kind of curve
and/or line. It is also possible that the transverse] cross-section eg incases
by increasing pressure
(Fig. 10213). An example of the operating force is the dashed thick ]me, I or
2. The different wall
possibilities marked I and 2 correspond to the earlier mentioned lines 1,2 of
the diagram. The A-section
relates to a pump of which only the piston is moving, while the B-section
relates to pumps where only
the chamber is moving. A combination of both movements at the some time is
also possible.
Fig. 102B shows an example of ua indicator diagram of a piston pump that has a
chamber with
a transversal cross-section that increases by increasing pressure.
Figs. 103A,B,C,D show details of the first embodiment. The piston moves in the
presse- rizing
chamber which comprises cylindrical and cone-shaped portions with circular
transversal cross-sections
with diameters that decrease when the pressure of the gaseous and/or liquid
media increases- This is
based on the specification that the operating force should not exceed a
certain maximum. The transition
between the various diameters is gradual without discrete steps. This means
that the piston can slide
easily in the chamber and adapt itself to the changing areas aril/or shapes of
the transversal cross-
sections without loss of sealing ability. If the operating force has to be
lowered by increasing pressure,
CA 02786315 2012-08-24
the transversal cross-sectional area of the piston is decreasing and by that
the length of the cucornference
as well. The circumfericat length reduction is based on compression up to the
buckling level or by
Jrelaxatimr The longitudinal cross-section of the piston means is trapezoid
with variable angle less than
e.g- 40 with the wall of the pressurizing chamber, so that it cannot deflect
backwards. The dimensions
of the sealing means change in three dimensions during every stroke. A
supporting portion of the piston
means, e.g. a disk or integrated ribs in the sealing means, e.g. positioned on
the non-pressurized side
daring a pumping stroke of the piston protects against deflection under
pressure. A loading portion of
the piston means, e.g. a spring washer with several segments, may also be
mounted e.g. on the
pressurized side of the piston. This squeezes the flexible sealing portion
towards the wall. This is
expedient if the pump has not been used for some time and the piston means has
been folded for some
time. By moving the piston rod, the sides of the trapezoid cross-section of
the sealing portion of the
piston means will he pushed axially and radially, so that the sealing edge of
the piston follows the
decreasing diameter of the pressurizing chamber. At the end of the stroke, the
bottom of the chamber in
the centre has become higher in order to reduce the volume of the dead romp
The piston rod may
mainly be guided in the cap which locks the pressurizing chamber. As the
piston in both directions of its
movement seals to the wall of the chamber, the piston rod e.g. comprises an
inlet channel with a spring
force-operated valve, which is closed in case of overpressure in the chamber.
Widrout the use of the
loading portion in the piston means, this separate valve may be superfluous.
In the pump design
according to the invention, the parts of the pump have been optimized for
working forces. The inside
diameter of the pump is over the main part of the pump chamber length larger
than that of existing
pumps. Consequently, the inlet volume is higher, even though the volume of the
remaining part of the
chamber is lower than that of existing pumps. This ensures that the pump can
pump quicker than
existing pumps, while the maximmr operating force required is sigaifrcarnly
reduced and lower than the
level reported by consumers to be comfortable. The length of the chamber can
be reduced, so that the
pump becomes practical, even for women and teenagers. The volume of a stroke
is still higher than that
of existing pumps.
Fig. 103A shows a piston pump with a pressurizing chamber 1 with portions of
different areas
of its transversal cross-sections of wall sections 2,3,4 and 5. The piston rod
6. The cap 7 stops the piston
means and guides the piston rod 6. The transitions 16,17 and 18 between the
section with the walls 2,3,4
CA 02786315 2012-08-24
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320 .
rzz y
and 5. The longitudinal centre axis 19 of the chamber I. The piston 20 at
the..begirming and 20' at the
end of the pu- stroke _
Fig. 103B shows the sealing portion 8 made of an elastic material and the
loading portion 9,
e.g. a spring washer with segments 9.1, 9.2 and 9.3 (other segments not shown)
and a support portion
10 of the piston means attached to the piston rod' 6 between two portions of
locking means 11. The
piston rod 6 has an inlet 12 and a valve 13. The angle , between the sealing
portion 8 of the piston
means and the wall 2 of the pressurizing chamber 1. The sealing edge 37. The
distance a is the distance
from the sealing edge 37 to the central axis of the chamber 1 in a transversal
cross-section at the
beginning of the stroke.
Fig. 103C shows outlet channel 14 in a means 15 which reduces the volume of
the dead room.
Angle a between the sealing portion 8' of the piston means and the wall 5 of
the pressurizing chamber
1. The distance a' is the distance from the sealing edge 37 to the central
axis of the chamber 1 in a
transversal cross-section at the end of the stroke. Shown is that distance a'
is approximately 41% of
distance a. The loading portion 9'.
Fig. 103D shows the longitudinal cross-section of the chamber of a floor pump
(ei,n, 60 - 19.3
mm, length 500 mm) according to the invention of which the transversal cross-
sections are chosen so
that the operating force remains approximately constant and is chosen in
accordance with ergonomic
demands: e.g. as in the Figure: 277 N. Other force sizes can also be chosen
This is only giving the
starting point for the quantification of a floorpump according to the
invention as a constant operating
force may not be ergonomically correct, As a comparison the cross-sections of
an existing low pressure
floor pump 32 mm, length 470 mm) is shown in dotted lines, and that of an
existing high pressure
floor pump (s,_, 27 mm, length 550 men) is shown in dashed lines. It is
clearly shown that the floor
pump according to the invention both has a bigger stroke volume, thus faster
inflating tyres, and a lower
operating force than existing pumps. The chamber according to the invention
can be tailored to
ergonomic demands during the entire stroke.
Figs. 104A,B,C,D,E,F show details of the second preferred embodiment. The
sealing
portion of the piston means is made of an elastically deformable material
supported by, a
support means which can rotate around an axis parallel to the center axis of
the chamber. The
321
y~- ~ ~ 2 Z 4r
consequence of this movement is that it supports a larger area of the sealing
means the higher the
fissure is in the chamber. The loading portion for the Support portion
initiates the movement of --
support means. The loading portion in the form of a flat-shaped spring can
change dimensions in a
direction perpendicular to the centre line of the chamber. The spring becomes
more and more stiff the
higher the pressure in the chamber. It can also be a spring on the arcs where
the support means torus
around. By decreasing the diameter of the sealing portion it increases its
length This is the case with an
elastically deformable material which is only a bit compressable, like e.g.
rubber. Therefore the piston
rod sticks out of this sealing means at the beginning of a stroke. If other
material for the sealing portion
is chosen, its length may remain urchangend or may decrease by decreasing its
diameter.
Fig. 104A shows a piston pump with a pressurizing chamber 21 with portions of
different
transversal cross-section areas. The chamber has cooling ribs 22 at the high-
presser side. The chamber
can be (injection) moulded. The piston rod 23. The cap 24 guides the said
piston rod. The piston 36 at
the beginning and 36' at the end of a pump stroke.
Fig. 104B shows the elastically defom,able sealing portion 25 which is
fastened to the piston
rod 23 by means 26 (not drawn) A part 27 of the piston rod 23 is sticking out
of the sealing portion 25.
Support portion 28 is hanged op on ring 29 which is fastened to the piston rod
23. Support portion 28
can tam around axis 30. Loading portion 31 comprises a spring which is
fastened in a bole 32 onto the
piston rod 23. The sealing edge 38.
Fig_ 104C shows that pan 27 of piston rod 23 is almost covered by the
elastically deformed
sealing means 25', which has now increased its length and decreased its
diameter. Thesealing edge 38'.
The distance a' between the sealing edge 38 and the central axis 19 of the
chamber is approximately
40t of that of distance a in the shown transversalcrosssection.
Fig. 104D shows section A-A of Fig. 104B. The loading portion 31 is fastened
at one end in
the hole 32 of the piston rod.23. The support portion 28 and the ring 29. The
support portion is stopped
by a stop surface 33 (not drawn). The support portion 28 is guided by the
guiding means 34 (not
drawn).
Fig. 104E shows section B-B of Fig. 104C. The support means 28 and the loading
means 31
are moved towards the piston rod 23. The rib 22.
CA 02786315 2012-08-24
322
Fig. 104F shoves an alternative for the loading means 31. It comprises springs
35 on each axis
30.
Figs. 105A,B,C,D,E,F,G,H show details of the third embodiment. It is a variant
of the first
embodiment. The sealing portion comprises a flexible impervious membrane for
gaseous and/or liquid
media. This material can change its dimensions in three directions without
folds. This sealing portion is
mounted in an 0-ring which seals to the wall of the chamber. The O-ring is
loaded to the wall by a
loading means, eg. a spring in the circumference. The O-ring and spring are
further supported by a
support means which can rotate around an axle fastened to the piston rod. This
support means can be
loaded by a spring.
Fig. 105A shows a longitudinal cross-section of a piston pump analog to that
of Fig. 103A, The
piston 49 at the beginning and 49' at the end of the pump stroke.
Fig. 105E shows a piston means at the beginning of a stroke comprising a
sealing means 40:
e.g. a stressed skin, that is fastened to a sealing means 41: e.g. an O-ring.
This O-ring is loaded by a
spring 42 which is positioned on the circumference of the sealing mesas 41 and
sealing means 40. The
central axis 39 of the spring 42. The O-ring 41 and/or spring 42 is supported
by support means 43 that
can rotate on axis 44 which is attached to the piston rod 45
and positioned perpendicular to the central axis 19. It comprises a certain
amount of separate members
43', loaded in compression during the (compression) pump stroke. These are
positioned around the
circumference of the sealing means 40,41 and the loading means 42, which they
support. The support
means 43 can be loaded by a spring 46. The angle i between the wall of the
chamber 2 and the support
mean 43. The piston rod 45 is without an inlet or a valve. A supporting ring
and/or loading ring in the
form of a spring can be mounted in the 0-ring as an alternative for spring 42
(not drawn). The sealing
edge 48.
Fig. 105C shows the piston means at the end of the stroke. The sealing means
40', 41' is
thicker than at the beginning of a stroke: 40,41. The spring 46'. The Angle r
between the wall 5 and the
support means 43 at the end of a stroke. The distance a' between the sealing
edge 48 and the central axis
19 of the chamber is approximately 22% of the distance a at the beginning of
the stroke in the shown
cross-Section. Smaller distances e.g. 15%, 10% or 5 % are possible, and depend
only on the construction
of the suspension of the piston on the piston rod. Therefore, this is also
valid for all other embodiments.
CA 02786315 2012-08-24
323
Fig. 105D shows section C-C of Fig. 105A with supportmeans 43, axle 44 and
bracket 47:
Fig. 105E shows section D-D from Fie 105A.
Fig. 105F shows the two positions of the piston 118 of Fig. 105G and 118' of
Fig. 10511 in a
chamber. -
Fig. 105G shows a piston which is made of a composite of materials. It
comprises a skin 110 of
elastic impervious material and fibers 111. The fiber architecture results in
the dome-form when it is
under internal pressure. This form stabilizes the piston movement. As an
alternative the sealing means
may comprise a liner, fibers and a cover (not drawn). If the liner is not
tight, an impervious skin may be
added (not drawn). All materials at the compressed side of the piston comply
with the specific environ-
mental demands of the chamber. The skin is mounted in a sealing portion 112.
Within the s'on and the
sealing portion a spring force ring 113 may be mounted and which can
elastically deform in its plane,
and which enhances the loading of the ring 114. The scaling edge 117-
Fig 105H shows the piston of Fig. 105G at the end of a pump stroke. The dome
has been
compressed into shape 115, if there is still full overpressure. Shape 110' is
a result if the overpressure is
decreased e.g. after the media has been released.
Figs. 106A,B,C show details of the fourth embodiment. The piston means
comprises a rubber
tube which has a reinforcement, e.g. in the form of a textile yarn or curd
wound around. The neutral
angle between the tangent of the reinforcement winding and the centre line of
the hose (= so-called
braid angle) is mathematically calculated to be 54044'. A hose under internal
pressure will not change
2D dimensions (length, diameter), assuming no elongation of the reinforcement.
In this embodiment, the
diameter of the piston means decreases in relation to the decreasing diameter
of the cross-section of the
chamber at increasing pressures. The braid angle should be wider than neutral.
The shape of the main
part of the longitudinal cross-section of the pressurizing chamber is
approxunately a cone shape due to
the behaviour of the piston means. At the end of the pump stroke, when the
compressed medium has
been removed from the chamber, the piston means increases its diameter and its
length is decreased.
The diameter increase is no practical problem. The sealing force from the
piston to the wall of the
pressurizing chamber ought to increase by increasing pressure. This may e.g.
be done by the choice of a
braid angle so that the piston diameter decreases a bit less than the decrease
in diameter of the
transversal cross-section of the chamber. Therefore, the braid angle may also
be chosen to be smaller
CA 02786315 2012-08-24
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32y
than neutral and/or being neuhat In general, the choice of the braid angle
depends entirely on the
-design specification and therefore the braid angle may be wider and/or
smaller and/or teutral It -s even
possible that the braid angle changes from place to place in the piston.
Another possibility is that in the
same cross-section of the piston several reinforcement layers are present with
identical and/or different
braid angles: Any type of reinforcement material and/or reinforcement pattern
can be used. The place of
the reinforcement layer(s) may be anywhere in the longitudinal cross-section
of the piston. The amount
of linings and/or covers may be more than, one. It is also possible that a
cover is absent. The piston
- means may also comprise loading and supporting means, e.g. those showed
earlier. In order to be able
to adapt to larger changes in the areas of cross-sections of the chamber a bit
different coustntction of the
piston means is necessary. The cone comprises now fibers which are under
tension. These are coiled
together in the top of the cone near the piston rod, and at the open side of
the cone at the bottom of the
piston rod. These may also be fastened to the piston rod itself. The pattern
of the fibers is designed e.g-
so that these are under higher tension the higher the pressure is in the
chamber of pump where the media
is to be compressed. Other patterns are of course possible, just depending on
the specifcation. They
deform the skin of the cone, so that it adapt itself to the cross-section of
the chamber- The fibers may lie
loose on the liner or loose in channels between a liner and a cover or they
may be integrated on one of
the two or in both. It is necessary to have a loading means in order to obtain
an appropriate sealing to
the wall if there is no pressure under the cone yet. The loading member e.g. a
spring force member in
the form of a ring, a plate ear. may be build in the skin e.g. by inserting in
a moulding process. The
suspension of the cone on the piston rod is better than of the foregoing
embodiments because the piston
will now be loaded by tension. Therefore being more in balance and less
material is needed- The skin
and the cover of the piston may be made of elastically deformeble material
which comply with the
specific environmental conditions, while the fibers may be elastically or
stiff, made of an appropriate
material.
Pig. 106A shows a longitudinal cross-section of a pump with chamber 60. The
wall portions
61,62,63,64,65 art both cylindrical 61,65 and cone-shaped 62,63,64.
Transitions 66,67,68,69 between
the said portions. The piston 59 at the beginning and 59' at the end of a pump
stroke.
Fig. 106B shows piston means 50, a hose with a reinforcement 51, The hose is
fastened to the
piston rod 6 by clamp 52 or similar. The piston 6 has n'bs 56 and 57. Ribs 56
prevent the movement of
CA 02786315 2012-08-24
the piston means 50 relative to the piston rod 6 towards the cap 7, while sibs
57 prevent the movement
of the piston [Weans 50 relative to the piston rod 6 away from the cap 7.
Other configurations of the
fitting may be possible (not shown). On the outside of the hose, a protrusion
53 seals against the wall 61
of the chamber 60. Besides the reinforcement 51 the hose comprises lining 55.
As an example cover 54
is shown too. The shape of the longitudinal cross-section of the piston means
is an example. The sealing
edge 58.
Fig. 106C shows the piston means at the end of the stroke, where the gaseous
and/or liquid
medium is under pressure. The piston means may be designed in such a way that
the diameter change
only takes place via a radial change (not shown).
Fig. 106D shows the piston 189 of Fig. 106E and 189' of Fig. 106F at the
beginning and at the
end respectively of a pump stroke in a chamber of Fig. 106A.
Fig. 106F. shows a piston means which has approximately the general shape of a
cone with top
angle 2 ,. It is shown when there is no overpressure at the side of the
chamber. It is mounted in its top
on a piston rod 180. The cone is open at the pressurized side of the piston.
The cover 181 comprises a
sealing portion shown as a protrusion 182 with a sealing edge 188 and an
inserted spring force member
183, fibers 184 as support means and a liner 185. The member 183 provides a
loading to the cover, so
that said pretension 182 seals the wall of the chamber if there is no
overpressure at the side of the
chamber. The fibers 184 can lie in channels 186, and these are shown situated
between the cover 181
and the liner 185. The liner 185 can be impervious - if not, a seperate layer
209 (not shown) at the
pressurized side is mounted on the liner 185. The fibers are mounted in the
top 187 of the cone to the
piston rod 180 and/or breach other The same is the case at the bottom end of
the piston rod 180.
Fig. 106F shows the piston means at the end of a stroke. The top angle is now
2 z and
the distance a' between the sealing edge 188 and the central axis 19 of the
chamber is now
approximately 44 % of that distance a at the beginning of the stroke in the
shown cross-section. _
Fig. 107A,B,C,D,E show details of the fifth embodiment of the pump, with a
piston which is
constructed as another composite. structure, comprising a basic material which
is very elastic in all three
dimensions, with a very high degree of relaxation. If it is not tight of
itself, it may be made tight with
c -g. a flexable membrane- on the pressurized side of the piston means. The
axial stiffness is -
accomplished by several integrated stiffeners, which in a transversal cross-
section lie in a pattern, which
32~
optimally fills this section, while the in-between distance is reduced the
smaller the diameter of the
transversal cross-sectional section is. which in most cases means the hider
the pressure in the
pressurizing chamber is. In the longitudinal section of the piston the
stiffeners lie in several angles
between an axial direction and the direction of the surface of the piston
means. The higher the pressure
rates are, the more these angles are reduced and come near the axial
direction. Now therefore the forces
are being transferred to the support means, e.g. a washer, which is connected
to the piston rod- The
piston means can be mass-produced and is inexpensive. The stiffeners and, if
necessary, the sealing
means in the form of said flexable membrane, may be injection moulded together
with said basic
material in one operation. E.g. may the stiffeners be bonded together in the
top, which makes handling
16 easier. It is also possible to make the membrane by 'burning' it in said
basic material, during or after
injection moulding. This is specifically convenient if the basic material is a
therneoplast. The hinges
should than not be 'burned'.
Figs. 107F,G,H,I,J,K,L,M shows embodiments of the chamber and a sixth
embodiment of the
piston, fitting to this chamber. The sixth embodiment of the piston is a
variant on the one of Fig.
