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1
19627 - Piston ¨ Chamber Combination Vanderblom Motor 01-07-
2012
19627 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
circumpherential lengths at the first
and second longitudinal positions of said chamber and at least substantially
continuously different cross-
sectional areas and different circumpherential 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 circumferential 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.
19627 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
combustible techniques of oil derivatives like petrol, diesel, and which can
compete with current motors
based on said combustible technics. And additionally to comply with the demand
for reducing CO2.-
emission, so as to compete as well with combustible motors based on Hz, 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 derivatives 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 among others toxic gasses like CO,
and gasses like CO2 which
a) 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 (limousine,
4 wheel drive) for a
passenger car.
The new combustible motors based on H2, or even air are lacking 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 current 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 setting 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 fine masked network will these motors not be
distributed, because
nobody will buy such motor, due to lack of availability, and nobody 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 independent of
networks for providing the energy
source. A current development of a home filling station for H2 seems an
interesting but quite so tricky
thought, because this gas is a very dangerous gas, and should only be handled
by instructed personnel.
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19627 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.
19627 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 displacing said 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 guided by a bearing on one or both sides of the cylinder.
The piston rod outside the
cylinder may be pushing or pulling an external device. It may also be engaging
a crank shaft, so that a
rotation occurs of the crank shaft axel, which may result in motion of e.g. 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 EP 1 179
140 Bl. 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 wall 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
container, and the wall of the chamber, said internal pressure may have
influence on the- speed of the
motion of the piston.
An actuator according to the invention is a piston chamber combination which
has an inflatable
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 size, and the piston may be moving in the chamber or vice versa
preferably without 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.
5
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. Thus said
motion may be initiated
by reaction forces from the wall of the chamber to the wall of the 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 to 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 in
a chamber with a so-called
constant maximum working force shape (W02008/025391 ¨ 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 sequentially 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
longitudinal 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
strings directed from 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.8D), and optionally with a slight angle with the centre
axis of the chamber and/or
at least 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 wall of the piston, optionally approximately just under said middle
point of the elastically
deformable wall of said piston, said movement will result in an 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 time 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 (191), the movable end of
the piston, is coming 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 longitudinal position.
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,
so that the part of the container 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
position.
The overpressure is measured in relation to the atmospheric pressure, which is
why when the
piston may be positioned inside a closed 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 be
under atmospheric pressure.
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
the wall may also due, 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
constant or variable, and adjustable. Said enclosed space may be communicating
with a pressure source.
In 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 enabling contraction of said container.
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 sealingly 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
0 the wall of the chamber ¨ this will reduce the friction force between
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 out 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, without
engaging the wall of the chamber. This may be done by reducing the pressure
inside the 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 without jamming.
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 W02008/025391, in order to guide the piston during said part of the stroke,
without 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 chamber.
The engaging means may
be pushing or pulling when the piston is moving from second to first
longitudinal 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 sealingly
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.
It may however also be possible that the piston is comprising a piston rod
which extends in two
longitudinal directions, and one piston rod may normally be a continuation of
the other. One or both
piston rods may comprising engaging means, e.g. positioned outside the
chamber. When both piston rod
ends may extend outside the chamber, one bearing of the piston rod may be
fastened rigidly to the
chamber, 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 return 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 sealingly moving relative to the chamber 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.
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:
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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 its rotation into a movement of the piston from
first to second longitudinal 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 impuls of
the contra weights 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
may be 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 same 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 axel 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 axel. With an 0-
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.
In a nineth aspect, the invention relates to a combination of a piston and a
chamber,
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.
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 space 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 be
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
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
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towards a first longitudinal position of the chamber. The pressurization is
done by connecting the
third enclosed space, which has overpressure in relation to the first enclosed
space, to the first
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 communcating said second enclosed space during a
period
of the time when the piston is moving from second to first longitudinal
positions of the
chamber.
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
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 adjustable.
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
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 means 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.
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=
A pump, wherein the engaging means may have an outer position where the piston
may be at the
second longitudinal position of the chamber, and an inner position where the
piston may be at the
first longitudinal position of the chamber.
The technology of the piston-chamber combination may be used in a motor,
specifically in a car motor
¨ specifically the self-propelling actuator.
= The piston may also move relatively with the tapered wall, within a
chamber, which may be
cylindrical, or conical (not shown).
The chamber in which the ( actuator) piston is positioned, may be of the type
wherein said chamber
may be comprising internal convex shaped walls of longitudinal cross-sectioned
sections near a first
longitudinal position, said section may be updivided from each other by a
common border, a distance
between two following common borders defines the height of the walls of said
longitudinal cross-
is sectional sections, said heights are decreasing by an increasing
internal overpressure rate of said
piston, or in the direction from first to second longitudinal position the
transversal length of the cross-
sectional common borders may be determined by the maximum work force, which
may be chosen
constant for said common borders.
Additionally may said chamber comprising a wall of a cross-sectional border
which is parallel to the
centre axis of said chamber.
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And, said piston-chamber combination may comprise a transition between said
convex shaped walls
and said parallel wall when said transition may be comprising at least a
concave shaped wall, which
may be positioned near a second longitudinal position.
And said piston-chamber combination may comprise a concave shaped wall, which
may be positioned
at least on one side to a convex shaped wall.
1
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19627 SUMMARY OF THE INVENTION ¨ feasibility study
The feasibility study for a 'green' motor is as follows ¨ please review Fig.
10B and Fig. 11B
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
5
continuously 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 pumping system using the energy efficient piston-chamber combination
according to
W02000/070227, of which at least one step is being energized by an external
green power source, e.g.
10
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. 110 and 13F.
That system is complying to
the earlier stated specifications.
TRANSLATIONAL POWER SOURCE for a 'green' motor based on the principle of Fig.
11A
15
The overall system solution regarding this invention is, that said 'green'
motor as such may be
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 H2 generated preferably when the motor is running
by e.g. electrolyses, or
optionally by a H2 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 continuously 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
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W02000/070227 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 017 mm (from 0 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 4-+ big
sphere) which is not jamming in
said 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 not being zero
between the wall of the chamber and the 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 (W02008/025391, 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 (W02009/083274). 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 Bars
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%
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energy may be saved: e.g. by using a piston based on e.g. claim 1 of
EP1179140B1 or on Figs.5A ¨ 5H
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 a solar cell
(which should not be bigger than a roof of a common car, 6r 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 1-12 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 said 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 unnecessary, 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 11 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.
19627 ( amended) added matter to the description ¨ feasibility study in 19618
The feasibility study until now did not incorporate quantitatively the lack of
heat generated by a motor
of this invention, in comparison with Otto Motor types.
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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-
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 H2), from a flywheel or from regenerative 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. 11G, 15C or 15D and Fig.13F,G and Fig.14D 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,G and Fig.14D 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, 1600cc, weight 836kg, with a 53 kW
/
71 pk gasoline motor, comprising 4 cylinders of each 0 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 weight 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 luggage.
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The chamber of the pump shown in W02008/025391 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 0 58mm ¨ 017mm, respectively. Using an inflatable ellipsokle 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: 2'd
1St longitudinal positions) to approx. 0 bar
(stroke: 1st ¨+ 2nd 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 independent 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 3Y2 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
V2= 4/3 x 3,14 x 12,553 (025.1mm; P2=0,35 N/mm2)= 8280 mm3 to V1= 4/3 x 3,14 x
23,453 (0
46.9mm; P1=0,05 N/mm2) = 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: L1=302,78 ¨ 86,57=
216,21, Ar= 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 L1 is:
Wisothermal = -131V11n(P2/P1)= 0,35 x 54015 x In 7= 0,35 x 54015 x 2,302585 x
log 7 = 36788
Nmm/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
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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
5 = 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.
10 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 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
15 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
20 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 shown in Fig. 11F 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.
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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 (0 25,1 mm) with a
medium internal pressure
(3,5 Bar) to a bigger sphere shape (0 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 (0 46,9mm; 0,5 Bar) of the actuator piston to its
production shape (el
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 (0 25,1 mm, 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:
Wisothermal = -P V In(P2/P1)= -1(check this) x 4/3 x 3,14 x 12,553 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.
(* P2 absolute is 4,5 bar, if P1 = 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 modified compressor is a bit quicker charging the pressure storage
vessel.
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P = 2200 W for 8 Bar, hence for 3'4 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 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 24cc
/ 66cc (VW Golf
Mark II has motor of 53kW, 1600cc, 0 90mm, 4 cylinder 825W is approx. 24cc,
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.
END 19627 amended 19611 added matter to the description ¨ feasibility study in
19618
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10
A further development may be that the inflatable piston is moving in a
specially
designed chamber, so that the generated force of the piston 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 first principle according to Fig. IA
is a new aspect as
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
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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
crankshaft. 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 Fig.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.
In order to give the motor more power (torque on the main axle) may 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 reduction valve in said (lead) line [829]. Said reduction valve
may be communicating with a
speeder.
The pressure management in more detail of said actuator piston may be
organized as follows.
Both in the wall of the crank of the crankshaft and at the end 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 or the third enclosed space within
the crankshaft ¨ while
communicating with the second enclosed space, the piston may then be
pressurized through its enclosed
space and may be moving from a second to a first longitudinal position in the
chamber. While
communicating 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
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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.
5 At the final second longitudinal position of the piston may the hole
FILL IN
More than one actuator piston-chamber combination in said motor may be present
on the
10 same axle. This concept however may not be helpfull 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.
HOW IS IT RUNNING AND HOW IS THE INTERRELATIONSHIP BETWEEN THE ACTUATOR
PISTON/CHAMBER COMBINATIONS PER ONE CRANKSHAFT ORGANIZED??
The crankshaft itself may be an inefficient way to generate rotational motion,
and moreover, the
stroke length of this 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
33.2% of energy needed for a 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 are 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 structure. Thus, this motor type
may not fully complying to
said specifications, when one would aim e.g. a 'green' car motor.
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Thus, in order to complying to specifications a crankshaft may be avoided, as
well as a gear.
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.
Al
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 mentioned, may
this decreased use of energy specifically be obtained in a chamber around a
circleround centre line,
which may be concentrically positioned around the main axle of said motor, by
reducing the distance
from a 1st rotational position to a 2'd rotational position of a piston in
said chamber to approximately the
radius of said piston, so that the motor almost continuously may be powering
said axle.
Al
A conical chamber, wherein a piston may function as a self-propelled actuator,
may be bended
circularly in the longitudinal direction, and may be filling 3600 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 c.q. 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 centre axis 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.
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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-H, 9A-C), which due to its symmetrical form enables a
less complex
construction for the bearings of the piston rod. E.g. the piston rod may be
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.
However, 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 ¨ sphere)
has, may be less than of a
ellipsoide +-4 sphere actuator piston. This calls for a motor, where more than
one actuator piston per
chamber is being used. Additional issues call for the same, because the
actuator piston is moving
interruptedly (please see later), and more than one piston in the same 3600
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 'hesitations' in the
motion of another actuator piston, said actuator pistons may be positioned on
different positions on the
centre axis of said chamber. As an example, if the 360 chamber has been
updivided in 4 identical
subchambers, the number of actuator pistons may be 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 1st 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
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1st circular position, because the circular 1st position and the circular 2'd
position are in direct
continuation of each other in 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 / 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
accomplished that said computer is steering the pressure from a pressure
vessel, which is serving as a
Jo 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 very well be
of the kind having differing cross-sectional in the transitional direction.
Because of the speed of the
movement may this chamber be of a kind having a constant circumpherence, so
that the piston only is
bending during operation. But of course, chambers having differing sizes of
the transitional
circumpherence 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 be a wheel, which is rolling over
said camdisk. Thus, as
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 outerpart of said
wheel may have a notch,
in which a drive belt, which may be driving auxiliary 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.
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The most reliable system may be a fixed piston in a rotating chamber. An
advantage may be, that the
motor may be comprising more than one piston, e.g. 5 pistons, which each may
be positioned at
different rotational positions, which may make the motor turning smoothly,
because the transition of a
piston from its 11 rotational position to its 2nd rotational position may be
powered by e.g. 4 other pistons.
And the "hesitation behaviour" @lease see later) of a piston while moving from
a 2nd to a 1st 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 fluid 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 additionally reduced to approx. 350 kg. The TWR is now approx. 5,6.
Controlling the rotational motor may be done in a similar way as the
controlling of the motor with
translating pistons (or even with translating chambers and non-moving pistons,
or even when both are
moving ¨ not shown).
Controlling means: putting into function, starting up, speeding up, slowing
down, powering up,
stopping, and taking the motor out of use.
Putting 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 turning.
On the same axle as the moving piston or moving chamber is using, may there be
a starter motor, which
is using electricity from a starter battery, which itself is loaded by
electricity from a solar energy. The
starter motor may be turning said axle, and so initiate the rotation.
FILL IN
The pressure management may be done as follows.
A
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In the motor where the piston is moving, needs this piston 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.
5
NEW electronic/mechanic SOLUTION
Otherwise, would it be possible to create a mechanical solution, as the change
of pressure is of a certain
frequency: e.g. a camshaft, which is communicating with the drive shaft
through a time belt. The camshaft
10 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.
15 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.
NEW electronic/mechanic 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.
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TRANSLATIONAL POWER SOURCE for a motor based on the principle of Fig. 11F
A still more reliable system may be obtained by a new principle according to
Figs. 11F and 13F for the
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 be obtained by a change of
volume of the enclosed space of the piston. The improved reliability may
relate to reducing the number
of transitions of pressurized fluid, which may leak. In this principle may
mainly the controlling devices
be using energy for changing the volume of the enclosed space. This may very
well be done so that also
to
here energy is being reduced, by using again a piston (e.g. one for the
function of said piston, and
preferably one for the speed/power ¨ optionally a separate piston for the
power management) which is
moving sealingly in a cylinder, said cylinder having continuously differing
transitional cross-sectional
area's and e.g. changing circumferences so that again a 65% reduction of the
energy used may be
obtained. Also for this principle may the embodiment with a fixed piston in a
rotational chamber be the
best option for reducing the use of energy. Constant circumferences may also
work, but the gained
reduction may be lower.
The change (and consumption) of pressure of a fluid within an inflatable
piston may also be
done in an alternative way, alternative to the principle shown in Fig. 11A. 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 (torque) of said motor, and this may be done serially of
simultaneously. The energy is coming
from
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 principle of that shown in Fig. 11A. There
will in this new principle be no
leaks between high pressure fluid when the piston is moving from 2nd to 1st
longitudinal positions, and
low pressure fluid when the piston is moving vice versa in the joints, such as
crankshaft ¨ big end
bearing, and the two parts of the connecting rod.
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The energy used may be used to move a piston in a conical chamber which may be
optimized
to reducing the working force on the piston rod of said piston, for changing
the volume of the enclosed
space. Additionally is the energy used may be used in a similar piston-chamber
combination as the one
used for said volume changing, for adjusting the volume of the enclosed space.
The movement of the volume changing piston may be done by using pressurized
liquid which is
moving a piston in a chamber from one point to another an vice versa by means
of e.g. valves or other
kind of control devices, or by magnetic guidance. This is also valid for the
piston which is adjusting the
volume of the enclosed space ¨ the control of the movement of said piston may
be done by
communicating with a speeder, which is controlled by e.g. a person or a
computer.
ROTATING POWER SOURCE FOR A MOTOR based on the principle of Fig. 13E
The change (and consumption) of pressure of a fluid within an inflatable
piston may also be done
in an alternative way, alternative to the principle shown in Fig. 12A. 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
(torque) of said motor, and this may be done serially of simultaneously.
This prin-
ciple is in rotating power sources still more efficient than for transitional
power source systems, because
the distance from 1st to 2nd rotational positions is almost nil ¨ therefore
may the piston which is changing
the volume of the enclose space be guided by a cam disk, which may be mounted
on the axle, around
which the motor power source is rotating.
In fact this is the most efficient motor.
A motor with a circular chamber may comprise a wall, at least a part of the
length* of the centerline of
said chamber, which is parallel to the centre axis of said chamber.
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In a motor may a conical chamber( elongate or circular*) be of a type where
the force of the piston rod,
generated by the actuator piston, is constant. That may also be the case for
any of the pumps which are
incorporating in said motor, where a fluid is pressurized.
The chamber in which said actuator piston is positioned may be comprising
internal convex shaped walls
of longitudinal cross-sectional sections near a first longitudinal position,
said section may be updivided
from each other by a common border, a distance between two following common
borders define the
height of the walls of said longitudinal cross-sectional sections, said
heights are decreasing by an
increasing internal overpressure rate of said piston, or in the direction from
first to second longitudinal
positions, the transversal height of the cross-sectional common borders may be
determined by the
maximum work force, which be chosen constant for said common borders.
In case the piston is positioned in a cylindrical chamber with an internal
tapered center, said convex
shaped walls are concave shaped.
And, said piston-chamber combination may comprise a wall of a cross-sectional
border which is parallel
to the centre axis of said chamber.
25
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And, said piston-chamber combination may comprise a transition between said
convex shaped wall and
said parallel wall, where said transition may be comprising at least a concave
shaped wall, which may be
positioned near a second longitudinal position.
And, said piston-chamber combination may comprise a concave shaped wall which
may be positioned at
least on one side to a convex shaped wall.
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The various embodiments described above are provided by way of illustration
only and should not be
construed to limit the invention. Those skilled in the art will readily
recognize various modifications,
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
5 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,
10 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.
15 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
20 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.