107A,B,C,D,E. If the change of the area of a transversal cross-section of the
piston and/or the chamber
between two positions in the direction of movement is continuous but still so
big that this results in
leakages, it is advantageous to minimize the change of the other parameters of
the cross-section. This
can be illustrated by using e.g. a circular cross-section (Fixed shape) the
circumference of a circle is D,
while the area of a circle is No D (D -- diameter of the circle). That is to
say, a reduction of D will
only give a linear reduction of the circumference and a quadratic reduction of
the area. It is even
possible to also maintain the circumference and only reduce the area. If also
the shape is fixed e.g. of a
circle there is a certain minimum area. Advanced numeric calculations where
the shape is a parameter
can be made by using the below mentioned Fourier Series expansions. The
transversal cross-section of
the pressurizing chamber and/or the piston can have any form, and this can be
defined by at least one
curve. The curve is closed and can approximately be defined by two unique
modular parametrisation
Fourier Series expansions, one for each co-ordinate function:
.f (x J= 2 +~co cos (px)+~do sin (pxJ
CA 02786315 2012-08-24
where
?lof()cos(P_)dx
c ~
do=? fa f (x)an(Pt) dx
rz
0 <xs2w, oe1~I
p>oP
=cos-weighted average values of f(x),
dp = sin-weighted average values off(x),
p = representing the order of trigonometrical fineness
Figs. 107F, 107K show examples of said-curves by using a set of different
parameters in the
following formulas. In these examples only two parameters have been used If
inure coefficients are
used, it is possible to find optimized curves which comply to other important
demands as e.g. curved
transitions of which the curves have a certain maximum radii and/or e.g. a
maximum for the tension in
the sealing portion which under given premises may not exceed a certain
maximum. As an example:
Figs. 107L, 107M show optintized convex curves and non-convex curves to be
used for possible
deformations of a bounded domain in a plane under the constraints that the
length of the boundary curve
is fixed, and its numerical retrvamre is murirruzed. By using a starting area,
and a starting bourdary-
length it is possible to count on a smallest possible curvature for a certain
desired target area.
The pistons shown in a longitudinal cross-section of the chamber have been
drawn mainly for
the case that the boundary curve of the transversal cross-section is circular.
That is to say: in the case
that the chamber has transversal cross-sections according to e.g. those non-
circular of Figures 107F,
107K, 107L, 107M the shape of the longitudinal cross-section of the pistons
may be different.
All kinds of closed curves can be described with this formula, e.g. a C-curve
(see
PCTIDK9'//00223, Fig. IA). One characteristic of these curves is that when a
line is drawn from the
mathematical pole which lies in the section plane it will intersect the curve
at least one time. The carves
CA 02786315 2012-08-24
32
94- 17I
are symmetrical towards a line in the section plane, and could also have been
generated by the single
Fourier Series expans on which follow A piston n chamber w 11 he rnn a t~rsch
e ndserLihe
curve of the transversal cross-section is symmetric with reference to a line
which lies in the section plane
through the mathematical pole. Such regular curves can approximately be
defined by a single Fourier
Series expansion:
I(x)=co +Ycy cos(px)
2
where
?f()cos(px)et
0<x<2n, xc J)j
P>0,pcll2
c, = weighted average values effft),
p = representing the order of trigonometrical finenesr
When a line is drawn from the mathematical pole it will always intersect the
curve only one time. Specific formed sectors of the cross-section of the
chamber and/or the piston can approximately be
defined by the following formula:
I (x)= z+~cv cos (3px)
where
CA 02786315 2012-08-24
CA 02786315 2012-08-24
32~j
f(X) ro+a?= sin'(n)X
ee= 6rf(x)cos(3px)dr
P>0=pc lY,
v = weighted average values of f(x),
p = representing the order of trigonometeicat fineness
and where this aoss-section in polar co-ordinates approxheately is represented
by the following
formula:
r=n,+a sin("- p)I
where
020,
a>_0,
m?0,eo ER,
n>_0,n E R,
05g_< 2,
and where
r = the limit Of the 'petals" in the circular cross section of the activating
pin,
ro = the radius of the circular cross section around the axis of the
activating pin,
a = the scale factor for the length of the "petals ",
r=~, = rp + a
m = the parameter for definition of the 'petal" width
n = the parameter for definition of the number of petals"
CA 02786315 2012-08-24
330
= the angle which bounds the curve.
The inlet is placed close to the end of the stroke due to the nature of the
sealing portion
of the piston means.
These specific chambers may be prothrced by injection moulding, and e.g. also
by the
use of so-called superplastic forming methods, where almmrrium sheets are
boated and pressed by air
pressure either forced in a tool cavity or formed using also tool movement.
Fig. 107A shows a piston pump with a pressurizing chamber 70 in a longitndinat
section
to with a dlindrical portion 71, a transition 12 to a continueous concave
curved portion 73, another -
transition 74 to an almost cylindrical portion 75. The piston means 76 and 76'
is shown at the beginning
respectively at the end of the pump stroke. At the, end of the oudet channel
77 a cheek valve 78 can be
mounted (not shown). -
Fig. 1070 shows the piston mearu 76 comprising an elastic material 79 which
gives the
]ongimdina] section of the piston at low pressures the form of approximately a
cone. 'the material 79
functions also as a loading means. The bottom comprises a sealing means 80,
which can be folded
radially - this scaling means 80 is partially also working as a loading means.
The mom support means
comprises of stiffeners 81 and 82, of which the stiffeners 81 mainly support
the sealing edge 83 of the
piston means to the wall of the pressurizing chamber 70 while the other
sttfeners 82 transfer the load
from the sealing means 80 and the basic material 79 to the support means 84
e.g a washer which is
itself supported by the piston rod 6. The sealing means 80 is in this position
of the piston stream 76 still
a little bit folded, so that fold 85 will load the sealing edge 83 the more
the higher the pressure will be in
the chamber 70. Stiffeners 82 arc joined together in the top by joint 86. In
this position of the piston
means 70 the stiffeners 81 and 82 having angles between and with the central
axis 19, where is
approximately parallel with the central axis 19 of the pressurizing chamber
70. The angle , between the
surface of the piston 76 and the central axis 19.
Fig. 1070 shows the piston means 76' at the cod of the pump stroke. The
sealing means
80 has been folded together, while the elastic material 79 has been squeezed
together, resulting in the
stiffeners 81,82 are directed approximately parallel with the central axis 19.
The angle r between the
surface of the piston means 76' and the central axis 19 is positive, but
almost zero. The distance a'
337
between the sealing edge 83 and the central axis 19 in the shown cross-section
is 39% of that distance a
at the begmn of the stroke The mling metes 80'
Fig. 107D shows a transversal cross-section E-E of the piston means 76,
showing the
basic elastic material 79, stiffeners 81 and 82, folds 87 of the sealing means
80. Piston rod 6.
Fig. 107E shows a transversal cross-section F-F of the piston means 76',
showing the
basic elastic material 79, stiffeners 81 and 82, folds 87 of the sealing means
80. Clearly shown is that
the elastic material 79 is squeezed together.
Fig. 107F shows a series of transversal cross sections of a chamber where the
area
decreases in certain steps, while the circumference remains constant - these
are defined by two unique
modular parametrisation Fourier Series expansions, one for each co-ordinate
function. At the top left is
the cross-section which is the start cross-section of said series. The set of
parameters used is shown at
the bottom of the figure. This series show decreasing area's of the
transversal cross-section. The
numbers in bold in the figures show the decreasing cross-sectional area's of
the different shapes, with
the one in the comer left up as the starting area size.
The area of the shape of the cross-section bottom, right is approximately 28%
of the one of the top, left.
Fig. 107G shows a longitudinal cross-section of the chamber 162, of which the
transversal cross-sectional area changes by remaining circumference along the
central axis.
The piston 163- The chamber has portions of different cross-sectional area's
of its transversal cross-
section of wall sections 155,156,157,158. The transitions 159,160,161 between
said wall sections.
-Shown are cross-sections G-G, H-H and I-I. Cross-section G-G has a
circelround cross-section, while
cross-section H-H 152 has approximately an area between 90-10% of the one of
cross-section G-G.
Fig. 107H shows transversal cross-section H-H 152 of Fig. 107G and in dotted
lines as a
comparison cross-section G-G 150. Cross-section H-H has approximately an area
between 90-70% of
that of cross-section G-G The transition 151, which is made smooth. Also shown
is the smallest pan of
the chamber, which has approximately 50% of the-cross-sectional area of cross-
section GG.
Fig. 1071 shows a transversal cross-section 1-1 of Fig. 107G and in dotted
lines as a
comparison cross-section G-G: The cross-section 1-I has approximately an area
of 70% of that of cross-
section G-G- The transition 153 is made smooth. Also shown is the smallest
part of the chamber.
CA 02786315 2012-08-24
3~z
Fig. 1077 shows a variant of the piston of Fig. 107A.C in cross-section H-H
from Fig.
1070. The piston is now made of elastic material which is also hopes-vines so
that a se orate seafine__
means is not necessary. The distance c and d are different and by that the
deformations of the piston in
the same transversal cross-section H-H.
Fig. 107K shows a series of transversal cross-sections of a chamber where the
area
decreases in certain steps, while the circumference remains constant - these
are defined by two unique
modular paramelrisation Fourier Series expansions, one for each co-ordinate
function. At the top left is
the cross-section which is the start cross-section of said series. The set of
parameters used is shown at
the bottom of the figure; This series show decreasing area's of the
transversal cross-section, but it is also
possible to increase these areas by remaining the circumference constant. The
numbers in bold in the
figures show the decreasing cross-sectional area's of the different shapes,
with the one in the comer left
up as the starting area size.
The size of the cross-sectional area bottom right is approximately 49% of the
starting area size
tell, top.
75 Fig. 107L shows a convex curve optimized for a certain fixed length of the
boundary
curve, and a smallest possible curvature The general formula for the smallest
radius of curvature,
corresponding to the largest curvature of the figure shown in Fig. 107L is:
(L-IL (4nAd
The length specified by y is determined by:
1
Y=2 L4ZA,
where
r = smallest radius of curvature
L = boundary -length = constant
A, = decreased value of the staring domain area Ao
CA 02786315 2012-08-24
CA 02786315 2012-08-24
As an example from Fig. 103D: Domain area Ap = (30)' and boundary length L =
60 = 188-5
corresponding to the area and boundary length of a disk of radius 30. The
length is required to be
constant, but the area is decreased to the value A, to be specified. The
desired final configuration should .
_ have the area A, = (19/2) = 283.5. The convex curve with the smallest
possible curvature of the
boundary curve is now:
= 1.54
1/r=0.65
x=89.4
The curve on the Figure is not on scale and the Figure shows only the
principle.
The curve may further be optirruzed by exchanging the straight lines by curves
which may improve the
sealing of the piston to the wall.
Fig. 107M shows a non-convex curve optimized fora certain fixed length of the
boundary curve, and a smallest possible curvature. The general formula for the
smallest radius of
curvature, corresponding to the largest curvature of the figure shown in Fig.
107L is:
VVV r+4
].i
The length specified by xis determined by:
x=1L-(J+v)A,
2 n+l
where
r = smallest radius of curvaure
L = boundary -length = constant
A, decreased value of the starting domain area Ao
The non-convex curve (with obvious modifications of the string-like
intermediate double curve) with the
smallest possible curvature of the boundary curve:
~sy
=6.3
=1k=0.16
x=42
The curve on the Figure is not on scale and the Figure shows only the
prieeciple.
Fig. 108A,B,C show a seventh embodiment of the pump, with a piston means which
is
constructed as another composite structure, comprising a compressable medium
as e.g. a gaseous
medium like for example air (also is possible: only a non compressible medium
as e.g. a liquid medium
_ like water or a combination of compressable and a non-compressible medium)
within a closed chamber
which is constructed ase.g. a reinforced hose. It may be possible that the
lining, reinforcement and
cover at the pressurized side of the piston means is different from that of
the non-pressurized side - here
the skin can be built up as a pre-formed shaped skin, holding this shape
during the pump stroke. It is
also possible that the skin is made of two or more parts, which itself are pre-
farmed shaped, one at the
non-pressurized side of the piston means, the other on the pressurized side
(please see Fig_ 10813 part X
esp. parts Y+Z). During the pump stroke the two parts hinge in each other
(please see Fig. 108B XY
and ZZ). The adaptation of the sealing edge to the chamber in the transversal
cross-section may result in
a change of the cross-section of the piston at its sealing edge, and this may
result in a change of the
volume inside the piston. This volume change may give a change in the pressure
of the compressabte
medium and may result in a changend sealing force. Moreover, the compressable
medium functions as a
support portion as it transfers the load on the piston to the piston rod.
Fig. 108A shows a longitudinal section of the pressurizing chamber 90,
comprising a
contineous convex curve 91, with the piston 92 at the beginning of the pump
stroke, and 92'.at the cad
hereof. The high pressure part of the chamber 90 comprises an outlet channel
93 and an inlet channel 94
both with a check valve 95 and 96, respectively (not shown). For low pressure
purposes the check valve
95 can be removed. -
Fig. 108th shows piston 92 which is vulcanised directly on the piston rod 97,
comprising
a compressible medium 103 within a lining 99, a reinforcement 100 and a cover
101. Part X of the skin
99,100,101 is pre-shaped as it is with the parts Y and Z at the pressurized
part of the piston means 92.
A hinge XY is shown between part X and part.Y of the skin. Part X has an
average angle , with the
central axis 19 of the pressurized chamber 90. Part Y and Z are connected to
each other and have an in-
CA 02786315 2012-08-24
3~5
between angle õ which is chosen so that the forces will be directed mainly to
the piston rod- The angle
between parts Y' and Z' and is chosen so that the higher the fume in the
rh~mber thr. mgr re hie pariis_
perpendicular to the central axis. Hinge ZZ between the half of part Z. The
sealing edge 102.
Fig. 108C shows the piston at the end of a stroke. Part X' of the skin has now
an angle
with the central axis, white parts X' and Y' has an in-between angle i, and an
approximately
unchangend angle between Y' and Z'. The angle between the half parts of part Z
is approximately
zero. The distance a' between the sealing edge 102 and the cetetral axis 19 of
the chamber in the shown
transversal cross-section is approximately 40% of the distance a at the
beginning of the stroke. The
sealing edge 102' and compressed medium 103'.
Fig. 109A,B,C,D show details of a combination of a pressurizing chamber with
fixed
dimensions and an eight embodiment of a piston which can change its
dimensions. The piston is an
inflatable body which fills a transversal cross-section of the chamber. During
the spoke it may
constantly change its dimensions on and nearby the sealing edge. The material
may be a composite of an
elastically delbnnable liner and a support means like e.g. fibers (e.g glass,
boron, carbon or around),
Is fabric, filatement or the like- Depending on the fiber architecture and the
total restdting loading on the
piston - the piston is shown having a bit internal overpressure -it may result
in approximately the form
of a sphere or approximately an elleptical curve ('rugby ball' like form) or
any shape in between, and
also other shapes. A decrease of the transversal cross-sectional area of e.g.
the chamber causes a
decrease in the size of the inflatable body in that direction and a 3-
dimensional reduction is possible due
to the fiber architecture, which is based on the 'trellis-effect' where fibers
arc shearing Iayerwise
independantly from each other. The cover is also made of an elastically
deformable material, suitable for
the specific environmental conditions in the chamber. If the ]finer use the
cover is impervious it is
possible to use a separate bladder inside the body, as the body contains an
gaseous and/or liquid media.
The support means as e.g. fibers can only give strength by themselves.if the
pressure inside the body is
bigger than outside, because these am than in tension. This pressure condition
may be preferable to
obtain a suitable seating and life time. As the pressure in the chamber can
change constantly, the
pressure inside the body should do the same and be a bit higher, or should
always be highenat any point
of the pump stroke by remaining constant. The last solution can only be used
for low pressures as
otherwise the piston may jam in the chamber. For higher pressures in the
chamber an arrangement may
CA 02786315 2012-08-24
be necessary so that the internal pressare vary accordingly to the variations
of the pressure its the
chamber + shratld he a hit high rr Th' ay be arhiese t ~ceuegal ruff eeu
armngements-.-loading
regulating means - which are based on the principles to change the volume
and/or pressure of a medium
inside the piston and/or to change the temperature of the medium inside -
other principles are possible
too, as e.g. the right choice of the material of the skin of the piston, e.g.
a specific rubber type, where it
is E-module which defines the deformability, or the right choice of the
relative amount of the
compressable part of the volume inside the inflatable body, and its
compressabitity. Here a non-
- compressible mediumis used inside the piston. By a change in the size of the
transversal cross-sectional
area at the sealing edge the volume of the piston may change, because the size
of the piston in a
direction of the movement is constant. This change causes the eorrcompressable
medium to flow to or
from the a spring-force operated piston inside the hollow piston rod. It is
also possible that said spring-
force operated piston is situated elsewhere. The combination of the pressure
caused by the change of the
volume of the piston and the change in the pressure due to said spring-force
results in a certain sealing
force. The said spring-force works as a fine-turfing for the sealing force. An
improved load regulation
may be achieved by exchanging the non-comprmsable medium by a certain
combination of a
compressable and a non compressible medium, where the compressable medium
works as a load
regulating means. A father improvement is when said spring is exchangend by
the operation force of the
piston of the chamber, as it makes the retraction of the piston easier, due to
a lower sealing force and a
lower friction. A temperature raise of a medium inside the piston may be
achieved when specifically a
medium is chosen which can quickly be warmed up.
Fig. I09A shows the longitudinal cross-section of the pressurizing chamber of
Fig. IOSA
with the piston 146 of Fig. 109B at the beginning of a stroke, and of Fig.
109C at the end 146' of a
stroke- -
Fig. 109E shows a piston 146 with an inflatable body having a wall comprising
fibers
130 which have a pattern, so that the inflated body becomes a sphere. Cover
131 and liner 132. An
impervious bladder 133 is shown inside the sphere. The sphere is directly
mounted on the piston sod
120. It is locked at one end by a cap 121, and at the other end by cap M. The
hollow channel 125 of
the piston rod 120 has a hole 123 in its side inside the sphere, so that the
loading means being e.g. an in-
compressible medium 124 contained within the sphere can flow freely to and
from the channel 125 of
CA 02786315 2012-08-24
the piston rod 120. The other end of the channel 125 is closed by a movable
piston 126 which is loaded
by a m ne L27 Thyõ mnng ie muted-ttn-a-p isrnn and 128 The s ng 72"1 nines the
pressur.Y ^thin
the sphere and the sealing force. The sealing surface 129 is approximately in
a line contact with the of
the adjacent wall of the chamber. The fibers are only shown schematically (in
all the drawings of this
application)-
Fig. 109C shows the piston of Fig. 109B at the end of a stroke where the area
of
the cross-section is smallest. The sphere has now a much bigger sealing
surface 134 which is uniform
with the adjacent walls of the chamber. The piston 126 has moved in relation
to its position shown in
Fig. 9B, as the non-compressible medium 124' has been squeezed out of the
distorted sphere. In order
to minimize the friction force it is possible that the cover at the sealing
surface has ribs (not shown) or
may have a low-frictional coating (as well as the wall of the chamber - not
shown). As none of the caps
121 and 122 can move along the piston rod 120, the trellis effect only can be
a part of the material
surplus of the skin. The rest shows as a 'shoulder' 135 which may reduce the
life time considerably,
while it increases the friction as well. The sealing edge 129'. The distance
a' between the sealing edge
129' and the central axis 19 of the chamber in the shown transversal cross-
section is approximately 48%
of the distance a of at the beginning of the stroke.