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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,
so that the "hesitation
moment" for each of said 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 longitudinal 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 referent "19620"), in order
to synchronise the
force of each of said actuator pistons to said main axle.
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The feasibility study until now did not incorporate quantitatively the lack of
heat
generated by a motor of the 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 heat 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
10%, namely 8,75%, by the self-propelling actuator piston, and this is up to
now unprecedented (
David JC 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 regenerative
braking devices, than the total
used energy still may end under 10%.
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19618 amended 19611 added matter to the description ¨ feasibility study
The feasibility 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-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 H2), from a flywheel or from
regenerative 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. 11F 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, 1600cc, weight 836kg, with a 53 kW
/
71 pk gasoline motor, comprising 4 cylinders of each or 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 weight 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 luggage.
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The chamber of the pump shown in W02008/025391 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 0 58mm ¨ 017mm, respectively. Using an inflatable ellipsolde 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: 2'd
1 st longitudinal positions) to approx. 0 bar
(stroke: 1st
2nd 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 independent 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 3Y2 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
V2= 4/3 x 3,14 x 12,553 (025.1mm; P2=0,35 N/mm2)= 8280 mm3 to V1= 4/3 x 3,14 x
23,453 (0
46.9mm; P1=0,05 N/mm2) = 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: L1=302,78 ¨ 86,57= 216,21, Ar=
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 L1 is:
Wisothermal = -P V iln(P2/131)= 0,35 x 54015 x In 7=0,35 x 54015 x 2,302585 x
log 7 = 36788 Nmm/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
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
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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 3600 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
10 kW ¨ this may be enough to drive a VW Golf Mark II 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
15 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
20 energized. We use the principle shown in Fig. 11F 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
25 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 (0 25,1 mm) with a
medium internal pressure
30 (3,5 Bar) to a bigger sphere shape (0 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
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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 (0 46,9mm; 0,5 Bar) of the actuator piston to its
production shape (0
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 (0 25,1 mm, 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:
Wisothermal = 431V1In(P2/P1)= -1(check this) x 4/3 x 3,14 x 12,553 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.
(* P2 absolute is 4,5 bar, if P1 = 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 Umin, 2,2kW, 8 Bar, pressure storage vessel 100 I. We need the power, but
at a lower pressure,
so that this modified compressor is a bit quicker charging the pressure
storage vessel.
P = 2200 W for 8 Bar, hence for 31/2 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.
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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 24cc
/ 66cc (VW Golf
Mark II has motor of 53kW, 1600cc, 0 90mm, 4 cylinder ¨> 825W is approx. 24cc,
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.
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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 driveshafts.
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 may be 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).
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19617 optimal configuration of chambers for actuators in 19618
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 first 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 force 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
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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.
5 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 1/3
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
10 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
15 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 be
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,[1) may vary during the stroke from a 2nd to 1st
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; u= the
friction coefficient between the wall of the chamber and the flexible wall of
the actuator
piston],
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= 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(1.1)= the friction
force between the wall
of the chamber and the flexible wall of the actuator piston],
= the velocity v(T,F) should be optimised with the length L of said chamber
[where v=speed of
the actuator piston relative to the chamber; cp=angle between the wall of the
chamber and the
centre axis of said chamber; F= force from the piston rod],
= the energy used is as less as possible ¨ thus: the pressure drop (AV)
when the actuator piston
is moving from a 2nd 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
lubricators like
Superlube which has a much smaller friction coefficient than other lubricant,
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 ¨
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19617 thermodynamical issues in 19618
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
circleround 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 heat 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. 11A-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 heat
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. 11A-C, 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, 12A-C, 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
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fact an enclosed space of said actuator piston, both compression and
pressurisation will take place
in said chamber by changing its volume, so that heat and cooling may
balancing: this may be the
case with the combination of a non-moving actuator piston and a moving
(rotating) chamber (Fig,
13F-G). Again, now with thermodynamic's aspect, is this the most efficient
motor principle,
because the (theoretical) efficiency may be near 100%.
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19617 amended 19615 energy sources working together with the motor in
19618/19627
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,
CO2, 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 H2, or air compressed by
potential hydroenergy etc.
An H2 fuel cell may be 'charged' with H2, 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 continuously 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 H2 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 fossil fueled burner, or a compressor driven by a motor, burning fossil 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. H2 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
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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.
5
Preferably may a movable power source (e.g. a battery, a fuel cell, an
electrolyses
of H20 resulting in available H2 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
10 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
15 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
20 well be 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 n't noisy ¨ this contrary the
traditional method when a
combustible (fossile) motor is communicating with a alternator ¨ the e.g.
necessary H2 may be a
25 security hazard, and storage of H2 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 H2 for own use.
However, after having seen in 2009 a moped, with a combustible motor (<50cc),
using H2 from
instant electrolyses of water, said water being contained in the tank where
normally gasoline was
30 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
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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 H2, may be used to charge
said battery, of
which generated electricity may be used for the motor functions. 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
H2, 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 eletrolyses process for
generating H2 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. H2 as fuel.
In another configuration, where said pump is used for a repressuration 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 mentione 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
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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.
The tank, comprising conductive water may be filled up from an external
storage of water, and, if the
water is not conductive, it may be possible to add conductive material, so
that the water is becoming
conductive.
The pressure storage vessel may be pressurized, not only by a cascade of
pumps, but optionally also
from an external pressure source, by a pluggable connection (ref. 2701 in the
respective drawings).
The battery may be charged, not only by an alternator, solar cells or/and the
H2-fuel cell, but optionally
by an external electric power source, through a pluggable connection. ( ref
2700 in the respective
drawings).
The piston and the chamber may rotate both around the middlepoint around which
the chamber is
rotating.
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invention may be constructed with lighter weight than those based on the
classic piston-cylinder
combination.
For at the motor may function in the dark, a complement or addition to the
solar cells
may be necessary. This may be e.g. any other sustainable power source e.g. a
fuel cell, e.g. of a H2 type
which reacts with the 02 of the atmosphere, and giving electricity and H20.
This fuel cell may need
a relative small storage vessel, which may be of reduced pressure. This is to
say, that the
distribution system for h2 may be at home, or that the distribution system may
be not very dense.
In the motor type where an enclosed space is communicating with a
repressurisation cascade of
pumps, the electricity may be used to give energy to electric motor, which is
driving the piston
pump through another crankshaft - this may be done as a complement to the
energy of the solar
cells, e.g. when it is dark, or this may be done at any time.
Additionally may a generator been added to this motor type, which may be
driven by the main axle,
and which may load the accumulator.
In the motor type where the fluid in the enclosed space has been separated
from the repressurisation
cascade, possibly ore electric energy may be needed, for the control of
valves. This may 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 11F. and Fig. 13F, which may be needed for the repressurisation of the
pressure vessel 1063, and
889, respectively. This may be done by a cascade of pumps, of which at least
one is communicating
with the main axle, and at least one with an external power source. The pumps
may communicate
with a pressure vessel. For the solution in Fig. 13F may a pump also be
sufficient.
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19617 gearbox - clutch in 19618
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 may be half of the
above mentioned, in
order to generate the same power, with the configuration according the
feasibility study. This
reduced speed would suit the motor according this invention.
A reduced speed would limit the impuls 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 Doorne'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 functional 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: 0 0,65m (VW Golf Mark II),
- motor idle speed: 350 ¨ 400 rpm ¨ motor driving speed: 2x idle speed.
Thus:
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60 km/h: motor: 750 rpm
wheels: 490 rpm thus: gear ratio: 1:1,5 down
90 km/h: motor: 1000 rpm
5 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
10 140 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
15 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
20 gear down again.
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19617 motor sound in 19618
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 first
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
repressuration 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 ugly.
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 ugliness.
In the design according this invention will preferably the speed of the fluid
be lower than the speed
of sound, optionally will a shock 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).
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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 pressure 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
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19627 SUMMARY OF THE INVENTION
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, whick is communicating
with said first chamber through a channel comprising a longitudinal
cross-sectional section o 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 defined
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 each other by
common 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. W0/2008/025391, where the smallest part of
the
chamber was 0 17mm.
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
ergonomical height, so that pumping is comfortable for the user
(WO/2008/025391).
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A spring-force operated piston, e.g. a flexible expandable inflatable
container
piston (e.g. EP 1 384 004 B1) may begin to move by itself from a second
longitudinal
position to a first longitidinal position in said chamber, where the cross-
sectional area and
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 parallellity 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 B1 shows chambers, where in the top
(first
longitudinal positions) and the bottom (second longitudoinal positions) of the
chamber a
Is
part of the inner wall of said chamber is parallel to the central axis: thus
there where the
piston rod 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 parallellity
in EP 1 179
140B1
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 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 chamner on a
certain
ergonomical height, so that pumping is comfortable for the user
(WO/2008/025391).
If said bottom part is hollow, it may be used it in tree ways.
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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
5 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, or
the piston
10 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 inner walls are positioned at least between two common
borders.
Preferably may said hollow part be used as an additional pumping volume of
said chamber
, and the piston should be able to move toward and in said bottom part 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 move,
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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
Thus, 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 longitudinale 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 usefull for a proper pumping at high pressures.
The positions of said common borders are in both cases (the bottom part 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.
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The fourth chamber is just the basic chamber with its chacteristic shape, and
nothing more.
Said chamber may have an exit which is a nippel.
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.
The piston may be engagingly movable relative to said chamber wall.
The piston may be scalingly movable relative to said chamber wall
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19616 ¨ added matter to the description of 19620 in 19627
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 fa 27
mm, so that the working force at 8 Bar is: F = p x 0 = 0,8 x 0,25 x 3,14 x 272
= 458 N. At 10
Bar this is: 572N
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 10
Bar, when the fa
17mm 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.
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19617 ¨ added matter for 19620 elongate conical chamber design in 19627
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
to 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 Võ , which is defined as the volume
of said chamber at a
position Lõ , Lõ measured from the overpressure side of said piston to e.g. a
farthest away second
longitudinal position (0-point), where there is an overpressure Põ , the
overpressure Põ is counted in
relation to a standard pressure, e.g. the atmospheric pressure, used in this
calculation:
Võ = 3,14.[0,00046. Sx3 +(1,118-0,00139.L). Sx2+ (900-2,236.L +
0,00139.L2).Sx]
where:
Vx is the rest volume at Fix= z Bar over standard pressure, where Võ = Vo /
(z+1).
Vo = is the total volume of said conical chamber, where S = L = the total
length of said conical
chamber.
Sõ = a step in the iterative calculation process.
The longitudinal positions where Põ = 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 3'd 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 Sõ is found from said equation, and gives the x-coordinate of said
dot, as S.L.
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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.
5 The y-coordinate of said dot is found as follows.
If a certain maximum working force Fma. has been chosen, than the position of
said dots at a certain
longitudinal position L. at the centre axis, from a chosen 0-point, can be
derived as follows:
D. = Fmax 0,008 . P. (P. in Bar, D in mm, F in kgf)
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.
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19622 a deformable fluid
The use of fluid within the actuator piston may be as follows:
1. a gaseous medium, such as air or N2: preferably for the CT pressure
management system,
2. a combination of a gaseous and a liquid,
to 3. a liquid, which may be hydraulic oil or H20: preferably for the ESVT
pressure management
system.
The use of a liquid may give a better economy for the pressurazation of the
actuator piston, as by
moving a volume of liquid to and from the actuator piston by the pump, no or
only a bit heat and
cold, resp. may be generated ¨ contrary the (de)pressuration of a gaseous
medium.
And, the reduction of the pressure of a gaseous medium, which takes heat, may
result in icing of the
wall of the actuator piston. This will affect also the lubrication of said
actuator piston with the wall
of the chamber, thus may affect the efficiency.
Because a liquid cannot be compressed, may the increase of the pressure taking
place at the very
last part of the traject of the piston of the pump. This works fine with a
quickly rotating camshaft or
crankshaft, as shown in e.g. Fig. 90L.
Thus, a liquid as deformable fluid may be preferred when using the Enclosed
Space Volume
Technology.
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19630 circular chamber design SUMMARY OF THE INVENTION
The circular chamber shown in Fig.! 3C and 14D, where a chamber may be 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 sub-chambers, on the
chamber wall may be identical. This, to avoid unnecessary friction, which
would decrease efficiency,
and add to wear of the pistons. The chamber may have a constant circular
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 said sub-
chambers is bigger than that of one chamber, having the same circle as centre
axis. Thus the force
of each chamber is bigger, than if onely 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
lying 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 are lying around a
centre axis of the chamber,
which may be a circle.
SM ¨ PVT1
In a final version, we expect 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 (9,11,13,15,17,19,21,23,25,27) 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
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said chamber on said chamber wall is independent of the position of said
actuator in said chamber,
and thus independent of the inside pressure of the actuator.
SM - PVT2
A chamber (with the above mentioned characteristics) is engagingly and/or
sealingly
moving over said sphere shaped piston (Fig.10H 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
corner ¨ both front wheels
to 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 boundery
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 thus 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 may be parallel to an axis through a
centre point of said
chamber, perpendicular the cross-sectional section of said chamber.
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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 somewhat 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 figures Z.2 etc. The
vector function for the base circle is standard: 3432.
(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, /] we define a circle, which will eventually trace out the full
chamber and thence also that part of the piston which has chamber-
wall contact. These circles have radii p(u) which depend on the base
circle parameter u E [0, Lb 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
32F1324-afrot321-1 figures 6, 7, and-8: 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 a and p in the Maple appendix and used
for illustrations in this report):
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(1.2) p(u) = a = u + /3 .
The parametrized Fermi tube surface with radius function p(u) which
is 'bent' around the base circle is then given by the vector function:
(1.3) r (u, v) = 'y(u) + p(u) = (cos(v) - ei (u) + sin(v) = e2(u))
,
where e1 (u) and e2 (u) are orthogonal unit vectors which span the or-
thogonal plane to the base circle as shown in figure 1:
1 ei (u) = (cos (u R), sin(u/R), 0) ,
(.4)
e2(u) = (0, 0, 1) .
The parametrized Fermi tube solid with radius function p(u) which
is likewise 'bent' around the base circle is then:
(1.5) F(u, v, w) = 7(u) + w = p(u) = (cos(v) - e1 (u) + sin(v) = e2(u)) .
Note that the surface is obtained from the corresponding solid simply
by setting w = 1:
(1.6) r(u, v) = F(u, v, 1) .
The volume of the Fermi tube solid (corresponding to the turning
angle interval [0, L]) is determined by
1 71-
(1.7) Vol = f v, w) du dv dw ,
w=o u=0
where the Jacobi function integrand is given by the partial derivatives
of F as follows:
(1.8) .7(u, v, w) = 1 ffu x FO=Flw I .
The area of the Fermi tube surface is (corresponding to the turning
angle interval [0, :
(1.9) Area =j .4 J (u, v) du dv
4=o ,
v=¨Ir
where now the Jacobi function integrand is:
(1.10) J(u,v)=Irxr,I.
The Maple output appendix contains an example of the calculation
of the respective tow 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 any other choice of geometric descriptor values.
The total area and total volume includes the values from the end
caps which we now discuss.
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PISTON AND CHAMBER 3
2. THE END CAPS
We assume that the end caps are spherical. This is not absolutely
needed. What we need 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 it and F
22.D 32-6
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 same 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 Ansatz of spherical caps.
The area of the cap with height h and base radius a is (see figure 3):
(2.1) A (h, p) (a2 h2)
The volume of the cap with height h and base radius a is
(2.2) V (h, p) = ¨1 = r = h = (3a2 + h2) .
6
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) r(u) = p(u) = .11 + (p' (u))2 .
In the tube geometry the values of a and h are determined only by
the radius function p(u) and its derivative p' (u) at the u end-values
u = 0 and u = L respectively; the base circle radius plays no role!
a = p(u) ,
(2.4)
h = p(u) (V1 _________________ + (p' (u))2 ¨ p' (u)) .
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
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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 around 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
- 3 2 tl Citt9 8, 9-, 19, 11, 12, and 13 below. Hence the resulting sliding
force is pro-
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 wall 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-
ber, 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.
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19640 SUMMARY OF THE INVENTION
EP 1179140B1 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 0-ring, which is
sealingly 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 0-
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 filly developed
aspect is a proper
assembling of the 0-ring to said support means. And, a proper assembling of
said support means
to a means which is keeping the 0-ring in place between the assembling points
of said support
means to said 0-ring.
There may be two preferred 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 bot avoid)
the change of shape of said sheet, when pressurized. And, additionally, a
shape change of said
sheet may additionally 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
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production size, when the piston is not at a second longitudinal position. A
third force may be
pulling the 0-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
reinforcements, 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 2D, 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 reinforcement layer of said sheet positioned closest to the
high pressure side of
said sheet, and another layer without reinforcements may be vulcanized on the
first mentioned
layer. The production thickness of each layer may be so thick, that the
decreased thickness at a
first longitudinal position may be enough for a longduring proper functioning
of said piston.
Also the 0-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 0-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 0-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 0-ring better
in place. Both ends
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of said rod may be sliding between two adjacent support means, while two rods
may slide along each
other through a support means.
5
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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
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 at a 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 posirtion. 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 B1). 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 PU-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
Polyurethan Foam.
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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 said
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 sandwich 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 sandwich 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 said stiffener having an increased thickness.