Fig 109D shows an improved inning of the sealing force, by having inside the
sphere an
incompressible medium 136 and a compressible medium 137. the pressure of the
media is regulated by
a piston 139 with a sealing ring 139 and a piston rod 140 which is directly
connected to the operating
force. The piston 138 can slide in the cylinder 141 of the sphere. The step
145 secures the sphere on the
piston rod 140.
Figs. I IOA,B,C show an improved piston where the surplus of the skin by small
cross-
sections of the chamber can be released which means an improved life time and
less friction. This
method concerns the fact that a suspension of the piston on the piston rod can
translate and/or rotate
over the piston rod to a position farther from the side of the piston where
there is the biggest pressure in
the chamber. A spring between the movable cap and a stop on the piston rod
functions as another
loading regulating means.
Fig. 1IOA shows a longitudinal cross-section of the chamber 169 of a pump
according to
the invention with two positions of the piston 168 respectively 168'.
CA 02786315 2012-08-24
378
Fig. S10B shows a piston with an inflatable skin with a fibers 171 in at least
two layers
with a fiber architecture which resu]Ls_ip aggt22z matelv~phere - 11ipxo'd õ
hen ;r,flatrvt incid tlw
piston. can be an impervious layer 172, if the skin is not tight. The media is
a combination of a
compressible medium 173, e.g. air, and an incompressable medium 174, e.g.
water. The skin 170 is
mounted at the end of the piston rod in cap 175 which is fastened to the
piston rod 176. The other end
of the skin is hingend fastened in a movable cap 177 which can glide over the
piston rod 176. The cap
177 is pressed towards the pressurized part of the chamber 169 by a spring 178
which is squeezed at the
other end towards a washer 179 which is fastened to the piston rod 176. The
sealing edge 167.
Fig. 1100 shows the piston of Fig. 110B at the end of the pump stroke. The
spring 178'
is compressed. The same is valid for the iecompressable medium 174' and the
compressible medium
173'. The skin 170' is deformed, and has now a big sealing surface 167'. The
distance a' between the
sealing edge 167 and the central axis of the chamber is approximately 43% of
the distance a at the
beginning of the stroke.
Figs. 11 LA,B,C show a piston which has at both of its ends in the direction
of movement
on the piston red a movable cap which takes the surplus of material away. This
is an improvement for a
piston in a one-way piston pump, but specifically is it possible now to use
the piston in a dual operating
pump where any stroke, also the revaction stroke, is a pump stroke. The
movement of the skin during
the operation is indirectly boated due to stops on the piston rod. These are
positioned so that the
pressure of a medium hs, the chamber cannot strip the piston from the piston
rod _
Fig. 111A shows a longitudinal cross-section of the chamber with an improved
piston
208 at the beginning and at the end (200') of a stroke.
Fig. 111B shows a ninth embodiment of the piston 208. The skin of the sphere
is
comparable with the one of Fig. 10. An impervious layer 190 inside is now
tightly squeezed in the cap
191 in the top and the=cap 192 in the bottom. Details of said caps are not
shown and all kinds of
assembling methods may be used. Both caps 191,192 can translate and/or rotate
over the piston rod 195.
This can be done by various methods as e.g. different types of bearings which
are not shown. The cap
191 in the top can only move upwards because of the existance of the stop 196
inside the piston. The cap
192 in the bottom can only move downstairs because the stop 197 prevent a
movement upwards- The
'tuning' of the sealing force comprises a combination of an incompressable
medium 205 and a
CA 02786315 2012-08-24
CA 02786315 2012-08-24
compressab]e medium 206 inside the sphere, a spring-force operated piston 126
inside the piston rod
195. The media car~freely flow througl the 1 207 of the - t nd thmgh hnlec 199
7,()Q ?Ql t?
rings or the like 202, 203 in said cap in the top and in said cap in the
bottom, respectively seal the caps
191,192 to the piston each The cap 204, showed as a screwed assembly at the
end of the piston rod 195
thighthens said piston rod. Comparable stops can be positioned elsewhere on
the piston rod, depending
on the demanded movement of the skin.
Fig. 111C shows the piston of Fig. I I1B at the end of a pump stroke. The cap
191 in the
top is moved over a distance x" from the stop 196 while the bottom cap 192
is.pressed against the stop
M. The compressable medium 206' and the non-compressable medium 205'.
Figs. I12A,B,C show an improved piston in relation to the earlier one's. The
improvements have to do with a better tuning of the sealing force by the
loading regulating means, a
reduction of friction by a smaller sealing contact surface, specifically by
smaller cross-sectional area's
The improved tuning concerns the fact that the pressure inside the piston now
directly is influenced by
the pressure in the chamber due to a pair of pistons on the same piston rod
and which is by that
independant of the existance of an operation force on the piston rod. This may
be specifically
advantageous during a stop in the pump stroke, if the operation force would
change, e.g. increase,
because the sealing force remains constant and no loss of sealing occurs. At
the end of a pump stroke
when the pressure in the chamber is decreased, the retraction will be more
easy due to lower friction
forces. In the case of a dual operating pump, the loading regulating means may
be influenced by both
sides of the piston, e.g. by a double arrangenment of this load regulating
means (not shown). The shown
arrangement of the pistons is complying with a specification: e.g. an increase
of the pressure in, the
chamber will give an increase of the pressure in the piston. Other
specifications may result in other
arrangements. The relation may be designed so that the increase can be
different from a lineair relation.
The construction is a pair of pistons which are connected by a piston rod. The
pistons may have an equal
area, different size and/or a changing area.
Due to a-specific fiber architecture and the total resulting loading - it is
shown with a bit
internal overpressure - the shape of the piston in a longitudinal cross-
section is a rhomboid figure. Two
of its corners in this section work as a sealing surface; which gives a
reduced contact area by smaller
transversals crow sections of the chamber. The size of the contact surface may
still be increased by the
3"
existance of a ribbed outer surface of the skin of the piston- The wall of the
chamber and/or the outside
of the piston can have a coating as e.t, nylon or cau be made of aloes-
friction ateria]
Not drawn is the possibility of a chamber which has transversal cross-
sectiozal shapes
according to e.g. those of Fig. 107F with a piston which has (in this case as
an example) three separate
pistons according to e.g. Fig. 112A-C which each seats in the first circular
cross-sectional area (Fig-
107F top, left), each other and the boundary curve, while at another point of
the longitudinal axis of the
chamber each seal one of the liner lobe-shaped parts and each other (Fig. IF
e.g. top, right), while at
still another point each seal one of the three lobe-shaped parts only.
Fig. 112A shows a longitudinal cross-section of a piston chamber combination
with a
tenth embodiment of a piston 222 at the beginning and at the end (222') of a
stroke in a chamber 216.
Fig. 112B shows a piston of which the main consuuction is described in Figs.
IIB and
11C. The skin comprises at the outside ribs 210. The skin and the impervious
layer 190 at the inside are
squeezrd at the top between an inner part 211 and an outer part 212, which are
screwed together. At the
bottom the similar construction exists with the itdrer part 213 and the outer
part 214. inside the piston.
there is a compressable medium 215 and a non compressable medium 219. The
pressure inside the -
piston is tuned by a piston arrangement which is directly activated by the
pressure of the chamber 216.
The piston 148 in the bottom which is connected to the pressurizing chamber
216 is mounted on a piston
rod 217 while at the other side another piston 149 is mounted and which is
connected to a medium of the
piston 222. The piston rod 217 is guided by a slide bearing 218 - other
bearing types can also be used
(not shown). The pistons on both sides of the piston rod 217 can have
different diameters - it is even
possible that the cylinder 221 in which these are moving, are exchanged by two
chambers, which can be
of a type according this invention - by that, the piston and/or pistons are
also of a type according this
invention. The sealing edge 220. the piston rod 224- Distance d, between the
piston 148 and orifice
223.
Fig. 112C shows the piston of Fig. 112A at the end of a stroke, while there is
still
high pressure in the chamber 216. Sealing edge 220'. The load regulating means
148' have a different
distance from the orifice 223 towards the chamber. Piston 148' and 149' are
shown positioned at a
larger distance than in Fig. 112B from the orifice 223: di.
CA 02786315 2012-08-24
Pig. 113A,B,C show the combination of a pump with a pressurizing chamber with
elactirally def~ahl oiall with d"fjyapnt re 54f the trap al rr h arxt p""--
stun a.itha fixrd
geornenical shape. Within a housing as e.g. cylinder with fixed geometrical
sizes an inflatabel chamber
is positioned which is inflatable by a medium (a non-compressable and/or a
compressable medium). It is
also possible that said housing can be avoided. The inflatable wall comprising
e.g. a liner-fiber-cover
composite or also added an impervious skin. The angle of the scaling surface
of the piston is a his bigger
than the comparative angle of the wall of the chamber in relation to an axis
parallel to the movement.
This difference between said angles and the fact that the momenlaneous
deformations of the wall by the
piston takes place a bit delayed (by having e.g. a viscose non-compressable
medium to the wall of the
chamber and/or the right tuning of load regulating means, which are similar to
those which have been
shown for the pistons) provides a sealing edge, of which its distance to the
central axis of the chamber
during the movement between two piston and/or chamber positions may vary. This
provides a cross-
sectional area change during a stroke, and by that, a designable operation
force. The cross-section of the
piston in the direction of the movement however may also be equal, or with a
negative angle in relation
to the angle of the wall of the chamber - in these cases the 'nose' of the
piston ought to be rounded of.
In the last mentioned cases it may be more difficult to provide a changing
cross-sectional area, and by
that, a designable operation force. The wall of the chamber may be equiped
with all the already shown
loading regulating means the one showed on Pig. 112B, and if necessary with
the shape regulating
means. The velocity of the piston in the chamber may have art effect on the
sealing.
Fig. 113A shows piston 230 at four positions of the piston in a chamber 231.
Around an inflatable wall a housing 234 with fixed geometrical sizes. Within
said wall 234 a
compressable medium 232 and a non-compressable medium 233. There may be a
valve arrangement for
inflation of the wall (not shown). The shape of the piston at the non-
pressurized side is only an example
to show the principle of the sealing edge. The distance between the sealing
edge at the end and at the
beginning of the stroke in the shown transversal cross-section
is approximately 39%_ The shape of the longitudinal cross-section may be
diferent from the one shown
fig. 113E shows the piston after the beginning of a stroke. The distance from
the sealing
edge 235 and the central axis 236 is 7.1 The angle between the piston sealing
edge 235 and the central
axis 236 of the chamberr. The angle v between the wait of the chamber and the
central axis 236- The
CA 02786315 2012-08-24
3tiZ
angle v is shown smaller than the angle . The sealing edge 235 arranges that
the angle v becomes as big
as the angle
Other embodiments of the piston are not shown.
Fig. 113Ã shows the piston during a stroke. The distance from the sealing edge
235 and
the central axis 236 is zz - this distance is smaller than z,
Fig. 113D shows the piston almost at the end of stroke. The distance from the
sealing
edge 235 and the central axis 236 is z, - this distance is smaller than z,.
Fig. 114 shows a combination of a wall of the chamber and the piston which
have
changeable geometrical shapes, which adapt to each other during the pump
stroke, enabling a continuous
sealing. Shown is the chamber of Fig.l3A now with only a non-compressable
medium 237 and piston
222 at the beginning of a stroke, while the piston 222" is shown just before
the end of a stroke. Also all
other embodiments of the piston which can change dimensions can be used here
too. The right choice of
velocity of the piston and the viscosity of the medium 237 may have a positive
effect on operations. The
longitudinal cross-sectional shape of the chamber shown in Fig. 14 may also be
different.
20
CA 02786315 2012-08-24
3k3
653 DESCRIPTION OF PREFERRED EMBODIMENTS
Figi01A-shewsihe4ongitudim2l-eoess-sestiosa ef-a-nonmoving-aen pr zed-pistots4
a54be
first longitudinal position of a non-pressurized chamber 1, having at that
position a circular cross-
sections with a constant radius. The piston 5 may have a production size
approximately the diameter of
the chamber 1 at this fast longitudinal position. The piston 5* when
pressurized to a certain pressure
level is shown. The pressure inside the piston 5* results in a certain contact
length.
Fig. 201B shows the contact pressure of the piston 5* of Fig. 201A. The piston
5* assay jam at
this longitudinal position.
Fig. 202A shows the tongimdinal cross-section of anon-moving non-pressurized
piston 5 at the
1o first longitudinal position and the piston 5' at the second longitudinal
position of a non-pressurized
chamber 1, the chamber having circular cross-sections with a constant radius
at both the first and second
longitudinal positions. The piston 5 may have a production size approximately
the diameter of the
chamber I at this fast longitudinal position. The piston 5' shows the piston
5, non-pressurized
positioned into the smaller cross-section of the second longitudinal position.
Fig. 202B shows the contact pressure of the piston 5' on the wall of the
chamber at the second
longitudinal position. The piston 5' may jam at this longitudinal position.
Fig. 202C shows the longitudinal cross-section of a non-moving non-pressurized
piston 5 at the
fast longitudinal position and the piston 5' at the second position of a non-
pressurized chamber 1, the
chamber having circular cross-sections with a constant radius at both the
first and second longitudinal
positions. The piston 5 may have a production size approximately the diameter
of the chamber 1 at this
first longitudinal position. The piston 5'* shows the piston 5, pressurized to
the same level as the one of
Fig. IA, positioned into the smatter cross-section of the second longitudinal
position.
Fig. 202D shows the contact pressure of the piston 5'* on the wall of the
chamber at the second
longitudinal position. The piston 5'* may jam at this longitudinal position:
the friction force may be 72
kg.
Fig. 203A shows the piston 5 of Fig. 201A, and the deformed piston 5"* when
pressurized to _
the same pressure level of that of piston 5* of Fig. 201A. The deformation is
caused by the pressure in
thechamber 1*, when the piston may not have means to limit the stretching,
which is mainly in the
meridian (longitudinal direction of the chamber) direction.
CA 02786315 2012-08-24
Fig. 203B shows the contact pressure. The piston 5" may jam at this
longitudinal position.
Fg. 204A shows the longitudinal cross-section of a p'eton 15 at tjie ceS9lld
7nngitudlAyLp~.tition
of a non-pressurized chamber 10, having a circular cross-section. The piston
15 may have a production
size approximately the diameter of the chamber 10 at this second longitudinal
position. Piston 15'*
shows the deformed piston 15 pressurized to a certain level. The deformation
is due to the fact that the
Young's modulus in the hoop direction (in a cross-sectional plane of the
chamber) is choosen lower than
that in the meridian direction (in the longitudinal direction of the chamber).
Fig. 204B shows the contact pressure on the wall of piston 15'*. This results
in an appropriate
friction force (4.2 kg), and suitable sealing
Fig. 204C shows the longitudinal cross-section of piston 15 at the second
longitudinal position
(production size) of the non-pressurized chamber 10, and when pressurized 15"*
at the first longitudinal
position - the piston 15"* may have the same pressure as when the piston 15'*
is positioned at the
second longitudinal position of the chamber 10 (fig. 4A). Also here is the
deformation in the hoop- and
meridian direction different.
Fig. 204D shows the contact pressure on the wall of piston 15"*. This results
in an appropriate
friction force (0.7 kg) and a suitable sealing.
Therefore, it is possible to sealingly move a piston comprising an elastically
deformable
container from a smaller to a bigger cross-sectional area while having the
same internal press re - within
the limitations for the diameters of the cross-sections which were chosen in
this experiment.
Fig. 205A shows the longitudinal cross-section of the piston 15 (production
size) and the piston
15' at the second longitudinal position of the non-pressurized chamber 10. The
piston 15'* is showing
the deformed structure of piston 15 when the piston 15 is pressurized. The
piston 15, 15'* have been
attached at the lower end to an imaginair piston rod in order to prevent
piston movement during
application of the chamber pressure.
Fig. 205B shows the contact pressure of the piston 15'* of Fig. 205A. This is
low enough to
allow movement (friction-force 4.2 kg) and suitable for sealing.
Fig. 205C shows the longitudinal cross-section of the piston 15 (production
size) and 15"*
pressurized and deformed by the chamber pressure at the second longitudnlal
position of the pressurized
chamber 10*. The piston 15, 15'* have been attached at the lower end to an
imaginair piston rod in
CA 02786315 2012-08-24
CA 02786315 2012-08-24
order to prevent piston movement during the application of the chamber
pressure. The deformed piston
15"* is approximately twice as long as the undeformed piston 15.
Fig. 205D shows the contact pressure of the piston 15 * of Fig. 205C. INS is
low enough to
allow movement (friction force 32 kg) and suitable for sealing-
Therefore, whenapplying a chamber pressure on a piston comprising a
pressurized elastically
deformable container, it is possible to sealingly move as well, at least at
the longitudinal position with
the smallest cross-sectional area. The stretching due to the applied chamber
force is big and it may be
necessary to limit this.
1 Figs. 206-209 deal with the limitation of the stretching of the slain of the
piston, which may
result in a contact area small enough to enable appropriate sealing and a
friction force low enough to
enable movement of the piston. This comprises a limitation of the stretching
in the longitudinal direction .
when the container may or may not be subjected to a pressure in the chamber,
and to allow expansion in
the transversal direction, when moving from the second to the first
longitudinal position of the chamber,
and specifically allow contraction when moving the other way around.
The stretching in the longitudinal direction of the wall of the container-type
piston may be
limited by several methods. It may be done by a reinforcement of the wall of
the container by using e.g.
textile and/or fiber reinforcement. It may also be done by an inside the
chamber of the container
positioned expanding body with a limitation for its expansion, while it is
connected to the wall of the
container. Other methods may be used, e.g- pressure management of a chamber in-
between two walls of
the container, pressure management of the space above the container etc. TThe
rciofereement may also
be positioned outside the piston. -
The expansion behaviour of the wall of the container may be depending on the
We of the
stretching limitation used. Moreover, the keeping of the piston which is
moving over the piston rod,
while expanding, may be guided by a mechanical stop. The positioning of such a
stop may be depending
on the me of the piston-chamber combination. This may also be the case for the
guidance of the
container over the piston rod, while expanding and/or sujected to external
forces.