Said Memory Foam material is quickly regaining its original size when
released,
after having been depressed, at normal working temperatures, such as 10 -
100c C. At lower
temperatures such as around the freezing point, it takes longer time, and that
may be too long, in
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order to comply to the demand of engagingly and/or sealingly connected to the
wall of the
chamber. It may be necessary that said stiffeners are being made of a spring
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 end of 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.
to
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 be
preferably made of Polyurethane), has become unstuck, so that its function is
lost.
In order to avoid that said stiffeners are becoming instuck another measure is
to
increase the thickness of the long end of said stiffeners, close to where
pressure is obtained from
the fluid under 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. Thus may need the size
of said layer
having 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
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(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
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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
5 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 reinforcement 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
10 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 independent claim.
15 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
20 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
25 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,
30 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
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have a certain pre-loading, so that the foam will be widened when the piston
is moving from a 2nd to
a 1st 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
1St longitudinal position of the chamber.
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19660 SUMMARY OF THE INVENTION
EP 1 179140 B1 shows an inflatable container piston type, while EP 1 384 004
B1 shows that
this piston type should have an unstressed 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 1 384
004 B1 shows that a reinforcement for such a desired behaviour may be a layer
where the
reinforcement strings are laying parallel besides each other in an unstressed
production model, and
these strings are connecting the two end parts, of which one is mounted on the
piston rod, while the
other can glide of the piston rod ¨ the rubber is directly vulcanized on both
ends. The reinforcement
layer is the inner layer, while another, thicker layer than the layer with
reinforcement strings, is
protecting said reinforcement layer. Both layers are being vulcanized on each
other, and at the end
parts, there may be another extra layer on top of the two. The function of the
second layer is
additionally to avoid that the reinforcement strings are '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. Having 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 017 mm (2"
longitudinal position) to
an 0 59 mm (1st longitudinal position). With two reinforcement layers on top
of each other with a very
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
compatible so,
that these can be vulcanized on each other, without getting lose from each
other under normal working
conditions.
It was observed that when the ellipsoide 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 may not be
reached and neither an expansion to 330%, only an ellipsokle 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
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chamber at a second longitudinal position is not parallel to the centre axis.
Just the wall of the chamber
is free of the wall of the container in said unstressed production state.
10
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19660-1.2 Update on the functioning of actuator piston
The actuator piston is comprising a container, said container is comprising a
wall around a cavity,
said cavity may be inflatable and pressurized by a fluid and/or may comprise a
foam, said container
is moving from rd to 1st longitudinal positions of the chamber, when
pressurized, in a 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
1.0 longitudinal position being smaller than the cross-sectional area and
circumferential length at said
first 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 may be 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, t = wall
thickness of the actuator piston), specifically when t/R<<<,
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When said actuator piston is being positioned in a wall of a chamber having an
positive angle with
the centre axis of said chamber in the direction from a 2nd to a 1St
longitudinal position, an
asymmetry arises in the reaction forces from the wall of said chamber, because
there will be no
5 reaction forces on chamber positions nearest a 1st longitudinal position
of the chamber on the
ultimate position nearest a 1St longitudinal position part of the contact area
(wall chamber ¨
container), 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
he wall of said container ¨ the wall of said conatiner of the actuator piston
is rolling over the wall
10 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, thus also the
friction forces. A
15 movement of said actuator piston towards a 1st longitudinal position may
occur (sliding). This may
reduce said contact height, because the portion of said wall of the container
nearest a 2nd
longitudinal position may reduce its circumference, and thus also that of the
contact area nearest a
2nd longitudinal position.
20 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 nearer a first longitudinal position, until said asymmetry of
forces occurs again,
whereafter the cycle may start again.
25 It is the ability to increase (= rolling) a contact height in a
longitudinal cross-section of the engaging
wall of the container and the wall of the chamber, thereby making the height
in immediate
continuation of the existing height larger, that is the main reason of the
behaviour of the actuator
piston.
30 The means to do so may be for e.g. an ellipsoid shaped actuator piston:
= 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,
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= 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
continuously 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, thereby 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 between the wall of the container and the
wall of the
chamber again is decreasing.
The actuator piston will stop running towards a 1st 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 1st 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 2nd to
1st longitudinal positions, is additionally forcing the contact area of the
wall of said actuator piston
to the wall of the chamber nearest to the 1st 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 1st longitudinal position,
thus 'ahead' of the
container in the direction of the movement, even the pressure is low, the
movement is smoothly.
The reason may be 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.
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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 wall of said container
is convex shaped,
flexible, while the several different area's are positioned in continuation of
each other.
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19660-2 inflatable piston ¨ strength and stiffness
The inflatable piston of the type where an ellipsoYde at a 2" longitudinal
position of a
chamber is becoming a enlarged ellipsokle / (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 4:5H is expanding the wall of the cylinder. The size of said
Hoop stress
aff 1 is in general approximately 10x the size of the internal pressure in
said cylinder2. This is the
reason why a the actuator piston already at a low internal pressure is
rocketing from a 2" to a 1st
longitudinal positions in a cylinder according section 19620 of this patent
application.
The size of the Hoop stress o'H 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
- 2" longitudinal position / 0 17mm: is approx. 3x the internal pressure in
the piston,
- 1st longitudinal position / 0 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 os3 which applies, can be compared with the longitudinal
stress at
of a cylindrical cylinder, which is half of the size of the Hoop stress GH .
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 Cx = [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
(NH = pRit p= internal pressure, R= 1/2 diameter of the cylinder, t= wall
thickness of the cylinder.
2 Strength and Stiffness of Engineering Systems, Frederick A Leckie, Dominique
J. Dalbello, Springer, 2009
ISBN: 978-0-337-49473-9
3 as = pRi2t p= internal pressure, R= 1/2 diameter of the sphere, t= wall
thickness of the sphere.
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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 for a
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 = 100, thus sin 100 = 0,174, while we
keep a cylinder 0=
81mm, at a 1St longitudinal position ¨ this gives ei 53,7mm at a 2"
longitudinal position, and a wall
thickness of the actuator piston: 3.5mm ¨ pressure at a 2nd LP = 10 Bar, at a
1st LP = 2,25 Bar.
CI = R/t [1 - t/R ] = 10,6 aH2 = 24 N/mm2 4Fpropuigjoni = 2125N
C2 = R/t [1 - t/R ] = 6,7 aH1 = 67 N/mm2 F propulsion 2 = 3933 N
Conclusion: it is possible to use a motor according to this invention, which
has approximately the
size of a current petrol motor.
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19680-2 ¨ 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
circumference of said
5
piston is having a production size of that of the circumference of the 2"
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" to a 1st longitudinal
position is done solely by
means of the internal pressure of said piston, having a continuous outside
wall of said piston, a
10
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 st 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
15
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 --
20
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 area
between the wall of said chamber and the wall of said piston may be restricted
("dis continuous") to
a certain area of the wall of said piston, and that may be done at least in
two ways:
25
= the contact area may be a separate part of the wall of said piston - it may
expand 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.
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The Hoop stress in the wall of a inflatable container type piston (please see
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 1st to a 2nd
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 press= 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 N2) 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 1-1Y2 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. 1 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 first
to a second longitudinal position, to said enclosed space (e.g. W02010/094317
or
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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 exorbitant
swallowing up of
the wall of the piston when inflated, and a foam, preferably an open cell
foam. The open cells may
be containing 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 would 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 2"1 longitudinal position.
Thereafter a fluid is injected
into the cavity of said container, when it is at a 1st 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 contianer 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
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foam, comprising open cells. This shrinkage may be compensated by a very small
increasing of the
pressure of the medium in said open cells, or 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 wall of said container piston, in order to get the wall
to its originally planned
position.
The separate wall part of a piston is 'sticking out' of the wall of the piston
- it has thereby a bigger
circumference that the rest of the wall nearby, while the transition of
circumferences from the wall of
said piston to the separate part is more or less abruptly or stepped.
The contact area of said separate part with the wall of said chamber may be
small - this may be done
by choosing the right shape of the separate part, e.g. circle segment, wherein
the top of said segment is
having contact with the wall of the chamber.
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207 SUMMARY OF THE INVENTION
In general, a new design for a combination of a chamber and a piston for e.g.
a pump must
ensure that the force to be applied to operate the pump 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 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 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 area 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 tyre. 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, the volume of air
provided will depend on the area of the piston. However, in order to compress
the air, the first
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translation of the piston will be relatively easy (the pressure is relatively
low), whereby this may be
performed with a large area. Thus, totally, a larger amount of air may be
provided at a given pressure
during a single stroke of a certain length.
Naturally, the actual reduction of the area may depend on the intended use of
the combination
5 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.
10 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
member,
15 - elastically deformable means, supported by the supporting members,
for sealing against an
inner wall of the chamber,
the support members being rotatable between 100 and 40 relative to the
longitudinal axis.
20 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 wall of the chamber
Another technology is one wherein the piston comprises an elastically
deformable container
comprising a deformable material.
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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.
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 with the deformable
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 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.
Also, the first cross-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 95-105, 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.