All kinds of fluids may be used - a combination of a compressable and a
non.compressable
medium, a compressible medium only or a non-compressable medium only.
3k~
As the change of the size of the container may be substantial from the
smallest moss-sectional
area: where it bas its production size and expanded at the biggest moss-
sectional area. a communication
of the chamber in the container with a first enclosed space, e.g. in the
piston rod may be necessary- In
order to keep the pressure in the chamber, the first enclosed space may be
pressurized as well, also
during the change of the volume of the chamber of the container. Pressure
management for at leash the
first enclosed space may be needed.
Fig. 206A shows a longitudinal cross-section of the chamber 186 with a concave
wall 185 and
an inflatable piston comprising a container 208 at the first longitudinal
position in the chamber 186 and
the same 208' at the second longitudinal position in the chamber 186: The
central axis 184 of the
chamber 186. The container 208' shows its size, when pressurized, which is
approximately its
production size, having a textile reinforced 189 in the skin 188 of the wall
187. During the stroke
starting at the second longitudinal position of the chamber 186, the wall 187
of the container expands
until a stop arrangement, which may be the textile reinforcement 189 and/or a
mechaulcal stop 196
outside the container 208 and/or another stop arrangement stops the moveunent
during the stroke. And -
thus the expansion of the container 208. Depending on the pressure in the
chamber 186, there slit] may
occur a longitudinal stretching of the wall of the container, due to pressure
in the chamber 186. The first
main function however of the textile reinforcement is to limit this
Longitudinal stretching of the wall 187
of the container 208. It results in a small contact area 198. The second main
function of the textile
reinforcement 189 is to allow a contraction when the container is moving to
the second longitudinal
position (and vice versa where an expansion is necessary). During the stroke
the pressure inside the
container 208,208' may remain constant. This pressure depends on the change in
the volume of the
container 208,208', thus on the change in the eircumpherical length of the
cross-sections of the chamber
186 during the stroke. It may also be possible that the pressure changes
during the stroke- It may also be
possible that the pressure changes during the stroke, depending or not of the
pressure in the chamber
186.
Fig. 20681 shows a first embodiment of the expanded piston 208 at the fast
longitudinal position
of the chamber 186. The wall 187 of the container is build up by a skin 188.
of a flexable material,
which may be e.g. a rubber type or the like, with a textile reinforcement 189,
which allows expansion
and contraction. The direction of the textile reinforcement in relation to the
central axis 184 (= braid
CA 02786315 2012-08-24
angle) is different from 54 44'. The change of the size of the piston during
the stroke results not
_ssccccsmi1y in n identical chape_ ac deasm~_lhte, 3.o the 2pane nn the thin
nF fhr ll of the
container may be smaller than that of the container as produced when
positioned at the second
longitudinal position) of the chamber 186. An impervious layer 190 inside the
wall 187 may be present.
It is tightly squeezed in the cap 191 in the top and the cap 192 in the bottom
of the container 208,208'.
Details of said caps are not shown and all kinds of assembling methods may be
used - these may be
capable to adapt themselves to the changing thickness of the wall of the
container. Both caps 191,192
may be able to translate and/or rotate over the piston rod 195. These
movements may be done by
various devices as e.g. different types of bearings which are not shown. The
cap 191 in the top of the
to container may more upwards and downwards. The stop 196 on the piston rod
195 outside the container
208 limits the upwards movement of the container 208. The cap 192 in the
bottom may only move
downwards because the stop 197 prevent a movement upwards - this embodiment
may be thought to be
used in a piston chamber device which has pressure in chamber 186 beneath the
piston. Other
arrangements of stops may be possible in other pump types, such as double
working pumps, vacuum
pumps etc. and depends solely of the design specifications. Other arrangements
for enabling and/or
limiting the relative movement of the piston to the piston rod may occur. The
tmdng of the sealing force
may comprise a combination of an incompressible fluid 205 and a compressable
fluid 206 (both alone
are also a possibility) inside the container, while the chamber 209 of the
container may communicate
with a second chamber 210 comprising a spring-force operated piston 126 inside
the piston rod 195. The
fluid(s) may freely flow through the wall 207 of the piston rod through the
hole 201. It may be possible
that the second chamber is commtmicating with a third chamber (see Fig. 12),
while the pressure inside
the container also may he depending on the pressure in the chamber 186. The
container may be
inflatable through the piston rod 195 and/or by comtmmicating with the chamber
186. O-rings or the
lice 202, 203 in said cap in the top and in said cap in the bottom,
respectively seal the caps 191,192 to
the piston rod. The cap 204, shown as a screwed assembly at the end of the
piston rod 195 drighthens
said piston rod. Comparable stops may be positioned elsewhere on the piston
rod, depending on the
demanded movement of the wall of the container- The contact area 198 between
the wall of the
container and the wall of the chamber.
CA 02786315 2012-08-24
3g
Fig. 206C shows the piston of Fig. 206B at the second longitudinal position of
the chamber .
The -ca 191 in ffie to is moved over a distance a' from the sto 196. The -
force o erated valve
piston 126 has been moved over a distance b'. The bottom cap 192 is shown
adjacent to the stop 197 -
when there may be pressure in the chamber 186 below the piston, than the.
chamber 186' may be
pressed against the stop 197. The compressable fluid 206' and the non-
compressable fluid 205'-
Fig- 2061) is a 3-dimensional drawing and shows a reinforcement matrix of
textile material,
allowing elastically expansion and contraction of the wall of the container
208,208', when sealingly
moving in the chamber 186.
The textile material may be elastical, and laying in separate layers over each
other. The layers may also
lay woven in each other. The angle between the two layers may be different
from 54044'. When the
material type and thickness is the some for all layers, and the number of
layers even, while the stitch
sizes for each direction are equal, the expansion and contraction of the wall
of the container may be
equal in the XYZ-direction. When expanding the stitch ss and it, respectively
in each of the directions of
the matrix will become bigger, while contracting these wil become smaller. As
the material of the
threads may be elastical, another device may be necessary to stop the
expansion, such as a mechanical
stop. This may be the wall of the chamber and/or a mechanical stop shown on
the piston rod, as shown
in Fig. 206B.
Fig. 206E is a 3-dimensional drawing and shows the reinforcement matrix of
Fig. 206D which
has been expanded. The stitches ss' and tt' which are larger than the stitches
ss and tt. The result of the
contraction may result in the matrix shown in Fig. 2061).
Fig. 206F is a 3-dimensional drawing and shows a reinforcement matrix of
textile material
which may be made of inelastic thread (but elastically bendable), and lay in
separate layersover each
other or knitted in each other. The expansion is possible because of the extra
length of each loop 700,
which is available, when the container is in the production size - also
pressurized, when positioned at the
second longitudinal position of the chamber. Stitches ss" and tt" in each
direction. When the wall of the
container is expanding the inelastic material (but elastically bendable) may
limit the maximum expansion
of the wall 187 of the container 217. It may be necessary to stop the movement
of the container 217
over the piston rod 195 by e.g. stop 196, so that sealing may remain. The lack
of such a. stop 196 may
give the possibility of creating a valve.
CA 02786315 2012-08-24
3Hg
Fig. 206G is a3-dimensional drawing and shows the reinforcement matrix of Fig.
206F which
has been expanded. The stitches ss"' and st' which are larger than the
stitches so" and tt" The re ult
of the contraction may result in the matrix shown in Fig. 206F.
Fig. 206H shows three stages I, II and III of a production process of the
piston comprising an
elastically deformable container. Over a rod 400 is a rubber muncher 401
positioned, over which a
reinforced manchet 402 e.g. according to those of Fig. 406E-G is positioned.
Over the last mentioned
another rubber manchet has been positioned. Between the ratchet 401 and the
rod one or more caps 404
may be positioned- All may slide over the rod 400. The rod 400 may be hollow
and may be connected
to a high pressure steam source. Stage II: the pressurized steam may enter the
cave 408 of the oven 406
by outlets 405 which may be positioned at the end of the rod. A piece of the
complete rubber/rein
forcement manchets 407 may be cut and transported over the rod 400 into the
cave 408. The cave may
than he closed and pressurized steam is injected into the cave. Vulcanisation
may take place, incl. the
mounting of the wall of the container on the caps 404. The manchet may take
the form of the curve.
After vulcanisation the cave may be opened and the container which has than
its production size, is
pushed out (ID). In order to use the vulcanisation time of a piston to also
produce other pistons several
methods may be used. Bulging of the (complete: incl. textile reinforcement)
rubber manchets 407 may
take place before the vulcanisation. The rod 400 may than be updivided in
several parts, each
approximately the height of a container at its production size. Each may be
disconnected from the main
rod before entering a cave. And/or, several caves may be present at the end of
the production feed line,
which may each stand, receive a complete manchet 407 and vulcanize it. This
may be achived by the
caves rotating and/or translating to and from the end of die production feed
line. It may also be possible
that a number of vulcanisation caves are integrated in the production feed
line.
Fig. 207A shows a longitudinal cross-section of the chamber 186 with a concave
wall 185 and
an inflatable piston comprising a container 217 at the first longitudinal
position of the chamber and the
same 217' at the secondlongimdinal position. The container 217' shows,
pressurized, approximately its
production size-
Fig- 207B shows the expanded piston 217 at the first longitudinal position of
the chamber. The
wall 218 of die container is build up by a skin 216 of an clastical material,
which may be eg. a robber
type or the like, with a fiber reinforcement 219 according to the Trellis
Effect, which allows expansion
CA 02786315 2012-08-24
of the container wall 218. The direction of the fibers in relation to the
central axis 184 (= braid angle)
may be different from 54044'. The contact area 211 between the wall 218 of the
container 217 and the
wall 185 of the chamber 186. Due to the expansion the thickness of the wall of
the container may be
smaller, but not necessarily very different than that of the container as
produced when positioned at the
second longitudinal position- An impervious layer 190 inside the wall 187 may
be present. It may be
tightly squeezed in the cap 191 in the top and the cap 192 in the bottom of
the container 217,217'.
Details of said caps are not shown and all kinds of assembling methods may be
used - these may be
capable to adapt themselves to the changing thicltaess of the wall of the
container. Both caps 191,192
may translate and/or rotate over the piston rod 195. These movements may be
done by various methods
as e.g. different types of bearings which are not shown. The cap 191 in the
top may move upwards and
downwards until stop 214 limits this movement. The cap 192 in the bottom can
only move downwards
because the stop 197 prevent a movement upwards -'his embodiment is thought to
be used in a piston
chamber device which has pressure in chamber 186 beneath the piston. Other
arrangements of stops may
be possible in other pump types, such as double working pumps, vacuum pumps
etc. and depends solely
of the design specifications. Other arrangements for enabling and/or limiting
the relative movement of
the piston to the piston rod may occur
During the stroke the pressure inside the costumer 217,217' may remain
constant- It may also be
possible that the pressure changes during the stroke. The tuning of the
sealing force may comprise a
combination of an incompressabte fluid 205 and a compressable fluid 206 (both
alone are also a
possibility) inside the container, while the chamber 215 of the container
217,217' may communicate
with a second chamber 210 comprising a spring-force operated piston 126 inside
the piston rod 195. The
fluid(s) may freely flow through the wall 207 of the piston rod through the
hole 201. It may be possible
that the second chamber is communicating with a thud chamber (see Fig. 210),
while the pressure inside
the container also may be depending on the pressure in the chamber 186. The
container may be
inflatable through the piston rod 195 and/or by communicating with the chamber
186. 0-rings or the
like 202, 203 in said cap in the top and in said cap in the bottom,
respectively seal the caps 191,192 to
the piston rod. The cap 204, shown as a screwed assembly at the end of the
piston rod 195 thighthens
said piston rod.
CA 02786315 2012-08-24
psi
Fig. 207C shows the piston of Fig. 207B at the second longitudinal position of
the chamber
- 186. The contact area 211'. which is small. The can 191 is moved over a
distance e' from the stop 16.
The spring-force operated valve piston 126 has been moved over a distance d'.
The bottom cap 192 is
shown adjacent to the stop 197 - if there is pressure in the chamber 186, than
the 192 is pressed against
the stop 197. The conipressable fluid 206' and the non-compressable fluid 205'
which may have
changed volume in the container.
Figs. 208A,B,C deal with the construction of the piston which may be identical
with that of
Figs. 207A,D,C with the exception that the reinforcement comprises of any kind
of reinforcement means
which may be bendable, and which may ly in a pattern of reinforcement 'colums'
which do not cross
each other. This pattern may be one of parallel to the central axis 184 of the
chamber 186 or one of
where a part of the reinforcement means may be in a plane through the central
axis 184.
Fig. 208A shows an inflatable piston comprising a container 228 at the first
longitudinal
position of the chamber 186 and the same 228' at the .second longitudinal
position of the chamber 186 -
pressurized - where it has unpressurized its production size
Fig. 208B shows the container 228 at the first longitudinal position of the
chamber 186.
The wall 221 of the container comprises an elastical material 222,224 and the
reinforecement means 223
e.g. a fiber. An impervious layer 226 may he present. The contact area between
the container 228 and
the wall 185 of the chamber 186.
Fig. 208C shows the container 228' at the second longitudinal position of the
chamber 186.
The contact area 225' may be a bit larger than that of the contact area 225.
the top cap 191 has been
moving e' from the stop 214.
Fig. 208D shows a top view of the piston 228 and 228', respectively with the
reinfor-cement
means 223, and 223" respectively at the frost and second longitudinal position
of the clamber 186
respectively.
Fig. 208E shows a top view of a piston alike the one of 228 and 228';
respectively with an
alternative embodiment of the reinforcement means 229, and 229' respectively
at the first and second
longitudinal position of the.chamber 186 respectively. A pan of the
reinforcement does not ly in planes
through the central axis 184 in the longitudinal direction of the chamber 186.
Fig- 208F shows a top
CA 02786315 2012-08-24
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view of the piston alike the one of 228 and 228' with a reinforcement 227 and
227' in the wall in the
wall of the container in plates not through the central axis 184 of the
chamber T86. lhxinp the woke
the wall of the container turns around the central axis 184.
Fig. 208G shows schematically how fibers 802 may be mounted in caves 431 of
the cap 430.
This may be achieved by rotating the cap and the fibers around the central
axis 433, each may have its
own velocity, while the fibers 432 are being pushed towards and in the caves
431.
Fig. 209A shows a longitudinal cross-section of the chamber 186 with a convex
wall 185 and
an inflatable piston comprising a container 258 at the beginning and the same
258' at the end of a stroke.
The pressurized container 258' at the second longitudinal position.
Fig. 209B shows the longitudinal cross-section of the piston 258 having a.
reinforced skin by a
plurality of at least elastically deformable support members 254 rotatably
fastened to a common member
255, connected to the an skits 252 of said piston 258,258'. These members are
in tension, and depending
on the hardness of the material, they have a certain maximum stretching
length. This limited length
limits the stretching of the skin 252 of said piston. The common mernber 255
may slide with sliding
means 256 over the piston rod 195. For the rest is the construction comparable
with that of the piston
208,208'. The contact area 253.
Fig. 209C shows the longitudinal cross-section of the piston 258'. The contact
area 253'.
Figs. 210-212 des] with the management of the pressure within the container.
Pressure
management for the piston comprising an inflatable container with an
elastically deformable wall is an
important part of the piston-chamber construction. Pressure management has to
do with maintaining the
pressure in the container, in order to keep the sealing on the appropriate
level. This means during each
stroke where the volume of the container changes. And in the long term, when
leakage from the
container may reduce the pressure in the container, which may effect the
sealing capability. A flow of
fluid may be the solution. To and from the container when it changes volume
during a stroke, and/or to
the container as such (inflation).
The change in die volume of the container may be balanced with a change in the
volume of a
first enclosed space, communicating with the container through e.g. a hole in
the piston rod. The
pressure may at the same time also he balanced, and this may be done by a
spring force operated piston
which may be positioned in the first enclosed space. The spring force may be
originated by a spring or a
pressurized enclosed space, e.g. a second enclosed space, which communicates
with the lust enclosed
space by a pair of pistons. Any kind of force transfer may be arranged by each
of the pistons, e.g. by a
combination of the second enclosed space and a piston herein, so that theforce
on the piston in the first
.enclosed space rcmaines equal, while the force on the piston in the second
enclosed space reduces, when
the pair of pistons moves. towards the first enclosed space e.g. when fluid is
moving from the first
enclosed space into the container- This complies well with p.V = constant in
the second enclosed space.
The tuning of the pressure in the chamber of the container during the entire
or a part of the stroke may
also be done by a communication of the chamber and the chamber of the
container. This has already
been described in W000/65235 and WO00/70227.
The container may be inflated through a valve in the piston and/or the handle
of the piston rod.
This valve may be a check valve or an inflation valve, e.g. a Schrader valve.
The container may be
inflated through a valve which communicates with the chamber. If an inflation
valve is used, a Schrader
valve is preferable because of its security to avoid leakages and its ability
to allow to control all kinds of
fluids. In order to enable inflation, a valve actuator may be necessary, e.g.
the one disclosed in
W099/26002 or in US 5,094,263. The valve actuator of W099/26002 has the
advantage that inflation
may be enabled by a very low force - thus very practical in case of manual
inflation Moreover,
combined with a valve with a spring-force operated valve core, the valve
closes automatically when
equal pressure levels has been obtained.
If the flow of pressurized volume from the enclosed space to the container and
vice versa may be
substantial, it may be preferred to have a pressure/volume source with a
bigger volume than the volume
of the enclosed space and a pressure level which is equal, lower or higher
than the pressure in the
container In the last mentioned case the volume of the pressure source may be
reduced in comparison
with a pressure source with an equal pressure level of that of the container
In the case that the pressure level in the pressure source is higher of that
of the container it may be
necessary that during the stroke the flow between the pressure/volume source
and the container may be
steered by means of valves. These valves may have a springforce operated core
pm, which may be is
actuated. The actuators may open/close the valves of even contineously change
the flow. An example is
a analogeous construction used for inflating the container due to pressure
drop by leakage (please see the
next page). Other valve_types and valve steering solutions are possible. This
may also be a method of
CA 02786315 2012-08-24
CA 02786315 2012-08-24
~Sy
ctintiously maintani g the pressure level in the container at a predetermined
level. -
Having_a valve c "satin with the chamber it ma able matic inflation of the
container, when the pressure in the container is lower than the pressure in
the chamber- When this may
not be the case, such higher pressure in the chamber may be created
temporarily by closing the outlet
valve of the chamber near the second longitudinal position of the container in
the chamber. This closing
and opening may be done manually, e.g. by a pedal, which opens a channel which
communicates with a
space between the valve actuator (W099126002) and e.g. a Schrader valve. When
open, the valve
actuator may move, but lacks the force to depress the spring-force operated
core pin of the valve and
hence the Schrader valve may net open - thus the chamber may be closed, and
any high pressure may be
build up for enabling inflation of the container. When the channel is closed,
the actuator functions as
disclosed in W099126002. The operator may check the pressure in the container
by a pressure gangs,
e.g. a manometer" Opening and closing of this outlet valve may also be done
automatically. This may be
done by all kinds of means, which initiate the closing of the outlet by a
signal of any kind as a result of a
mezsnrement ofpressure being lower than a predetermined value.
The automatic inflation of the container to a certain pre-determined value may
be done by a
combination of a valve communicating with the chamber and e.g. a release valve
of the container. It
releases at a certain predetermined value of the pressure, e.g. to the space
above the container or to the
chamber- Another option may be that the valve actuator of W099/26002, may be
open firstly when a
pre-determined value of the pressure has been reached, c g. by combining it
with a spring. Another
option may be that the opening to the valve actuator is closed when the
pressure reaches a value over the
pre-determined one, by e.g. a spring force operated piston or cap. Or, by
combining the piston 292 of
Fig. 211E with means so that the piston opens the channel 297 when a certain
pressure has been reached
(not shown).
Fig 210A shows a piston-chamber system with a piston comprising a container
208,208' and a -
chamber 186 having a central axis 184 according to Fig. 206A-C. The inflation
and pressure
management described here may also be used for other pistons comprising a
container. The container
208,208' may be inflated through a valve 241 in the handle 240 and/or a valve
242 the piston rod 195. If
no handle is used, but e.g. a rotating axle, it could be hollow, communicating
with e.g. a Schrader
valve. The valve 241 may be an inflation valve, e.g. a Schrader valve,
comprising a bushing 244 and a
3rs"
valve core 245. The valve in the piston rod 195 may be a check valve, having a
flexible piston 126- The
chamber between the check valve 242 and the chamber 209 of the container
208,208- was earlier
described as the 'second' chamber 210. The manometer 250 enables control of
the pressure inside the
container - no further details are shown. It may also be possible to use this
manometer to control the
pressure in the chamber 186. It may also be possible that the chamber 209 of
the container 208,208' has
a release-valve (not drawn) which may be adjusted to a certain pre-determined
value of the pressure.
The released fluid may be directed to the chamber 209 andlor to the space 251.
Fig. 210B shows an alternative option for the inflation valve 241. Instead of
the inflation valve
241 in the handle 240, only a bushing 244 without a valve core 245 may he
present, which enables
connection to a pressure source. -
Fig. 210C shows details of the bearing 246 of the rod 247 of the check valve
126. The bearing
226 comprises longitudinal ducts 249 enabling passage of fluid around the rod
247. The spring 248
enables a pressure on the fluid in the second chamber 210. The stop 249.
Fig. Z10D shows details of the flexible piston 126 of the check valve 242. The
spring 248
keeps the pressure on the piston 126.
Fig. 210E shows the pressure source 451 which may have a pressure which
exceeds the
pressure level of the container. Inlet valve 452 with e.g. a valve actuator
453 (the configuration 459
shown is analogeous to the one of Fig. 211E (292,297)), and outlet valve 454
with e.g. a valve acmator
455 (the configuration 451 shown is analogeous to the one of Fig. 211E
(292,297)). The space 460 is
connected to the chamber 457, while the space 462 is connected to the chamber
458. The valves 452 and
454 may be mounted in the piston rod 456, which may be updivided in two
chambers 457 and 458.
Fig 210F shows the construction of Fig. 210E where two black boxes are shown
comprising
each a valve arrangement which may be ateemble by external signals. The
steering 415 may receive
pressure signal 416 grid X417, respectively from the inside of the piston at
different longimdinal positions
of the chamber. The steering 415 may send signals 418 and 419, respectively to
the acmator 422 of the
outlet valve arrangement 420 and to the actuator 423 of the inlet valve
arrangenment 421. This valve
and valve steering arrangement may he analogeously to the one shown in
Fig.211F.
Fig. 211A shows a piston-chamber system with a piston comprising a container
248,248' of
which the central part is identical with container 208,208' and a chamber 186
having a central axis 184
CA 02786315 2012-08-24
~Sb
1
CA 02786315 2012-08-24
according to Fig. 206A-C. The inflation and pressure management described here
may also be used for
ether pistons comprising a container. The container 248,248' may be inflated
through a valve
communicating with the chamber 186. This valve may be a check valve 242
according to Fig. 210A,D
or it may be an inflation valve, preferably a Schrader valve 260 The fist
enclosed space 210 is
communicating with the chamber 209 in the container by a hole 201, while the
first enclosed space 210
is communicating through a piston arrangement with a second enclosed space
243, which may be
inflated through e.g. an inflation valve like a Schrader valve 241 which may
positioned in the handle
240. The valve has a core pin 245. If no handle is used, but e.g. a rotating
axle, it may be hollow and a
Schrader valve may communicate with this channel (not drawn). The- Schrader
valve 260 has a valve
actuator 261 according to W099/26002. The foot 262 of the chamber 186 may have
an outlet valve 263,
e.g. a Schrader valve, which may be equipped with another valve actuator 261
according to
W099126002. In order to manually control the outlet valve 263, the foot 262
may be equipped with a
pedal 265 which can turn an angle around an axle 264 on the foot 262. The
pedal 265 is connected to a
piston rod 267 by an axle 266 in a non-circular hole 275 in the top of the
pedal 265. The foot 262 has an
inlet valve 269 (not drawn) for the chamber 186. The (schematically drawn)
spring 276 keeps the pedal
265 in its initial position 277, where the outlet valve is kept open. The
activated position 277' of the
pedal 265 when the outlet valve is kept elosed. The cruder channel 268.
Fig. 211B shows a detail of the communication by a pair of pistons 242,270
between the first
enclosed space 210 and the second enclosed space 243. The piston rod 271 of
the pair of pistons is
guided by a bearing 246. The longitudinal ducts 249 in the bearing 246 enable
the transport of fluid
from the spaces between the bearing 246 and the pistons 242 and 270. The
spring 248 may be present.
The piston rod 195 of the piston type container 248,248' with internal wall
194. Pistons 242,270 seal on
internal wall 194.
Fig. 2110 shows an alternative wall 273 of the piston rod 272 of the piston
type container
248,248' which has a angle with the central axis 184 of the chamber 186. The
piston 274 is
schematically drawn, and can adapt itself to the changing cross-sectional
area's of the inside the piston
rod 272.
Fig. 211D shows piston 248' on which a housing 280 is build. The housing
comprises a
Schrader valve 260, with a core pin 245. The valve actuator 261 shown as
depressing the core pin 261,
3rj
while fluid may enter the valve 260 through channels 286, 287, 288 and 289.
When the core pin 245 is
not depressed the piston tine 279 may sea] the wall 285 of the inner cylinder
283. The inner cylinder
283 may be sealingly enclosed by scaling 281 and 284 between the housing 280
and the cylinder 282.
The chamber 186.
Fig. 211E shows the construction of the outlet valve 263 with a cote pin 245,
which is shown
depressedby the valve actuator 261. Fluid may flow through channels 304, 305,
306 and 307 to the
apenened valve. The inter cylinder 302 is sealingly enclosed between the
housing 301 and the cylinder
303 by sealings 281 and 284. A channel 297 having a central axis 296 is
positioned through the wall of
the inner cylinder 302, the wall of the cylinder 303 and the wall of the
housing 301. At the outside of
to the housing 301 has the opening 308 of channel 297 a widening 309 which
enables a piston 292 to seal
in a dosing position 292' by a top 294. The piston 292 may be moving in
another channel 295 which
may have the same central axis 296 as channel 297. The bearing 293 for the
piston rod 267 of the piston
292. The piston rod 267 may he connected to the pedal 265 (Fig. 211A) or to
other actuators
(schematically shown in Fig. 211E).
Fig. 211E shows the piston 249' and the inflation arrangement 368 of Fig_
2111), besides the
arrangement 369 to control the outlet valve of Fig. 211E. The inflation
arrangement 368 comprises now
also the arrangement 370 to control the valve of Fig. 211E. This may be done
to enabling the closing of
the valve, when the predetermined pressure has been reached, and opening it
when the pressure is lower
than the predetermined value- A signal 360 is handled in a converter 361 which
gives a signal 362 to an
actuator 363, which is actuating through actuating means 364 the piston 292.
When the chamber has a lower working pressure than the pre-determuned value of
the pressure
in the piston, the arrangement 369 to control the closing and opening of the
outlet valve 263 may be
controlled by another actuator 363 through means 367 initiated by a signal 365
from the converter 361.
A measurement in the chamber, giving a signal 371 to the converter 361 and/or
366 may automatically
detect whether or not the actual pressure of the chamber is lower than the
working pressure of the
piston. This may be specifically practical when the pressure of the piston is
lower than the pre-
determined pressure. -
Fig. 211G shows schematically a cap 312, 312' with a spring 310 connected to
the housing 311
of a valve actuator 315. The spring 310 may keep the opening 314 tig0ily
closed. The contact area 313
CA 02786315 2012-08-24
3s$
of the cap 312 with the cylinder 282 (fig. 211D). When the force on the cap
312 from the chamber
becomes bigger, the ca~i may move to a position where the cav 312' is shown
until there is equivalence
of the forces on the cap by the medium/media of the chamber. The spring 310
may determine the
maximum value of the pressure to depress the valve core pin 245. A Schrader
valve 260.
Fig. 212 shows en enlonged piston rod 320 in which a pair of pistons 321,322
are positioned at
the end of a piston rod 323, which may move in a bearing 324.
Figs. 213A,B,C show the combination of a pump with a pressurizing chamber with
elastically
deformable wall with different areas of the transversal cross sections and a
piston with a -fixed
geometrical shape. Within a housing as e.g. cylinder with fixed geometrical
sizes an infatablt chamber
is positioned which is inflatable by a fluid (a non-compressable and/or a
compressible fluid). It is also
possible that said housing may be avoided. The inflatable wall comprising e.g.
a liner-fiber-cover
composite or also added an impervious skin. The angle of the sealing surface
of the piston is a bit bigger
than the comparative angle of the wall of the chamber in relation to an axis
parallel to the movement.
This difference between said angles and the fact that the momentaneous
deformations of the wall by the
piston takes place a bit: delayed (by having e.g. a viscose noncompressable
fluid in die wall of the
chamber and/or the right tuning of load regulating means, which may be similar
to those which have
been shown for the pistons) provides a scaling edge, of which its distance to
the central axis of the
chamber during the movement between two piston and/or chamber positions may
vary. This provides a
cross-sectional area change during a stroke, and by that, a designable
operation force. The cross-section
of the piston in the direction of the movement however may also be equal, or
with a negative angle in
relation to the angle of the well of the chamber - in these cases the 'nose'
of the piston may be rounded
of. In die last mentioned cases it may be more difficult to provide a changing
cross-sectional area, and
by that, a designable operation force. The wall of the chamber may be equiped
with all the already
shown loading regulating means the one showed on Fig-. 212B, and if necessary
with the shape
regulating means. The velocity of the piston in the chamber may have an effect
on the sealing.
Fig. 213A shows piston 230 at four positions of the piston in a chamber 231.
Around an inflatable wall a housing 234 with fixed geometrical sizes. Within
said wall 234 a
compressable fluid 232 and a non-compressable fluid 233. There may be a valve
arrangement for
CA 02786315 2012-08-24
CA 02786315 2012-08-2435-9
inflation of the wall (not shown). The shape of the piston at the non-
pressurized side is only an example
to show. the _ nncinle_f th sealing The dicianrP h iween the - lingxdge ar the
endsnd at the
begimting of the stroke in the shown transversal cross-section is
approximately 39%_ The shape of the
longiudiual cross-section may be diferent from the one shown
Fig. 2135 shows the piston after the beginning of a sn-eke. The distance from
the sealing edge
235 and the central axis 236 is zr The angle between the piston scaling edge
235 and the central axis
236 of the chamber. The angle v between the wall of the chamber and the
central axis 236. The angle v
is shown smaller than the angle - The sealing edge 235 arranges that the angle
v becomes as big as the
angle - Other embodiments of the piston are not shown.
Fig. 213C shows the piston during a stroke. The distance from the sealing edge
235 and the
central axis 236 is zi - this distance is smaller than z,.
Fig. 213D shows the piston almost at the end of stroke. The distance from the
sealing edge 235
and the central axis 236 is zr - this distance is smaller than zr-
Fig. 214 shows a combination of a wall of the chamber and the piston which
have
2-28 changeable geometrical shapes, which adapt to each other during the pump
stroke, enabling a
continuous sealing. It has its production size at the second longitudinal
position of the chamber.
Shown is the chamber of Fig- 213A now with only a non-compressable medium 237
and piston 385 at
the beginning of a stroke, while the piston 385' is shown just before the end
of a stroke. Also all other
embodiments of the piston which may change dimensions may be used here too.
The right choice of
velocity of the piston and the viscosity of the medium 237 may have a positive
effect on operations. The
longitudinal cross-sectional shape of the chamber shown in Fig. 14 may also be
different.
Figs. 215A-F show embodiments of the chamber with cross-sections of different
sizes which
have constant circumpherential sizes. This is another solution for the jamming
problem of the cited
pistons of WO 00/70227. The pistons according to claim 1 may also function
well in these specific
chambers, when the reinforcement of the. skin allows pans of the wall of
thecontainer having different
distances from the central axis of the chamber in a longitudinal cross-section
of the chamber may also be
used: e.g. the position of the reinforcement of e.g. Fig. 208D approximately
paralell with the central
axis of the chamber, and when the reinforcement is made of e.g. elastical
threads (Figs. 206D, 206E),
or those shown in Figs. 206F, 206G allowing each an individual size. The one
showed in Figs. 209A,
CA 02786315 2012-08-24
209B may also function well. Pistons comprising non-elastically deformable
containers or elastically
deforaiable containers with a production size approximately the size of the
circumpherencial length of
the first longitudinal position of the chamber, having a reinforcement which
allow contraction with high
frictional forces may move in sorb chambers without jamming, anti may jam in
chambers where the
cross-sections have different circumpherencial sizes. If the braid angle of
the reinforcement of a
container may becorne.5444' the otherwise elastically deformable container
becomes non-elastical
deformable, that is to say flexible deformahle, but it will not jam in these
chambers, as it may be bent. If
the change of the area of a transversal cross-section of the piston and/or the
chamber between two
positions in the direction of movement is continuous but still so big that
this results in leakages, it is
advantageous to immunize the change of the other parameters of the cross-
section This can be illustrated
by using e.g. a circular cross-section (fixed shape): the circumference of a
circle is D, while the area of
a circle is ki D' (D = diameter of the circle). That is to say, a reduction of
D will only give a linear
reduction of the circumference and a quadratic reduction of the area. It is
even possible to also maintain
the circumference and only reduce the area. If also the shape is fixed e.g. of
a circle there. is a certain
minimum area. Advanced numeric calculations where the shape is a parameter can
be made by using the
below mentioned Fourier Series expansions. The transversal cross-section of
the pressurizing chamber
and/or the piston can have any form, and this can be defined by at least one
curve. The curve is closed
and can approximately be defined by two unique modular parametrisation Fourier
Series expansions,
one for each co-ordinate function
f (x )= z +~co cos (px)+>do no (px)
where
~G)
ct,J f(x)cos(px)dx
de. 2J f(x)si(p4dr
0<x12tr, xc
p>0.pn
C, = cos-weighted average values of f(x),
d = sin-weighted average values off(e),
p = representing the order of trigonometricalfineness
Figs. 215A, 215E show examples of said curves by using a set of different
parameters in the
following formulas In these examples only two parameters have been used. If
more coefficients are
used, it is possible to find optimized curves which comply to other important
demands as e.g. curved
transitions of which the curves have a centaur maximum radii and/or e.g. a
maximum for the tension in
the sealing portion which under given premisses may not exceed a certain
maximum: As an example:
Fig. 215F shows optimized convex curves and nomconvex curves to be used for
possible deformations
of a bounded domain in ,a plane under the constraints that the length of the
boundary curve is fixed, and
its numerical curvature is minimized. By using a starting area, and a starting
boundary-length it is
possible to count on a smallest possible curvature for a certain desired
target area.
The pistons shown in a longitudinal cross-section of the chamber have been
drawn mainly for
the case that the boundary curve of the transversal cross-section is circular.
That is to say: in the case
that the chamber has tra sversal cross-sections according to e.g. those non-
circular of Figures 215A,
215E, 215F the shape of the longitudinal cross-section of the pistons may be
different.
All kinds of closed curves can be described with this formula, e.g. a C-c rve
(see
PCT/DK97/00223,Fig- IA). One characteristic of these curves is that when a
line is drawn from the
mathematical pole which lies in the section plane it will intersect the curve
at least one time. The curves
are symmetrical towards a line in the section plane, and could also have been
generated by the single
- Fourier Series expansion which follow. A piston or chamber will be more easy
to produce when the
CA 02786315 2012-08-24
CA 02786315 2012-08-24
,6t
curve of the transversal cross-section is symmetric with reference to aline
which lies in the section plane
f niglithr atliciii Cal_pnle S ~rh re~tlar n~rvrs_ran_allpTnximatrN
j>~define~b~' d Sin le.~'rnmer_
Series expansion:
f(x)= 2+~cecos (px)
where
ra = 2 J~ f (x) cos(x) dr
0<x<2rz, xe11""~~/N
p>O. PE FI\
c, = weighted average values off(x),
p = representing the order of trigonometricalfineness.
When a line is drawn from the mathematical pole it will always intersect the
carve only one time.
Specific formed sectors of the cross-section of the churches' ardor the piston
can approximately be
defined by the following formula:
P x )- 2+~ee cos (3pv)
where
CA 02786315 2012-08-24
v=6 rf(x)cos(3px)dx
a rz
O<x<_2>c, e IN
p>O.pe
c, = weighted average values off(x),
p = representing the order of tngonometrical fineness
and where this cross-section in polar co-ordinates approximately is
represented by the following
formula:
where
ro>
a>0
m?O,me ,
2o,ne
05(052
and where -
I = the limit of the "petals" in the circular cross section of the activating
pin,
ra = the radius of the circular cross section Ground the axis of the
activating pin,
a = the scale factor for the length of the petals
r. = ro+a -
m = the parameterfor definition of the petal" width
n = the parameterfor definition of the number of "petals"
36q
the angle which bounds the curve.
The inlet is-positioned close to the end of the stroke due to the nature of
the sealing
portion of the piston means.