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An optional or additional technology is one wherein 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.
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:
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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 wall of the chamber
the support members being rotatable between 100 and 40 relative to the
longitudinal 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 a 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 common 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 means 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 defmes 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,
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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
deformable material.
Thus, 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.
to
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 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. In one 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 situation, 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 be preferred to provide means for defining the volume 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 sealing.
A simple manner would be 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
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longitudinal position of the container. In this situation, a simple piston
between the two pressures may be
provided (in order to not loose any of the fluid in the deformable container).
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 of 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 sealing between the container
and the chamber
wall, it is preferred that an internal pressure, such as a pressure generated
by a fluid in the container, 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 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.
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
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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 longitudinal 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 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
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 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".
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One type of piston, which may be used in this type of combination, is the one
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 wall of the chamber.
Another type of piston is the one -comprising an elastically deformable
container comprising a
deformable material.
Another aspect of 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 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. The fact that the material is resilient will provide the
problem of deformation of the
piston and, if the pressure increases, lack of sealing due to the resiliency
of the material. This is
especially a problem if the dimension changes required are large.
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In the present aspect, the resilient material is supported by a helical flat
spring. A helical spring
is able to be expanded and compressed in order to follow the area of the
chamber while the flat structure
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
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 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 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.
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Thus, alternatively to the combinations where the piston adapts to the cross-
sectional changes of
the chamber, this aspect relates to a chamber having adapting capabilities.
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.
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 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
function of the combination.
Naturally, the present combination may be used for a number of purposes in
that it primarily
focuses 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
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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 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 PCT/DK96/00055 (including the US Continuation
in Part of 18 April
1997), PCT/DK97/00223 and/or PCT/DK98/00507. 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 lcarpump' for
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,7J, 12A-C may be
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 Fig. 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 be
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.
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Through these embodiments, reliable and inexpensive pumps optimized for manual
operation,
e.g. universal bike pumps to be operated by women and teenagers, can be
obtained. The shape of the
walls of the pressurizing chamber (longitudinal 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 molding, from taper swaged tubes etc.
In a piston pump a medium is sucked 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 valve
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 compressible medium can be compressed by the movement of the chamber
and/or the piston.
In the case of a non-compressible medium is inside the chamber, e.g. the
piston may be equipped 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.
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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
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 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.
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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.
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The various embodiments described above are provided by way of illustration
only and should not be
construed to limit the invention. Those skilled in the art will readily
recognize various modifications,
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 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.
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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
from the first to the second longitudinal position of the chamber.
Preferably the second cross-sectional 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 rotatably 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 100 and 40 relative to
the
longitudinal axis.
According to an embodiment of the invention there is also 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,
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
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embers against an inner wall of the chamber.
Preferably the piston comprises an elastically deformable container 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, 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 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
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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 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
to 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,
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.
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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 wall of the chamber the support members
being rotatable between 100 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 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-
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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 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, 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
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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,
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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 deformable 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 deformable 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 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.
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
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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 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.
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.
Preferably 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 pump 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
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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
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 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.
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.
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Preferably the actuator further comprises a fluid exit connected to the
chamber
and comprising a valve means.
Preferably the actuator further 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
translation of the piston into a rotation of the crank.
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207-1 SPECIFICALLY PREFERRED EMBODIMENTS
According to an embodiment of the invention, there is provided 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, 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
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 cross-sections of the different
cross-sectional areas have different cross-sectional shapes,
the change in cross-sectional shape of the chamber (162) being
continuous 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 cylinder (162) at the
first longitudinal position thereof amounts to 80-120% of a
second circumferential length of the cross-sectional shape of
the chamber (162) at the second longitudinal position thereof.
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Preferably is 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 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 is 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
substantially elongate, such as lobe-shaped, parts.
Preferably is a
first circumferential length of the cross-sectional shape of
the cylinder (162) at the first longitudinal position thereof
amounts 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
Preferably is the first and
second circumferential lengths are at least substantially
identical.
Preferably is the
cross-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
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Preferably is 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
thereof.
Preferably is the cross-
sectional area of said chamber (162) at the second longitudinal
position thereof is 95-70% of the cross-sectional area of said
chamber (162) at the first longitudinal ttosition thereof.
Preferably is the cross-
sectional area of said chamber (162) at the second longitudinal
position thereof is approximately 50% of the cross-sectional
area of said chamber (162) at the first longitudinal position
thereof.
According to an embodiment of the invention there is also provided
a pump for pumping a fluid, the pump comprising:
a combination according to any of the preceding claims,
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).
Preferably are 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
longitudinal position of the chamber (162).
Preferably is 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
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position where the piston means is at the first longitudinal
position of the chamber (162).
According to an embodiment of the invention there is also provided
a shock 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
position where the piston means is at the second longitudinal
position.
Preferably a shock absorber which is further comprising
a fluid entrance connected to the chamber (162) and comprising
a valve means.
Preferably a shock absorber which is further
comprising a fluid exit connected to the chamber (162) and
comprising a valve means.
Preferably is
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
first to the second longitudinal positions of the chamber
(162).
Preferably a shock absorber which is
further comprising means for biasing the piston means toward
the first longitudinal position of the chamber.
According to an embodiment of the invention there is also provided
an actuator comprising:
a combination according to any of claims 1 to 9,
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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
and the second longitudinal positions of the chamber.
Preferably is an actuator which is further comprising a -
fluid entrance connected to the chamber (162) and comprising a
valve means.
Preferably is an actuator which is further comprising
a fluid exit connected to the chamber and comprising a valve
means.
Preferably is an actuator which is further
comprising means for biasing the piston means (76, 163) toward
the first or second longitudinal position of the chamber.
Preferably is an actuator which is wherein
the introducing means comprise means for introducing
pressurised fluid into the chamber (162).
Preferably is an actuator which is wherein
the introducing means are adapted to introduce a combustible fluid,
such as gasoline or diesel, into the chamber (162), and wherein
the actuator further comprises means for combusting the
combustible fluid.
Preferably is an actuator which is further
comprising a crank adapted to translate the translation of the
piston means into a rotation of the crank.
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653 SUMMARY OF THE INVENTION
In the first aspect, the invention relates to a combination of a piston and a
chamber, wherein:
the container is made to be elastically expandable and to have its
circumpherical length in the
stressfree and undeformed state of its production size approximately the
circumpherential length of the
inner chamber wall 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
first cross-
sectional area. In certain situations, the second cross-sectional area is
approximately 50% of the first
cross-sectional area.
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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.
to The deformable material may also be spring-force operated devices, such
as springs.
Thus the container may be 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 circumpherencial 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 length and to contract it when moving in the opposite
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 level 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 be a possibility to keep this
pressure, e.g. by using a valve
for inflation purposes. In the case when spring-force operated devices are
being used to obtain the
pressure, a valve may not be necessary.
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When the cross-sectional area of the chamber changes, the volume of the
container may
change. Thus, in a cross-section through the longitudinal direction of the
chamber the container may
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 may be 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
further 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 the container due to leakage e.g. through
the wall 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 the wall
of the container expands when the piston moves to such a big cross-sectional
area at the first 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 that a pressure raise
may be communicated to the first enclosed space and the container, despite the
fact that the volume of
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the container and thus the second enclosed space may become bigger as well.
This may be achieved by
e.g. a combination of a piston and a chamber (the second enclosed space) with
different cross-sectional
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 this situation, a
simple piston between the two pressures may be provided (in order to not loose
any of the fluid in the
deformable 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
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 communicate with a valve for inflation. When the piston does not have an
inflation valve, the fluid
may be non-permeable for the material of the 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
friction to and from the first closed chamber. When the piston does have an
inflation valve the wall 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
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valve has a spring biased valve core pin and closes independent of the
pressure in the piston, and all
kinds of fluids may flow through it. It may however also be another valve
type, e.g. a check valve.
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-documents 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 inflated automatically.
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 actuator 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 turning around 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.
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Obtaining the predetermined pressure in the container may be achieved manually
- the operator
being informed by a pressure gauge e.g. a manometer which is measuring the
pressure in the container.
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
pressure 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 99/26002 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
deformable container wall.
Expansion or contraction of the container wall which is initiated by the
changing size of the
circumpherential 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 length
(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 wall 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 vulcanized within e.g.
two layers of elastic material, e.g. rubber. When the container has its
production size, not only the
elastic material of the wall, but also the reinforcement is stress free and
undeformed. Expansion of the
reinforced wall of the container means that the distance between the crossings
(= stitch size) may
become larger as the threads expand, while contraction makes the stitch size
smaller as the threads
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contract. The sealing of the wall of the container to the wall of the chamber
may be established by
pressurizing the container to a certain pressure. Hereby will the threads
being expanded a little bit so
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 bended loops of the
lcnittings. 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 size 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 oven is closed, and steam of over 100 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. In 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 analogous with the above
mentioned ones
regarding 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
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inflatable, connected to the wall of the container. When inflatable, the
reinforcement functions also to
limit the deformation of the wall of the container due to the pressure in the
chamber.