These specific chambers may be produced by injection moulding, and e.g.. also
by the
use of so-called superplastic forming methods, where aluminium sheets are
heated and pressed by air
pressure either forced in a tool cavity or formed using also tool movement:
Fig. 215A shows a series of transversal cross-sections of a chamber where the
area
decreases in certain steps, while the circumference remains constant - these
are defined by two unique
modular pararnetrisation Fourier Series expansions, one for each co-ordinate
function. At the top left is
the cross-section which is the start cross-section of said series. The set of
parameters used is shown at
the bottom of the figure. This series show decreasing area's of the
transversal cross-section. The
numbers in bold in the figures show the decreasing cross-sectional area's of
the different shapes, with
the one in the co- leff up as the starting area size.
The area of the shape of the cross-section bottom, right is approximately 28 %
of the one of the top, left.
Fig. 215B shows a longitudinal cross-section of the chamber 162, of which the
transversal cross-sectional area changes by remaining circumference along the
central axis.
The piston 163. The chamber has portions of different cross-sectional area's
of its transversal cress-
section of wall sections 155,156,157,158. The transitions 159,160,161 between
said wall sections.
Shown are cross-sections G-G, H-B and I-I. Cross-section G-G has a circelround
cross-section, while
cross-section H-H 152 has approximately an area between 90-70% of the one of
cross-section G-G.
Fig. 215C shows transversal cross-section H-H 152 of Fig. 207G and in dotted
lines as a
comparison cross-section G-G 150. Cross-section H-H has approximately an area
between 90-70% of
that of cross-section G-G. The transition 151, which is made smooth. Also
shown is the smallest part of
the chamber, which has approximately 50% of the cross-sectional area of cross-
section G-G.
Fig. 215D shows a transversal cross-section I-I of Fig. 207G and in dotted
lines as a
comparison cross-section G-G. The cross-section I-I has approximately an area
of 70% of that of cross-
section G-G. The transition 153 is made smooth Also shown is the, smallest
part of the chamber.
CA 02786315 2012-08-24
CA 02786315 2012-08-24
3 G`j
Fig. 215E shows a series of transversal cross-sections of a chamber where the
area
in_ceuain_stepc whir the m{ renre rrm Marv -these am~5ned.=b twn t rpie
modular parametrisation Fourier Series expansions, one for each co-ordinate
function. At the top left is
the cross-section which is the start cross-section of said series- The set of
parameters used is shown at
the bottom of the figure. This series show decreasing area's of the
transversal cross-section, but it is also
possible to increase these areas by remaining the circumference constant. The
numbers in bold in the
figures show the decreasing cross-sectional area's of the different shapes,
with the one in the comer left
up as the starting area size. The size of the cross-sectional area bottom
right is approximately 49% of the
starting area size left, top.
Fig. 215F shows a convex curve optimized for a certain fixed length of the
boundary
curve, and a smallest possible curvature. The general formula for the smallest
radius of curvature,
corresponding to the largest curvaure of the figure shown in Fig. 7L is:
r=Jx(L- IL - (411 Ad
The length specified by y is determined by:
Y 2 '-4.A,
where
smallest mdiur of curvature
L = boundary-length = constant
A, = decreased value of the stoning domain area Aa
As an example from Fig: 203D: Domain area Av = (30)s and boundary length L =
60 = 188.5
corresponding to the area and boundary lengdt of a disk of radius 30. The
length is required to be
constant, but the area is decreased to the value A, to be specified. The
desired final configuration should
have the area A, _ (19/2)' = 283.5. The convex curve with the smallest
possible curvature of the
boundary curve is now:
r=1.54
=1/r=065
x = 89.4
The curve on the Figure is not on scale and the Figure shows only the
principle.
The curve may further be optimized by exchanging the straight lines by curves
which may improve the
sealing of the piston to the wall.
Fig. 216, shows a combination where the piston comprising an elastically
defomiable
container 372 which is moving in a chamber 375 within a cylinder wall 374 and
a taper wall 373 e.g.
shown her in the centre around the central axis 370. The piston is banged up
in at least one piston rod
371. The container 372,372' is shown at the second longitudinal position of
said chamber (372') and at
the fast longitudinal position (372).
All solutions disclosed in this document may also be combined with piston
types for
which the chambers having cross-sections with constant circumpherential sizes
may be die solution for
the problem ofjamming.
Fig. 217A shows a convex chamber 380 witin a wall 381. "s" meuss stroke.
Fig. 237B shows the ForceStroke diagram in the direction shown in Fig. 217A.
This curve shows the optimized change of the force when an operator is pumping
in strokes where die
intake of fluid lies approximately at the fast longitudinal position of the
chamber and the outlet is
approx. at the second longitudinal position of the chamber. The curve tangents
the maximum operating
force approximately at the end of the pumping stroke.
Fig. 218A shows an example of a Movable Power Unit 390, shown movable by
parachute 391, and by wheels 392.
Fig. 218B shows the Movable Power Unit 390, with a power unit comprising a set
of
solar cells 393 on top and a motor 394. Moreover a water pump 395, and a
compressor 396. The
-steering unit 397_
CA 02786315 2012-08-24
3 6~
507 DESCRIP"1TON OF PREFERRED ENIBODIhoIFNTS
Figure 301 shows a valve actuator in a clio-on valve connector to be cpog led
to e.¾_ a Sehrader valve.
The piston 477 is very near the first end 492 of the cylinder 470. The
connector has a housing 500 and
the sealing means comprises one annular portion 475. The securing means
comprises temporary thread
476. The housing also has a center axis 479 and a coupling section 510.
Figure 301A shows an enlarged detail of Figure 301. The cylinder 470 has a
cylinder wall
portion 511 with a diameter which fits the piston ring 508 of the piston 477.
Near its first end 492, the
cylinder wall comprises enlargement wall portions 475a,475b,476a with an
enlarged diameter,
comprising flow channel portions 471,472,473 around the piston means 477,508
when the activating pin
has enough opened the core of the valve. The flow from the pressure source to
the valve can now be
established. The fast end 492 of the cylinder 470 functions here as a stop for
the movement of the
activating pin. The channel portions 473 and 474 are parts of the piston
control means 476c. These parts
can have several shapes which depend on the chosen production technique: e.g.,
channel portions
473,474 as sector parts of a circle and (507) as cylinders made by injection
moulding, while
alternatively channel portions (507) could also be drilled holes. Channel
portions 473,474 could be
considered 'flow shaped', and are constructed to reduce aerodynamic drag. She
inclined enlargement
wall portion 475a has an angle with the center axis 479, which is larger than
0 and smaller than 20 ,
normally in the interval 1 < < 12 with respect to the direction of the
gaseous and/or liquid medium
or media, respectively coming from the pressure source. The piston control
means 476c has three
grooves with walls 476a and 476b, respectively- The wall 476a has an angle
which is larger than 0 -
and smaller than 200 (usually in the interval between 60 and 12 ) with respect
to the direction of the
gaseous and/or liquid medium or media coming from the pressure source. The
alternative for the
forementioned channel portions 473 and 474 are channels (507) where the piston
control has no grooves.
In this alternative, a hole (507) parallel to the center axis 479 and beside
the piston control connects
channel portion 475b (shown as dree holes with dotted lines) and the coupling
hole.
Figure 301B shows section G-G from Figure 301A, with the channel portions 473
and 474 -
and the stopper 492. The alternative channel portion (507) is sketched by
dotted lines.
Figure 302 shows a valve actuator in a universal clip-on valve connector with
the housing
504 and with a sealing means comprising a first annular portion 482 and a
second annular sealing
CA 02786315 2012-08-24
36(Y
portion 483 situated coaxially with the center axis 486 of the coupling
section, in the direction of the
center axis 486 of the e Q section 501 The fnst -- -portion, 482 is closer to
the opening
502 of the coupling section than the second annular sealing portion 483, and
the diameter of the first
annular sealing portion 482 is larger than the diameter of the second annular
sealing portion 483. The
coupled valves can be secured by at least one 'clip' (= i.e. temporary thread)
476. However, two clips
493 opposite each other are preferable. A taper cone 501 near the sealing
surface 482 helps center the
valve. The taper cone has an angle with the center axis 486, and normally this
angle is > 45 . A
scperate cylinder sleeve 496 with cylinder wall portion 509 is shown which is
sealed. It is fastened by
for example a snap-lock 497 in the wall of the housing 504. This is an
economical way of making the
to negative slip angle of the inclined enlargement wall portion 512 possible.
The cylinder sleeve 496 has
distant from the piston stop 495 an angle , so that the piston ring 508 is non-
sealing there.
Figure 302A shows the channel portions 480 and 481 respectively defined by the
enlargement wall portions 487 and 488 of the piston contact means,
respectively. The activating pin is
streamlined with the piston 484 and the piston rod 485. The wall portion 487
has an angle with the
center axis 486 seen in the direction of the medium coming from the pressure
source, which is larger
than 0 and smaller than 20 (usually in the interval between 6 and 12 ) The
stepped surface 498 of
wall of housing 504 makes an air tight connection from the wall of the
cylinder sleeve 496 to the
cylinder 499. It is of course also possible to make the air tight connection
on the other side of the
cylinder. In the bottom of the cylinder sleeve 496,is the inclined enlargement
wall portion 512 shown
which together with the piston ring 515 forms channel portion 471.
Figure 302B shows section H-H of Figure 302A and the stopper 495 for the
movement of
the activating pin. Also shown is the wall portion 488 and the channel
portion481-
Figure 303 shows an activating pin which is comparable of the one from Figure
301. The
piston 529 is also shown. The piston rod 531 need not to be sealed against the
piston control.
The cylinder 536 of the valve actuator is within housing 532 of the valve
connector.
The coupling section 530 is also shown.
Figure 303A shows a charnel portion 533 with an expansion 535 and a channel
portion
534 formed as a radial drilling 534 The piston ring 539 opens and closes this
conducting channel at its
orifice 537, depending on the position of the activating pin. The direction of
the channel portion 534 in
CA 02786315 2012-08-24
CA 02786315 2012-08-24
3C
relation to the center axis is comparable with the angle of channel portion
471 of Fig- 301A. The wall
of expansion 535 has an angle comparable to angle of the wall 476a -Fig. IA.
Also shown is the
cylinder wall portion 538 of the cylinder 536.
Figure 304 shows an activating pin and its cylinder, which was shown in Figure
301. This
is built in an assembled pipeline housing means 520,521 or the like, in which
a valve 522 with a spring-
force operated core pin 523 is situated, e.g_ a Schrader valve. The activating
pin is engaging with the
core pin 523 of the valve.
Figure 305 shows a valve actuator in a universal valve connector. It is
comparable with the
one of Figure 301. However, two sealing means 540, 541 with an in-between
distance A can seal two
valves of different sizes. Two enlargements I and 2 of the diameter of the
cylinder 542 in the cylinder
wall 550 are shown, with the in-between distance B. An activating pin 543 is
also shown, with two
engaging levels on a distance B. 'Ihe in-between distances can be equal or
different if for example the
valves are of a different type, so that the distance from the co- pin to the
sealing is not the same.
Between the two enlargements 1 and 2 is a cylindrical wall portion 544, with
cylinder portion 545,
which fits the piston ring 508. Also is shown the center axis 546, the
coupling section 547 and its
opening 549 from the housing 549.
3~o
CA 02786315 2012-08-24
19597 DESCRIPTION OF PREFERRED EMBODIMENTS
Fig. 401A shows line XX between two of the three engaging surfaces 1,2 of the
basis 4 with a
rigid surface 5, around which the combination 6 may move. The line Y-Y between
two of the three
engaging surfaces 2,3 of the basis 4 with a rigid surface 5, around which the
combination 6 may move.
The line Z-Z between two of the three contact points 1,2 of the basis 4 with a
rigid surface 5, around which
the combination 6 may move.
Fig. 401B shows the combination 6, comprising a chamber 7, a guiding 8 for the
piston and 9, a
handle to. The basis 4 with contact points 1, 2 and 3, which are rounded off
towards the rigid surface. The
chamber 7 is rigidly connected to the basis 4 by means of reinforcement 11.
Fig. 402A shows the handle 10 of the combination 6 when the combination 6 is
in
its rest position 12.
Fig. 402B shows the combination 6 in its rest position 12, when the transition
13 between the
combination 6 and the reinforcement 14 of the basis 40 is in its rest
position. The transition 13 may be
made of a flexible material, and is positioned around the chamber 7.
Fig. 402C shows the activated position 14 of the handle 10, when the handle 10
has been
moved from its rest position 12 at the front side of the said rest position.
Fig. 402D shows the activated position 15 of the handle 10, when the handle
has been moved
from its rest position 12 at the back side of the said rest position.
Fig. 402E shows the activated position 16 of the handle 10, when the handle
has been moved
from its rest position 12 at the left front side of the said rest position.
Fig. 402F shows the activated position 17 of the handle 10, when the handle
has been moved
from its rest position 12 at the left back side of the said rest position.
Fig. 402G shows the activated position 18 of the handle 10, when the handle
has been moved
from its rest position 12 at the right front side of the said rest position.
Fig. 402H shows the activated position 19 of the handle 10, when the handle
has been moved
from its rest position 12 at the right back side of the said rest position.
Fig. 403A shows a floor pump where the transtion between the chamber 7 and the
basis 4 is an
elastically deformable bushing 20.
Fig. 403B shows an enlargement of the transition between the chamber 7 and the
basis 40. The
chamber 7 has a protrusion 21 which complies with a groove 22 in the bashing
20, enabling a simple
mounting of the chamber 7 in the base 40. The protrusion 41 on top of the
reinfoircement 42 of the
CA 02786315 2012-08-24
basis 40.
Fig. 403C shows a floor pump where the transition between the chamber 7 and
the basis 4 is an
elastically deformable bushing 23.
Fig. 403D shows an enlargement of the transition between the chamber 7 and the
40. The
chamber 7 has a groove 25 which complies with a protrusion 24 in the bushing
23, enabling a simple
mounting of the chamber 7 in the basis 40.
Fig. 404A shows the combination 6 in the form of a floor pump with a cab 25
which allows a
transversal translation and/or deflection of the piston rod in relation to the
rest of the combination 6 and
the basis 43. The basis 43 may be directly, by means of the reinforcement 42,
or indirectly e.g. by
means of a flexible bushing be connected to the basis 41.
Fig. 404B shows an enhugment of the cap 25 of Fig. 404A, when the piston 44 is
at the end of
a stroke farthest from the basis 43. The piston rod 9 is moving in a guiding
means 26, of which the
convex contact inner surface 31 is in line contact at its centre line 27 with
the piston rod 9. The guiding
means 26 is being held within the cap 9 by surfaces 36 and 37, and by a
flexible O-ring 28. The cross-
sectional area of the space 29 between surfaces 36 and 37 of the cap 9 and the
guiding means 26 is
shown bigger than the cross-sectional area of the ring 28 itself, so as to
make a substantial compression
of the ring 28 possible (see e.g. Fig. 404C). the distance a between the
outside of the piston rod 9 and
the wall 38 of the spaces 33 and 34 of the cab 9. Said distance a may be
approximately the same
distance b between the piston rod and the wall 38 of the cab 9 in the top of
the cab.
Fig. 404C shows Fig. 4B where the centre axis 32 of the piston rod 9' is
deflectedangle am
relation to the centre axis 30 of the rest of the combination. The space 29'
is almost being filled up by
the compressed ring 28', which is compressed by the translated guiding means
26'. The space 34'. The
space 33'. The contact surface 35 between the guiding means 26' and the piston
rod 9'. Distance a' is
smaller than distance a of Fig. 404B.
Distance b' is smaller than ditance b of Fig. 404B, and more than the
diufference between distances a
and a'.
Fig. 404D shows an enlargement of the cap 25 of Fig. 404A, when the piston 44
may be at the
end of a stroke closest to the basis 43. The centre line 30 of the
combination. The spaces 33 and 34
between the inner walls 38 of the cab 25 and the piston rod 9.
Fig. 404E shows Fig. 404D when the piston rod 9' is translated to tch left, to
a distances"
between the outside of the piston rod 9' abd the inner wall 38 of the cab 25.
The guiding means 26" is
4 "-
CA 02786315 2012-08-24
moved to the left, compressing the ring 28" - shown is that the space 29" has
been filled up in this
cross-section by the compressed ring 28". The space33" is approximately equal
the space 34" with a
distance a" which is equal distance b" which is smaller than distance a.
Fig. 405A shows the left portion 51 of the handle 52 and the right portion 53
of the handle 52, in
relation to the centre axis 54 of the combination 55. The angle a between the
centre axis 56 of the left
portion 51 of the handle 52 and the centre axis 57 of the right portion 53 of
the handle 52 is less than 180,
when viewing from the position X of the user. The center point 61 of the left
portion 51 and center point
62 of right portion 53.
Fig. 405B shows the a front view of the floor pump of Fig. 5A, comprising the
handle 52 and the
combination 55. Handle 52 with the left 51 portion and the right 53 portion.
The centre axis 54 of the
combination 55.
Fig. 406A shows the left portion 58 of the handle 59 and the right portion 60
of the handle 59, in
relation to the centre axis 54 of the combination 55. The angle (t between the
centre axis 56 of the left
portion 58 of the handle 59 and the centre axis 61 of the right portion 60 of
the handle 59 is more than
1800, when viewing from the position X of the user.
Fig. 406B shows the a front view of the floor pump of Fig. 406A, comprising
the handle 59 and
the combination 55. The handle 59 with the left 58 portion (= tamed around
right portion 53) and the right
portion 60 (= turned around left portion 51).
31
CA 02786315 2012-08-24
CLAIMS
19618 30-06-2011
1. A piston-chamber combination comprising a chamber (162,186,231) which is
bounded by an
inner chamber wall (156,185,238), and comprising an actuator piston inside
said chamber to be
engagingly movable relative to said chamber wall at least between a first
longitudinal position and a
second longitudinal position of the chamber,
said chamber having cross-sections of different moss-sectional areas and
different
circumferential lengths at the first and second longitudinal positions, and at
least substantially
continuously different cross-sectional areas and circumferential lengths at
intermediate longitudinal
positions between the first and second longitudinal positions, the cross-
sectional area and
circumferential length at said second longitudinal position being smaller than
the cross-sectional area
and circrmiferential length at said first longitudinal position,
said actuator piston comprising a container
(208,208',217,217',228,228',258,258', 450,450')
which is elastically deformable thereby providing for different cross-
sectional areas and circumferential
lengths of the piston adapting the same to said different cross-sectional
areas and different
circumferential lengths of the chamber during the relative movements of the
piston between the first
and second longitudinal positions through said intermediate longitudinal
positions of the chamber,
the actuator piston is produced to have a production-size of the container
(208,208',217,217',228,228',258,258',450,450') in the stress-free and
undeformed state thereof in which
the circumferential length of the piston is approximately equivalent to the
circumferential length of said
chamber (162,186,231) at said second longitudinal position, the container
being expandable from its
production size in a direction transversally with respect to the longitudinal
direction of the chamber
thereby providing for an expansion of the piston from the production size
thereof during the relative
movements of the actuator piston from said second longitudinal position to
said first longitudinal
position,
the container (208,208',217,217',228,228',258,258',450, 450') being
elastically deformable to
provide for different cross-sectional areas and circumferential lengths of the
actuator piston,
characterized by the fact that
5p
CA 02786315 2012-08-24
= the combination comprises means for introducing fluid from a position
outside said container into
said container, thereby enabling pressurization of said container, and thereby
expanding said
container,
= a smooth surface of the wall of the actuator piston, at least on and
continuously until nearby its
contact area with the wall of the chamber,
thereby displacing said container from a second and to a first longitudinal
position of the chamber.