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 axis,
the piston being movable- in the chamber at least from a second longitudinal
position to a first
longitudinal position,
the chamber having an elastically deformable 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 to a chamber having adapting capabilities.
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.
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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.
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 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 longitudinal position thereof and another at a second
longitudinal 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 cross-sectional area is at least 2%, such 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%, such at least 95%
larger than the second cross-sectional area.
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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
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 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
eircumpherencial length of
the first longitudinal position of the chamber, having a reinforcement type
which allows contraction with
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 the second longitudinal position of the chamber, having a
reinforcement type of the skin which
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allows parts of the wall of the container having different distances from the
central axis of the chamber
in a longitudinal cross-section of the chamber may also be used.
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
functioning of the combination.
The piston may also slide over an internal and 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
focuses 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 connected to the chamber may
provide pumps, motors,
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 not 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 decisive for the type
of application: pump,
actuator, shock absorber or motor. In a piston pump a medium may be sucked
into a chamber which
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may thereafter be closed by a valve arrangement. The medium may be compressed
by the movement of
the chamber and/or the piston and thereafter a valve may release this
compressed medium from 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 compressible medium may be
compressed by the
movement of the chamber and/or the piston. In the case a non-compressible
medium may be positioned
inside the chamber, e.g. the piston may be equipped 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 pneumatic and/or
hydraulic applications than
the above mentioned piston pumps.
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.
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
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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 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, in the 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 (ergonomical)
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.
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 different
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.
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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.
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 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.
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 set 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
it may be possible to transport a MPU by parachute, as the construction of
devices based on the
invention may be constructed with lighter weight than those based on the
classic piston-cylinder
combination.
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The various embodiments described above are provided by way of illustration
only and should not be
construed to limit the invention. Those skilled in the art will readily
recognize various modifications,
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 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.
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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.
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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.
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.
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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.
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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.
Preferably 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 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.
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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,
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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 so
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 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, an outer annular disk and an inner annular disk abutted in
said central passage to
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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 running 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.
to 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,
derivable 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,
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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.
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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
longitudinal 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.
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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 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 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'.
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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 arranged as to the Trellis Effect.
Preferably is the reinforcement means comprising a flexible 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 and/or 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.
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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 dimension.
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.
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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.
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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.
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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 first 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 preceding 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.
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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.
20
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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 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, 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 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
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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 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 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 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.
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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 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 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.
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507 SUMMARY OF THE INVENTION
The valve actuator of the present invention and embodiments thereof are
subjects of
claims 1 and 2 to 17, respectively. A valve connector and a pressure vessel or
hand pump,
comprising a valve actuator of the present invention are subjects of claims 18
and 19,
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
operated core pin of a valve (e.g. a release valve), as well as in valve
connectors (e.g. 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 first end of the cylinder. In the piston's
second position, it is at
a second predetermined distance from the first 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 and/or
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 arranged 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 connect valves of different sizes to a valve actuator having
a single arrangement
for the enlargement of the diameter of the cylinder. Now therefore the number
of enlargements
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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
gaseous and/or liquid media between the cylinder and the part of the valve
actuator which is
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 around 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 the 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 pin of a
permanently mounted valve.
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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 prederrnined 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 predetermined 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.
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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.
.=='
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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.
Preferably 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.
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According to an embodiment of the invention there is also provided a valve
actuator in a stationary
construction, such as a chemical plant.
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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 any 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 being 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 tire, 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.
In a second aspect is the problem of non-compliance 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 optmized 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
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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
to
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, which
might prohibite 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 may be 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 bring 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.
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This is also valid for piston-chamber combinations with differing cross-
sectional areas and
equal of differing cicumferentival sizes.
The guiding means may be comprising a washer with a small hole with an
appropriate
fitting 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 the
combination.
The washer may come back to its default position by means of a sprong-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,
to
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 may be
flexible, turnable.
In 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 oi 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 arm, when no force moments would arise. This is obtained if the
longitudinal axis of
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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 1800. However, it may also be
different from 1800.
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
180 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 arm, the hand may be positioned in relation to the
arm, 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 ellipse. 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 may be 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 turn
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, or different than that.
The conical shape of the cylinder may provide a substantial reduction of the
size
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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,
- 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.
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 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
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resulting pressure to open the valve and a larger cross-sectional area to
force more fluid into
the tire (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.
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19597-1 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,
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
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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 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.
to 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 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.
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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 0-ring
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 off at 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 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, 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
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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 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 first 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.
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19627 BRIEF DESCRIPTION OF THE DRAWINGS
In the following, preferred embodiments of the invention will be described
with reference to the drawings
wherein:
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Fig. 1A 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 - the piston arrangement is shown at the beginning, and at the end of a
stroke - pressurized - where it has unpressurized its production size.
Fig. 1B shows an enlargement of the piston of Fig. lA at the beginning of a
stroke.
Fig. 1C shows an enlargement of the piston of Fig. lA at the end of a stroke.
Fig. 2A 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 unpressurized its production size.
Fig. 2B shows an enlargement of the piston of Fig. 2A at the beginning of a
stroke.
Fig. 2C shows an enlargement of the piston of Fig. 2A at the end of a stroke.
Fig. 3A shows a longitudinal cross-section of a chamber with fixed different
areas of the
transversal cross-sections and a third embodiment of the piston comprising a
fiber reinforcement (no 'Trellis Effect') with radially-axially changing
dimensions during the stroke - the piston
arrangement is shown at the beginning, and at the end of a stroke, where it
has
its production size.
Fig. 3B shows an enlargement of the piston of Fig. 3A at the beginning of a
stroke.
Fig. 3C shows an enlargement of the piston of Fig. 3A at the end of a stroke.
Fig. 3D shows a top view of the piston of Fig. 3A with a reinforcement in the
wall in planes
through the central axis of the piston - left: at the first longitudinal
position,
right: at the second longitudinal position.
Fig. 3E shows a top view of the piston of Fig. 3A with a reinforcement 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 longitudinal position.
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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, where the piston is beginning to expand ¨ the movable cab
is
moving toward the non-movable cab.
Fig. 5B shows the piston of Fig. 5A, instanteneously 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
instanteneously
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,
where 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
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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 rt longitudinal position.
Fig. 7A shows an enlargement of the piston of Fig. J.A 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
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Fig. 7D 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. 7E shows the pattern of Fig. 6D when the wall of the container
has been
expanded
Fig. 7F 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
lo Fig. 7G shows the reinforcement matrix of Fig 7F,
which has been expanded
Fig. 8 shows a combination where the piston is moving
in a chamber and around a taper wall
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Fig. 9A shows a longitudinal cross-section of a chamber with fixed
different areas of the
transversal cross-sections 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 beginning,
and at the end of a stroke where it has its production size.
Fig. 9B shows an enlargement of the piston of Fig. 9A at the beginning
of a stroke.
Fig. 9C shows an enlargement of the piston of Fig-. 9A at the end of a
stroke.
Fig. 9D shows the piston of Fig 9A just entering a conical part of the
chamber.
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Fig. 10A shows a piston-chamber combination where a pressurized
ellipsokle 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. 10B 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. 10C shows a piston-chamber combination as that of Fig. 1 0A,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 position or
during its return to the second longitudinal position, thereby changing the
size
of said piston, adapting it continuously to the size of the chamber, in order
to
avoid jamming.
Fig. 10D shows the process of Fig.10A, when the piston is a sphere type,
as produced
at a second longitudinal position.
Fig, 10E shows the process of Fig. 10B, when the piston is a sphere type,
as produced
at a second longitudinal position.
Fig. 1OF shows the process of Fig. 10C, when the piston is a sphere
type, as produced
at a second longitudinal position.
Fig. 10G shows the process of Fig. 10A, with the exception that the
enclosed space
has a decreasing size during the moving from the 2rld to the lst longitudinal
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position, so that the use of the pressurized medium per stroke is being
reduced.
Fig. 10H shows the comparable process of that of Fig. 10B.
Fig. 101 shows the comparable process of that of Fig. 10C.
Fig. 10J shows the process of Fig. 10D, with the exception that the
enclosed space
has a decreasing size during the moving from the 2nd to the 1st longitudinal
position, so that the use of the pressurized medium per stroke is being
reduced.
Fig. 10K shows the comparable process of that of Fig. 10E.
Fig. 10L shows the comparable process of that of Fig. 10F.
Fig. 10M 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 eircleround centre axis,
around the centre of the centre axle of said motor.
Fig. lON 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
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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. 11B shows schematically the controlling means and the pressure
management for
the motor of Fig. 11A.
to Fig. 11C shows some worked out mechanical assemblies of the
motor of Figs. 11A 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. 11A and 11B.