2. A piston-chamber combination comprising a chamber (162,186,231) which is
bounded by an
inner chamber well (156,185,238), and comprising an actuator piston inside
said chamber to he
engagingly movable relative to said chamber wall at least between a first
longitudinal position and a
second longitudinal position of the chamber,
said chamber having cross-sections of different cross-sectional areas acrd
different
circumferential lengths at the first and second longitudinal positions, and at
least substantially
continuously different cross-sectional areas and circumferential lengths at
intermediate longitudinal
positions between the first and second longitudinal positions, the cross-
sectional area and
circumferential length at said second longitudinal position being smaller than
the cross-sectional area
and circumferential length at said first longitudinal position,
said actuator piston comprising a container
(208,208',217,217',228,228',258,258', 450,450')
which is elastically deformable thereby providing for different cross-
sectional areas and circumferential
lengths of the piston adapting the same to said different cross-sectional
areas and different
circumferential lengths of the chansber during the relative movements of the
piston between the first
and second longitudinal positions through said intermediate longitudinal
positions of the chamber,
the actuator piston is produced to have a production-size of the container
(208,208',217,217',228,228',258,258',450,450') in the stress-free and
undeformed state thereof in which
the circumferential length of the piston is approximately equivalent to the
circumferential length of said
chamber (162,186,231) at said second longitudinal position, the container
being expandable from its
production size in a direction transversally with respect to the longitudinal
direction of the chamber
thereby providing for an expansion of the piston from the production size
thereof during the relative
movements of the actuator piston from said second longitudinal position to
said first longitudinal
position,
CA 02786315 2012-08-24
the container (208,208',217,217',228,228',258,258',450, 450') being
elastically deferrable to
provide for different cross-sectional areas and circumferential lengths of the
actuator piston, and
comprising an enclosed space,
characterized by the fact that
= the combination comprises means for changing the volume of the enclosed
space communicating
with said actuator piston of said container from a position outside said
container, thereby enabling
pressurization of said container, and thereby expanding said container.
= a smooth surface of the wall of the actuator piston, at least on and
contincously until nearby its
contact area with the wall of the chamber,
and thereby displacing said container from a second to a first longitudinal
position of the chamber.
3. A piston-chamber combination according to claim 1 or 2, wherein said
actuator piston inside or
outside said chamber to be sealingly movable relative to said chamber wall.
4. A piston-chamber combination according to claim 1, 2 or 3, wherein a part
of said chamber,
positioned adjacent to said actuator piston are communicating with each other
through a chatmel or
through the atmosphere.
5. A piston-chamber combination according to any of claims 1- 4, wherein the
chamber is elongate.
6. A piston-chamber combination according to any of claims 1-4, wherein the
chamber is circular.
7. A piston-chamber combination according to claim 6, wherein the chamber is
formed around a
circleround centre axis.
+1
8. A piston-clramber combination according to claims 1-7, wherein the actuator
piston is depressurized
and not engaging with the wall of the chamber.
9. A piston-chamber combination according to claim 8, wherein the piston is
moving from a first to a
second longitudinal position of the chamber.
3?.b
CA 02786315 2012-08-24
10. A piston chamber combination according to claims 1-7, wherein a part of
the lengh of the wall of
the chamber is parallel to the centre axis of said chamber.
11. A piston chamber combination according to claim 10, wherein said wall of
the chamber is
positioned at an end of a stroke of the actuator piston.
12. A piston-chamber combination according to claims 1-7, wherein the
container (208,208',217,
217',228,228',258,258',450,450') is comprising a deformable material
(205,206).
13. A piston-chamber combination according to claim 12, wherein the defomable
material (205,206)
is a fluid or a mixture of fluids, such as water, steam and/or gas, or a foam.
14. A piston-chamber combination according to claims 12 or 13, wherein in a
cross-section through the
longitudinal direction, the container, when being positioned at the first
longitudinal position of the
chamber (186,231), has a first shape which is different from a second shape of
the container when
being positioned at the second longitudinal position of said chamber.
15. A piston-chamber combination according to claim 14, wherein at least part
of the deformable
material (206) is compressible and wherein the first shape has an area being
larger than an area ofthe
second shape.
16. A piston-chamber combination recording to claim 14, wherein the deformable
material (206)
is at least substantially incompressible.
17. A piston-chamber combination according to claims 1-7, wherein the
container is inflatable.
18. A piston-chamber combination according to claims 1-7, wherein the
container (208,208',
217,217',228,228',258,258',450, 450') additionally comprises an enclosed space
(210,243) communica-
ting with the deformable container.
19. A piston-chamber combination according to claim 18, wherein said
introduction of the fluid
CA 02786315 2012-08-24
from a position outside said container into said container is done through a
first enclosed space, which
is communicating with said enclosed space.
20. A piston-chamber combination according to claims 1, 3-7, further
comprising means for
removing fluid from said container to a position outside the piston, thereby
enabling contraction of said
container.
21. A piston-chamber combination according to claim 20, wherein the removal of
fluid is done through
a second enclosed space, which is communicating with said enclosed space.
22. A piston-chamber combination according to claim 2-7 or 18, wherein said
means are
communicating with said enclosed space of said piston, by changing the volume
of said enclosed space,
increasing said volume mid thereby depressurizing said actuator piston,
thereby enabling contraction of
said container.
23. A piston-chamber combination according to claim 22, wherein the piston is
movable relative to said
chamber wall at least from a first to a second longitudinal position of said
chamber.
24. A piston-chamber combination according to claims 1-7, wherein the wall of
the container
(208,208',217,217',228,228',258,258',450, 450') comprises a bendable
reinforment layer,
25. A piston-chamber combination according to any of the previous claims,
wherein the cross-section
of the contact surface of the container and the wall of the chamber is cutting
the central axis of said
container in the longitudinal direction approximately just aside the middle
point of said section of the
elastically deformable wall of the container, at the side of a second
longitudinal position.
26. A piston-chamber combination according to claim 25, wherein the cross-
section of the contact
surface of the container and the wall of the chamber is cutting the central
axis of said container in the
longitudinal direction approximately outside the middle point of said section
of the elastically
deformable wall of the container, at the side of a second longitudinal
position.
}fit
CA 02786315 2012-08-24
27. A piston-chamber combination according to claims 12, 17, 20 or 22, wherein
the scatter piston
is comprising a piston rod, which is comprising said enclosed space.
28. A piston-chamber combination according to claim 26, wherein the piston rod
is comprising
engaging means outside said chamber.
29. A piston-chamber combination according to claim 28, further comprising a
crank adapted
to translate the motion of the piston between second and first longitudinal
positions of the chamber into
a rotation of the crank.
30. A piston-chamber combination according to claim 28, wherein the crank is
translating its
rotation into a movement of the piston from first to second longitudinal
positions of the piston.
31. A piston-chamber combination according to claims 19, 21 or 28, wherein the
crank is comprising
said first and said second enclosed space.
32. A combination according to claims 1-7, wherein the cross-sectional area of
said chamber at the
second longitudinal position thereof is 95 - 15 % of the cross-sectional area
of said chamber at the first
longitudinal position thereof.
33. A combination according to claims 1-7, wherein the cross-sectional area of
said chamber at the
second longitudinal position thereof is approximately 50% of the cross-
sectional area of said chamber
at the first longitudinal position thereof.
34. A combination according to claims 1-7, wherein the cross-sectional area of
said chamber at the
second longitudinal position thereof is approximately 5% of the cross-
sectional area of said chamber at
the first longitudinal position thereof.
35. A combination according to claims 1-6, wherein said chamber comprising
convex shaped walls
of longitudinal cross-sectional sections near a first longitudinal position,
said sections are updivided
from each other by a common border, a distance between two following common
borders defines a
J~q
CA 02786315 2012-08-24
heigth of the walls of said longitudinal cross-sectional sections, said
heigths are decreasing by an
increasing overpressure rate of said actuator piston in relation to the
pressure in said chamber, the
transversal length of the cross-sectional common borders is determined by the
maximum work force of
said actuator piston, which is chosen constant for said common borders.
36. A combination according to claims 1-6, wherein said chamber comprising
convex shaped walls of
longitudinal cross-sectional sections near a first longitudinal position, said
sections are updivided from
each other by a common border, a distance between two following common borders
defines a heigth of
the walls of said longitudinal cross-sectional sections, said heigths are
decreasing in a direction from a
first longitudinal postion to a second longitudinal position, the transversal
length of the cross-sectional
common borders is determined by the maximum work force of said actuator
piston, which is chosen
constant for said common borders.
37. A combination according to claims 35 or 36, wherein said chamber is
further comprising a wall
which is parallel to the centre axis of said chamber.
38. A combination according to claims 35-37, wherein said chamber is further
comprising a concave
shaped wall.
39. A combination according to claim 38, wherein said chamber is further
comprising a transition
between said convex shaped wall and said parallel well, wherein said
transition may be comprising a
concave shaped wall.
40. A shock absorber comprising:
- a combination according to any of claims Ito 39,
means for engaging the piston from a position outside the chamber, wherein the
engaging means have an outer position where the piston is at the first
longitudinal position of the
chamber, and an inner position where the piston is at the second longitudinal
position.
41. A shock absorber according to claim 40, further comprising anenclosed
space,
communicating with the container.
JWO
CA 02786315 2012-08-24
42. A shock absorber according to claim 41, wherein the enclosed space has a
variable
volume.
43. A shock absorber according to claim 41, wherein the enclosed space has a
constant volume.
44. A shock absorber according to claim 41, wherein the enclosed space is
adjustible.
45. A shock absorber according to claims 41 - 44, wherein the container and
the enclosed space form
an at least substantially sealed cavity comprising a fluid, the fluid being
compressed when the piston
moves from the first to the second longitudinal positions of the chamber.
46. A pump for pumping a fluid, the pump comprising:
- a combination according to claims 1-39,
- means for engaging a second piston in a second chamber from a position
outside the chamber,
- a fluid entrance connected to the second chamber and comprising a valve
means, and
- a fluid exit connected to the second chamber.
47. A pump for pumping a fluid, the pump comprising:
- a combination according to claims 1-39,
means for engaging a piston in the chamber from a position outside the
chamber,
a fluid enhance connected to the chamber and comprising a valve means, and
a fluid exit connected to the chamber.
48. A pump according to claim 46 or 47, wherein the engaging means have an
outer position where the
piston is at the first longitudinal position of the chamber, and an inner
position where the piston is at
the second longitudinal position of the chamber.
49. A pump according to claim 46 or 47, wherein the engaging means have an
outer position where
the piston is at the second longitudinal position of the chamber, and an inner
position where the piston
is at the first longitudinal position of the chamber.
CA 02786315 2012-08-24
50. The use of a piston-chamber combination according to claim 1 or 2 in a
motor, specifically a car
motor.
51. A motor, characterized by the fact that it comprises attached hereto a
piston-chamber
combination according to claim 1.
52. A motor, characterized by the fact that it comprises attached hereto a
piston-chamber combination
according to claim 2.
+1
53. A motor according to claims 1, 3 - 39, 46 - 51. wherein the crankshaft is
comprising a second
enclosed space, communicating at one end with an external pressure source, and
at the other end with
the enclosed space of said actuator piston.
54. A motor according to claim 53 wherein the crankshaft is comprising a third
enclosed space,
communicating the enclosed space of the actuator piston, and and at the other
end communicating with
a repressuration pump, which is communicating with an electric motor, said
motor gets it energy from a
battery which is charged by an energy source, such as solar power, or a fuel
cell, such as a Hz -fuel cell,
or an alternator which is communicating with said main axle.
55. A motor according to claim 54, wherein said alternator is communicating
with the axle of an
auxiliarly power source, such as a combustion motor which is burning HZ
derived from electrolysis of
conductive water, and 0, of the air, the water coming from a tank which can be
filled up externally.
56. A motor according to claim 54, wherein the last mentioned pump is
communicating with the axle of
an auxiliarly power source, such as a combustion motor which is binning HZ
derived from electrolysis
of conductive water, and 0, of the air, the water coming from a tank which can
be filled up externally.
57. A motor according to claim 53, wherein the communication between the
pressure source and the
enclosed space of said actuator piston takes place during a part of each
crankshaft turn.
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CA 02786315 2012-08-24
58. A motor according to claim 54, wherein the communication between the
enclosed space of said
piston and the repressuration cascade takes place during a part of each
crankshaft turn.
59. A motor according to claims 57 mid 58, wherein said communications are
separated in time
from each other.
59. A motor according to claim 59, wherein said communications are performed
by a T-valve, being
controlled by a computer which is electrically communicating with the main
axle of said motor.
61. A motor according to claim 60, wherein the pressure and/or volume of the
supply channel to said
T-valve is being controlled by a reduction valve, said reduction valve being
controlled by a speeder.
62. A motor according to claim 61, wherein said reduction valve is
communicating with a pressure
storage vessel, which is communicating with a repressuration cascade of pumps,
of which at least one
pump is communicating with the main axel [of said crankshaft, through another
crankshaft,] while
at least one pump is communicating with an electric motor, said motor gets it
energy from a battery
which is charged by an energy source, such as solar power, Sr a fuel cell,
such as a H2 -fuel cell, or an
alternator which is communicating with said main axle.
63. A motor according to claim 62, wherein said alternator is communicating
with the axle of an
auxiliarly power source, such as a combustion motor which is binning H2 from
electrolysis of
conductive water, and 02 of the air, the water coming from a tank which can be
filled up externally.
64. A motor according to claim 63, wherein the last mentioned pump is
communicating with the axle of
an auxiliarly power source, such as a combustion motor which is burning H2
from electrolysis of
conductive water, and 02 of the air, the water coming from a took which can be
filled up externally.
65. A motor according to claims 62 - 64, wherein said pumps are piston ptunps
or rotational pumps.
66. A motor according to claims 2 - 39, 46 - 51, wherein the enclosed space,
the second enclosed
space and the third enclosed space form a closed cavity.
381
CA 02786315 2012-08-24
67. A motor according to claim 66, wherein the pressure in said cavity is
being controlled by a
piston-chamber combination, which communicating with a bi-directional piston-
chamber combination
which is controlled by a reduction valve, which is controlled by a speeder.
68. A motor according to claims 67, wherein said bidirectional actuator piston-
chamber combination
is which is communicating with a pressure vessel, said vessel is communicating
with a repressu- ration
cascade of pumps, of which at least one is communicating with the main axel of
said crankshaft,
through another cran](shaft], while at least one pump is communicating with an
electric motor, said
motor gets it energy from a battery which is charged by an energy source, such
as solar power, and/or
by electricity from a fuel cell, such as a He -fuel cell, and/6r by an
alternator which is communicating
with said main axle,
69. A motor according to claim 68, wherein the last mentioned pump is
communicating directly with
the axle of the auxiliarly power source, such as a combustion motor which is
burning Hz, derived from
electrolysis of conductive water, and 02 from the air, the water coming from a
tank which can be filled
up, and when necessary from a conductive means storage tank
70. A motor according to claim 67-69, wherein the pressure in said cavity is
being additionally
controlled bye piston-chamber combination, which is communicating with said
pressure vessel.
71. A motor according to claim 65, wherein the pressure in the closed cavity
of a piston is
controlled by a piston-chamber combination, which is communicating with the
main axle of said motor,
electronically by a computer.
72. A motor according to claim 65, wherein the pressure in the closed cavity
of a piston is
controlled by a piston-chamber combination, which is communicating with the
main axle of said motor
through a cam wheel, which is communicating with a cam shall.
73. A motor according to claims 61 or 70 , wherein said pumps are piston pumps
or rotational
pumps.
CA 02786315 2012-08-24
7t&
74. A motor according to claims 1 - 4, 6 - 73, wherein a piston is rotating
around the centre axis of the
chamber.
75. A motor according to claims 1 - 4, 6 - 73, wherein the chamber is
rotating.
76. A motor according to claims 74 and 75, wherein the piston and the chamber
are rotating.
77. A motor according to claim 74 -76, wherein the actuator piston-chamber
combination is
comprising at least two sub-chamber, which are comprising an actuator piston,
said sub-chambers are
positoned in continuation of each other, whereby a first circular position of
sub-chamber is adjacent to
a second circular postion of another adjacent sub-chamber.
78. A motor according to claim 77, wherein the sub-chambers are identical.
79. A motor according to claim 78, wherein each sub-chamber is comprising an
actuator piston, said
pistons are identical, where each piston is positioned at a different circular
position per sub-chamber, in
relation to each other.
80. A motor according to claims 74-79, wherein the shape of the piston is not
changing during the
stroke.
80. A motor according to claims 62 or 68, wherein the pressure vessel is being
pressurized
by an external pressure source, through a pluggable connection.
81. A motor according to claims 54, 62 or 68, wherein the battery is being
charged by an external
electrical power source through a pluggabe connection.
82. A piston-chamber combination comprising an elongate chamber (70) which is
bounded by an
inner chamber wall (71,73,75) and comprising a piston means (76,76',163). in
said chamber to be
sealingly movable relative to said chamber at least between first and second
longitudinal positions of
S'
CA 02786315 2012-08-24
said chamber,
said chamber having cross-sections of different cross-sectional areas at the
first and second longitudinal
positions of said chamber and at least substantially continuously differing
cross-sectional areas at
intermediate longitudinal positions between the first and second longitudinal
positions thereof, the
cross-sectional area at the first longitudinal position being larger than the
cross-sectional area at the
second longitudinal position,
said piston means being designed to adapt itself and said sealing means to
said different cross-sectional
areas of said chamber during the relative movements of said piston means from
the first longitudinal
position through said intermediate longitudinal positions to the second
longitudinal position of said
to chamber,
characterized by the fact that
the piston means (76,76',163,189,189') comprises:
- a plurality of at least substantially stiff support members (8 1,92,184)
rotatably fastened to a
common member (6,23,45, 180),
- mid support members being provided in elastically deformable means (79),
supported by
said support members, for sealing against the inner wall
(71,73,75,155,156,157,158) of the
chamber (70) said support members being rotatable between 10 and 401 relative
to the longitudinal
axis (19) of the chamber (70),
- the support members (81,82,184) are bendable.
83. A piston-chamber combination according to claim 82, wherein said piston
inside or outside said
chamber to be sealingly movable relative to said chamber wall.
84. A piston-chamber combination according to claim 82, wherein the support
members having a
pre-determined bending force.
85. A piston-chamber combination according to claim 82, wherein the support
members (8 1,82,
184) are rotatable so as to be at least approximately parallel to the
longitudinal axis (19).
86. A piston-chmnber combination according to claim 82, wherein the
elastically deformable
CA 02786315 2012-08-24
8
J 0 6
means (79) is made of Polyurethane-foam.
87. A piston-combination according to claim 86, wherein the PU-foam is
comprising a Poly-
urethane Memory foam and a Polyurethane foam.
88. A piston-chamber combination according to claim 87, wherein the
Polyurethane foam is
comprising a major part is Polyurethane Memory foam, and a minor part
Polyrrethane foam.
89. A piston-chamber combination according to claims 86 - 88, wherein the
Polyurethane foam is
provided with a flexible impervious layer.
90. A piston-chamber combination according to claim 89, wherein the impervious
layer has an
unstressed production size of which the circrunference is approximately the
circumference of the wall
of the chamber at a second longitudinal or circular position.
91. A piston-chamber combination according to claims 82 or 85, wherein the
common member is
attached to a crankshaft.
92. A piston-chamber combination according to claims 82 or 87, wherein the
common member is
attached to a piston-chamber combination, which is an external bidirectional
actuator.
93. A piston-chamber combination comprising an elongate chamber (70) which is
bounded by an
inner chamber wall (71,73,75) and comprising a piston means (76,76',163) in
said chamber to be
sealingly movable relative to said chamber at least between first and second
longitudinal positions of
said chamber,
said chamber having cross-sections of different cross-sectional areas at the
first and second longitudinal
positions of said chamber and at least substantially continuously differing
cross-sectional areas at
intermediate longitudinal positions between the fast and second longitudinal
positions thereof, the
cross-sectional area at the first longitudinal position being larger than the
cross-sectional area at the
second longitudinal position,
CA 02786315 2012-08-24
3 2 ~
said piston means being designed to adapt itself and said sealing means to
said different cross-sectional
areas of said chamber during the relative movements of said piston means from
the first longitudinal
position through said intermediate longitudinal positions to the second
longitudinal position of said
chamber,
characterized by the fact that
the piston means (49, 49') comprises:
- a phtrality of at least substantially stiff sapport members (43) rotatably
fastened by an axle
(44) to a piston rod (45),
- said support members being supported by a sealing means (41), said sealing
means being
supported by spring 42, for sealing against the inner wall
(71,73,75,155,156,157,158) of the chamber
(70) said support members being rotatable between Pro and (i2 relative to the
longitudinal axis (19) of
the chamber (70),
- afexible impervious membrane (sheet) (40) is mounted in said sealing means
(O-ring) (41),
and is positioned perpendicular to the centre axis (19) of said chamber (1),
- said membrane (flexible impervious sheet) is comprising a reinforment layer,
said support members (means), said sealing means (0-ring), said flexible
impervious membrane
(sheet) and said (lying) spring are vulcanized on each other.
94, A piston-chamber combination according to claim 93, wherein the support
members (81,82,184)
(means) are rotatable so as to be at least approximately parallel to the
longitudinal axis (19).
95. A piston-chamber combination according to claim 93, wherein said flexible
reinforment
layer (sheet) is comprising a spiral shaped reinforcement.
96. A piston-chamber combination according to claim 93, wherein said
reinforment layer (sheet)
is comprising a concentrically shaped reinforcement, positioned around the
centre axis of said chamber.
97. A piston-chamber combination according to claim 93, wherein said flexible
impervious
membrane (sheet) having a more than 900 angle with the centre axis of said
centre axis of said
chamber.
CA 02786315 2012-08-24
32
98. A piston-chamber combination according to claim 97, wherein said flexible
impervious
membrane (sheet) is mounted on said piston rod.
99. A piston-chamber combination according to claim 97, wherein said flexible
impervious
membrane (sheet) is vulcanized on said piston rod.
100. A piston-chamber combination according to claims 82 or 93, wherein the
common member is
comprised in a piston-chamber combination.
101. A piston-chamber combination according to claim 93, wherein the flexible
impervious sheet is
being supported by a foam.
102. A piston-chamber combination according to claim 101, wherein said foam is
being rehlforced
with stiff member, which are rotatably fastened to the piston rod.
103. A piston-chamber combination comprising a chamber (162,186,231) which is
bounded by an
inner chamber wall (156,185,238), and comprising a piston means inside said
chamber to he
engagingly movable relative to said chamber wall at least between a first
longitudinal position and a
second longitudinal position of the chamber,
said chamber having cross-sections of different cross-sectional areas and
different
circumferential lengths at the first and second longitudinal positions, and at
least substantially
continuously different cross-sectional areas and circumferential lengths at
intermediate longitudinal
positions between the first and second longitudinal positions, the cross-
sectional area and
circumferential length at said second longitudinal position being smaller than
the cross-sectional area
and circumferential length at said first longitudinal position,
said piston means comprising a container (208,208',217,217',228,228',258,258',
450,450`)
which is elastically deformable thereby providing for different cross-
sectional areas and circumferential
lengths of the piston adapting the same to said different cross-sectional
areas and different
circumferential lengths of the chamber during the relative movements of the
piston between the first
and second longitudinal positions through said intermediate longitudinal
positions of the chamber,
CA 02786315 2012-08-24
3
the piston means is produced to have a production-size of the container
(208,208',217,217',228,228',258,258',450,450') in the stress-free and
undeformed state thereof in which
the circumferential length of the piston is approximately equivalent to the
circumferential length of said
chamber (162,186,231) at said second longitudinal position, the container
being expandable from its
production size in a direction transversally with respect to the longitudinal
direction of the chamber
thereby providing for an expansion of the piston from the production size
thereof during the relative
movements of the actuator piston from said second longitudinal position to
said first longitudinal
position,
the container (208,208',217,217',228,228',258,258',450, 450') being
elastically deformable to
provide for different cross-sectional areas and circumferential lengths of the
actuator piston,
characterized by the fact that
the piston means (92,92',146,146',168,168', 208,208',222,222',222") comprises
an elastically
deformable container comprising a deformable material
(103,103',124,124',136,137,173,173',
174,174', 205,205',206,206'215,215',219,219').
104. A piston-chamber combination according to claim 103, wherein said
container in said chamber to
be sealingly movable relative to said chamber wall.
105. A piston-chamber combination according to claims 103 or 104, wherein the
deformable material
(103,103',124, 124',136,137,173,173',174,174',205,205',206,206'215,
215',219,219') is a fluid or a mixture of fluids, such as water, steam and/or
gas, or a foam.
106. A piston-chamber combination according to claim 105, wherein the
deformable material
(124,124', 136,174,174',205,205',219,219') is at least substantially
incompressible.
107.A piston-chamber combination according to claim 105 or106, wherein the
container is
inflatable.
108.A piston-chamber combination according to claim 103 or 104, wherein the
combination additionally is comprising a piston and, the wall of the container
is comprising a flexible
material, which is vulcanized on said piston rod.
CA 02786315 2012-08-24
3~0
109 A piston-chamber combination according to claim 108, wherein the wall of
the container is
comprising at least a layer with a reinforcement, positioned nearest to the
piston rod and vulcanized on
that, and a layer without a reinforcement which is vucanized upon said layer
with a reinforcement.
110. A piston-chamber combination according to claim 109, wherein the
reinforcement strengs are
laying parallel to the centre axis of said piston, aid are bendable.
I t l.A piston-chamber combination according to claim 107 or 108, wherein the
wall of the
container is comprising two reinforcement layers, where the reinforcements of
said taywers we
crossing each other with a very small angle.
112.A piston-chamber combination according my of the claims wherein the length
of a
container type piston is enlarged, so that the shape of an ellipsoide shaped
piston at a second
longitudinal position is remaining its shape, but not its size when being on a
first longitudinal position.
113. A motor according to claim 51, wherein a pressure regulator which is
communicating
with a pressure vessel and a third enclosed space, is communicating with a
speeder.
114. A motor according to claim 51, further comprising two cylinders, wherein
the third
enclosed space of each cylinder are communicating with each other through the
connection of the two
sub-crankshafts which are comprised in the crankshaft of said motor, and the
second enclosed spaces of
each cylinder are communicating with each other outside said crankshaft, (Fig.
19)
115.A motor according to claim 114, wherein the crankshaft configuration of
two piston-
chamber combinations the connector rods are positioned 180 from each other.
(Fig. 19)
116. A motor according to claim 114 and 115, further comprising more than two
cylinders,
wherein a second enclosed space is connected through the connection of said
sub-crankshafts of the
existing two cylinders, with the second enclosed space of the sub-crankshaft
of the cylinder to be
added. (Fig. 19)
CA 02786315 2012-08-24
: i.
117. A motor according to claim 52, farther comprising two cylinders, wherein
the 2"
longitudinal position of one cylinder is at the sane geometrical level of the
1st longitudinal position of
a second cylinder, both actuator pistons are communicating with each other
through a crankshaft, said
crankshaft is comprising two connected sub-crankshafts, one for each actuator
piston, where the
connection rods to these actuator pistons are positioned 1S0 from each other.
(Fig. 17)
118. A motor according to claim 117, further comprsing ESVT pimps for each of
the
cylinders, wherein said pumps are combined for said two cylinders into one
pump, through
communication of the enclosed space of one of the actuator pistons with the
enclosed space of the other
of the actuator pistons, said enclosed spaces being comprised in said
crankshaft, said enclosed spaces
are communicating with each other at the connection point of said sub-
crankshafts. (Fig. 17)
119. A motor accordung to claim 118, further comprising valves, which are
opening and
closing the connection between said ESVT-pump and said second or third
enclosed spaces, while each
connection has a check valve or check valve function, said valves are
controlled by either the pressure
of said ESVT-pump and/or by tappets, said tappets are communicating with a
camshaft, which is
communicating with the main axle of an auxilliarly motor. (Fig. 17)
120. A motor according to claims 117 - 119, further comprising more than two
cylinders,
where each added cylinder is communicating through the enclosed spaces of die
connected sub-
crankshafts of the existing sub-crankshafts, (Fig. 17)
121. A motor according to claim 52, further comprising two cylinders, wherein
the 1st
longitudinal position of one cylinder is at the same geometrical level of the
1st longitudinal position of
a second cylinder, both actuator pistons are communicating with each other
through a crankshaft, said
crankshaft is comprising two connected sub-crankshafts, one for each actuator
piston, where the
connection rods to these actuator pistons are positioned 00 from each other.
(Fig. 18)
122.A motor according to claim 121, further competing ESVT pumps for each of
the
CA 02786315 2012-08-24
3 i1-
cylinders, wherein said pumps are combined for said two cylinders into one
pimp, through
communication of the enclosed space of one of the actuator pistons with the
enclosed space of the other
of the actuator pistons, said enclosed spaces being comprised in said
crankshaft, said enclosed spaces
are communicating with each other at the connection point of said sub-
crankshafts. (Fig. 18)
123. A motor according to claim 122, further comprising valves, which are
opening and
closing the connection between said ES VT-pump and said second or third
enclosed spaces, while each
connection has a check valve or check valve function, said valves are
controlled by either the pressure
of said ES VT-pump and/or by tappets, said tappets are communicating with a
camshaft, which is
communicating with the main axle of an auxilliarly motor. (Fig. 18)
124. A motor according to claims 121 - 123, further comprising more than two
cylinders,
where the enclosed space(s) of each added (couple) cylinder(s) is(are)
separated through a filler in the
connection with said existing sub-crankshafts, and where the power strokes of
the added cylinders are
simultaneously the return strokes of the existing cylinders. (Fig. 18)
125. A motor according to claim 52, further comprising 2 cylinders wherein the
connection
rods are in a position of 1800 from each other, while the chambers have an
identical geometrical
position of their 1sn and 2n longitudinal positions. (Fig. 18)
126. A motor according to claims 114 - 125, wherein the piston-chamber
combinations for
each of the enclosed spaces in a sub-crankshaft, which are changing the
speed/pressure in a cylinder are
communicating with each other through the electric pressure regulator of the 2-
way actuators, which is
moving the piston rod of each of said piston-chamber combinations, and is
communicating with the
external speeder.
127. A motor according to claims 114-126, wherein the piston rods of the
pumps,
pressurizing the fluid in said pistons, are being powered by a 2 way actuator
piston powered by a
battery, which is powered by an auxillisely power source.
128. A motor according to claims 114-127, wherein the piston rods of the
pumps,
CA 02786315 2012-08-24
3g'
pressurizing the fluid in said pistons, ore being powered by a 2 way actuator
piston powered by a
battery, which is powered by an anxilliaely power source.
129. A motor according to claims 114-128, wherein the piston rods of the
pumps,
pressurizing the fluid in said pistons, are being powered by a 2 way actuator
piston powered by a
crankshaft, which is powered by an auxilliarly power source.
130. A motor according to claims 114-129, wherein the piston rods of the
pumps,
pressurizing the fluid in said pistons, are being powered by a 2 way actuator
piston powered by a
cranishafl, which is powered by an auxilliarly power source.
131. A motor according to claim 52, which is comprising a circular chamber and
a actuator
piston, wherein the piston rod is sealiugly movable in a cylinder, and the
enclosed space inside said
piston rod is communicating with pressure controller, which is communicating
with a remotely
positioned speeder, while the size of the enclosed space is regulated by a
pump with a conical chamber, of
which end is running over a cam profile, said cam profile is driven by an
auxilliarly electric motor
which is turning said cam, and tanning independently of said motor around the
same main motor uric.
132. A motor according to claim 131, wherein said actuator piston having a
wall a reinforcement,
said wall being mounted on an end fixed on said piston rod, and on a movable
end, which can
sealingly slide on said piston rod.
133. A piston-chamber combination comprising an elongate chamber (70) which is
bounded by an
inner chamber wall (71,73,75) and comprising a piston means (76,76',163) in
said chamber to be
sealingly movable relative to said chamber at least between first and second
longitudinal positions of
said chamber,
said chamber having cross-sections of different cross-sectional areas at the
first and second longitudinal
positions of said chamber and at least substantially continuously differing
cross-sectional areas at
intermediate longitudinal positions between the first and second longitudinal
positions thereof, the
cross-sectional area at the first longitudinal position being larger than the
cross-sectional area at the
second longitudinal position,
CA 02786315 2012-08-24
said piston means being designed to adapt itself and said sealing means to
said different cross-sectional
areas of said chamber during the relative movements of said piston means from
the first longitudinal
position through said intermediate longitudinal positions to the second
longitudinal position of said
chamber, the piston means (1300) is comprising:
- a plurality of at reinforcement pins (1302,1303,1304) rotatably fastened to
a holder plate
(1307) which is comprised by a holder (1308),
- said reinforcement pins being provided in elastically flexible foam,
supported by
said reinforcement pins, for sealing against the inner wall (XXXX) of the
chamber (70) said
reinforcement pins being rotatable between 00 and 40 relative to the
longitudinal axis (1319) of the
chamber (70),
- an impervious layer 1305, which is elastically flexible,
characterized by the fact that
the reinforcement pins are made of metal,
said holder plate is made of metal, and is comprising small closed, rounded
offend holes
(1329, 1330, 1331) in more than one row (1326,1327,1328),
- said reinforcement pins are being fastened by magnetic force to said holder
plate.
134. A piston-chamber combination comprising an elongate chamber which is
bounded by an
inner chamber wall and comprising a piston means in said chamber to be
sealingly movable relative to
said chamber at least between first and second longitudinal positions of said
chamber,
said chamber ]raving cross-sections of different cross-sectional areas at the
first and second longitudinal
positions of said chamber and at least substantially continuously differing
cross-sectional areas at
intermediate longitudinal positions between the first and second longitudinal
positions thereof, the
cross-sectional area at the first longitudinal position being larger than the
cross-sectional area at the
second longitudinal position,
said piston means being designed to adapt itself and said sealing means to
said different cross-sectional
areas of said chamber during the relative movements of said piston means from
the first longitudinal
position through said intermediate longitudinal positions to the second
longitudinal position of said
chamber, wherein
- the piston means comprises an elastically deformable container comprising a
defomtable material,
the deformable material is a fluid or a mixture of fluids, such as water,
steam and/or gas, or a foam,
CA 02786315 2012-08-24
3 j"~'
characterized by the fact that
the wall of said container is comprising a separate wall part (2106, 2112,
2113, 2123, 2133, 2142,
2143, 2207, 22xx, 22xx", 2244, 2244"; 2145, 2199, 2238), said separate wall
part has a bigger
circumference than the rest of the wall of said container, and is comprising
the contact aeon with the
wall of said chamber
135. A piston-chamber combination comprising an elongate chamber (70) which is
bounded by an
inner chamber wall (71,73,75) and comprising a piston means (76,76',163) in
said chamber to be
sealingly movable relative to said chamber at least between first and second
longitudinal positions of
said chamber,
said chamber having cross-sections of different cross-sectional areas at the
first and second longitudinal
positions of said chamber and at least substantially continuously differing
cross-sectional areas at
intermediate longitudinal positions between the first and second longitudinal
positions thereof, the
cross-sectional area at the first longitudinal position being larger than the
cross-sectional area at the
second longitudinal position,
said piston means being designed to adapt itself and said sealing means to
said different cross-sectional
areas of said chamber during the relative movements of said piston means from
the first longitudinal
position through said intermediate longitudinal positions to the second
longitudinal position of said
chamber, the piston means (1300) is comprising:
- a plurality of reinforcement pins (1352,1353,1354) rotatably fastened to a
holder plate
(1358) which is comprised by a holder (1359),
- said reinforcement pins being provided in an elastically flexible foam,
supported by
said reinforcement pins, for sealing against the inner wall (XXXX) of the
chamber (XXXX) said
reinforcement pins being rotatable between 0 and 401 relative to the
longitudinal axis (1319) of the
chamber (70),
- an impervious layer 1305, which is elastically flexible,
characterized by the fact that
- the reinforcement pins are made of a plastic, having sphere shaped ends
(1355, 1356,
1357),
- said holder plate is comprising small closed , rounded off sphere cavities
(1360, 1361,
1362) in more than one row (1326,1327,1328),
CA 02786315 2012-08-24
said sphere shaped ends fit into said rounded off sphere caivities,
said holder plate is further comprising openings (1363, 1364,1365 for guiding
said
reinforcement pins.
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