ENCLOSED SPACE VOLUME TECHNOLOGY
Fig. 11G 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. 11G, where a constant
repressuration of the
pressure storage vessel is done by a cascade of pumps, shown in e.g. Fig.
11A.
Fig. 111 shows a partially worked out one cylinder motor, based on the
concept shown
in Fig. 11H, where the velocity controller and the ES VT-pump
are being
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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. 11J left shows a scaled up of the left part of Fig. 11J.
Fig, 11J 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. 11H, where the ES VT-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. 1111; 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.
11K. 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. 11L left shows a scaled up of the left part of Fig. 11L.
Fig, 11 L right shows a scaled up of the right part of Fig. 11L.
Fig. 11M
shows a partially worked out one cylinder motor, based on the concept
shown
in Fig. 11H, where the ES VT-pump for the actuator piston chamber
combination now is being powered by a camshaft, said camshaft driven by an
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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. 11N shows a partially worked out two cylinder motor, based on Fig.
11M ¨ 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. 11N.
Fig, 11N right shows a scaled up of the right part of Fig. 11N.
Fig. 110 shows a partially worked out one cylinder motor, based on the
concept shown
in
Fig. 11K, where the ES VT-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 H2, 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.
110, where
the
ES VT-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 H20, said electrolyses powered by a battery; the pump
pump, which is re-pressurating the pressure storage vessel is directly driven
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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, 1113 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. 11K, where the ES VT-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 H20, 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. 11R shows a
partially worked out two cylinder motor, based on Fig. 11Q ¨
where the ES VT-pumps, one for each actuator piston-chamber combination,
are being powered by a camshaft, which is directly driven by the auxiliary
power from a gas (e.g. air) forced cooled combustion motor, using 112,
derived by the electrolyses of H20, 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 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.
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Fig. 11R left shows a scaled up of the left part of Fig. 11R.
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. 111- 11R with the main axle of the motor.
Fig. 11T shows a detail of the joint of the connecting rod of the actuator
piston and the
crankshaft on the main axle of the motor according to Figs. 111¨ 11R.
Fig. 11U shows a detail of the joint of the base of the piston-chamber
combination
1060 of Figs. 11I - 11R with the main axle of the motor.
Fig. 11V shows the mechanism driving a pump of Figs. 11H ¨ 11R, and its
base.
Fig. 11W shows the connecting joint between the two crankshafts of the 2-
cylinder
motor according to Figs. 11J, 11L, 11N, 11P, 11R.
Fig. 11W' shows an improved sealing between the crankshafts of Fig. 11W.
Fig. 11X shows the connecting joint between the two crankshafts of a 2-
cylinder
motor where the channels of each crankshaft are being separated.
Fig. 11X' shows an improved sealing between the crankshafts of Fig. 11X
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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 energi ed by solar
energy, including control means.
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.
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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 non-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 incl. a storage pressure vessel, where the
continuously changing internal pressures of said actuator pistons are
determined by a separate piston-chamber combination for each of said
actuator pistons, computer controlled.
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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 continuously 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.
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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
combination 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. 140 shows an enlarged detail of the cross-section of said piston
in said circular
chamber of Fig. 140, when the piston is at a second circular position.
Fig. 14H shows the configuration of Fig. 14E, 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 gear.
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SHORT DESCRIPTION OF PREFERRED EMBODIMENTS
Fig. 141 shows that part of the pressure management system which is
controlling
the speed of the motors, e.g. on which a wheel / propeller has been
mounted, when said wheels / propellers of a vehicle have different speeds
e.g. for wheels of a car, while turning around a corner.
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AUXILLIARLY POWER SOURCES
Fig. 1 5A shows a 1-12-fuel cell as electrical power source for
repressuration pump(s) for
pressurizing the pressure storage vessel, the necessary components and the
power lines.
Fig. 1 5B shows a combustion motor, using 1-12 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 run, which is communicating with (a) pump(s), for
repressuration of the pressure storage vessel.
Fig. 15C shows a combustion motor, using 1-12 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 1-12 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
repressuration of the pressure storage vessel.
30
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ESV'T ¨ CRANKSHAFT DESIGN ¨ MULTIPLE USE OF COMPONENTS
Fig. 16A shows a scaled up 2-way actuator of the Figs. 11G-
R.
Fig. 16B shows a pre-study of the 2-way actuator of Fig. 16A.
15
25
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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 2nd to a 1st
longitudinal position is the power stroke, and the stroke from the 1st 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 sub-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.11R, whereby the
combustion
motor here is forced liquid cooled, whereby one of the ES VT-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 communication 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 enlargement 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 enlargement 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 I. shows an enlargement 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 enlargement of Fig. 17D right.
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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 enlargement 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 enlargement 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.
1() Fig. 17F 1. shows an enlargement 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 enlargement of Fig. 17F right.
Fig. 17G 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. 170 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. 170 r. shows an enlagernent 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 I. 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.
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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 enlargement of Fig. 18A left and a diagram of the in-
between
relationship of the connection rods of both actuator pistons.
Fig. 18A r. shows an enlargement of Fig. 18A 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 enlargement 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 enlargement 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 enlargement 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 enlargement 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 enlargement of Fig. 18D left and a diagram of the in-
between
relationship of the connection rods of both actuator pistons.
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Fig. 18D r. shows an enlargement 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. 18E1. shows an enlargement 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 enlargement of Fig. 18E 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 enlargement 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 enlargement of Fig. 18F right.
Fig. 180 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 enlargement of Fig. 180 left and a diagram of the in-
between
relationship of the connection rods of both actuator pistons.
Fig. 180 r. shows an enlargement of Fig. 180 right.
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CT ¨ CRANKSHAFT DESIGN ¨ MULTIPLE 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 a combustion
motor, which is burning H2, 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, so that
the ri enclosed spaces (exits) are communicating with each other through
the connection of the two sub-crankshafts, while the 2nd 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 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 3I'd 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 an enlargement of Fig. 19C right.
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19620 BRIEF DESCRIPTION OF THE 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 continuation of said chamber.
Fig. 23 shows an advanced conical shaped chamber with constant
maximum work
force characteristics of a pump showing the specific
internal concave
transition from the internal conically shaped part of the chamber to the
straight inside at second longitudinal positions, which is
parallel to the centre
axis of the chamber.
Fig. 24 shows an expandable deformable piston, which will not
move by itself from
a second longitudinal position 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.
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19630 BRIEF DESCRIPTION OF THE DRAWINGS
In the following, preferred embodiments of the invention will be described
with reference to the drawings
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. 31A shows the Fig. 14D, where the section X-X has shown.
Fig. 31B shows an scaled up detail of section X-X of the chamber of Fig.
31A.
MATHEMATICAL DESCRIPTION OF THE CIRCULAR CHAMBER AND A PISTON
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 bas
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
radius of the virtual sphere is given in (2.3).
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,
visible inside the transparent chamber wall.
Fig. 32G shows the contact area between the piston and the chamber.
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
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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Fig. 32J shows Fig. 32H, 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.
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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 0-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 first longitudinal position, showing the spiral reinfor-
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 first 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 0-ring and a flexible impervious layer, the last mentioned
at a centain 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, 0-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.
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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
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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 1st 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. 550 shows a solution for an automatic clockwise
rotation of the
reinforcement pins of the foam when the piston is running towards a 1st
longitudinal position.
Fig. 55H shows an enlargement of the holder plate on the holder from
Fig. 55G.
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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 force on the piston rod is constant (please see 19620).
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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 axis, with a 200
angle.
Fig. 64B shows an ellipsoide type piston in a chamber with a
longitudinal centre axis, with a 100
angle.
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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. 81A shows a chamber of a pump according to section 19620, with an
inflatable piston according to section 19680 on three different
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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. 81D shows said (scaled up) piston, which is positioned in a second
to 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 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.
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Fig. 83G shows the enlargement 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
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, 831-1.
Fig. 83J shows the piston of Fig, 83E on a second longitudinal position,
with 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
pulling
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
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types), while the piston is shown on a second and first longitudinal
position.
Fig. 84F shows a sphere piston with a inflatable toroid as separate
part, as shown
in Fig. 84B for a ellipsoide shaped piston.
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19690-2 ¨ SHORT DESCRIPTION OF PTREFERRED EMBODIMENTS
In the following, preferred embodiments of the invention will be described
with reference to the
drawing wherein:
A single moving piston in a chamber
Fig. 90A shows a rotating piston in a circular chamber, where the piston
is
connected to the axle by a connecting rod, said axle and connecting rod
are comprising a channel, communicating with each other.
Fig. 90B shows an enlargement of a detail of the assembling of the
connection
rod and the axle, and the teeth between the axle and the connecting rod.
Fig. 90C shows the enlargement of the connecting rod on which the piston
is
mounted, based on Fig. 14F, when the piston is positioned at a first
circular position.
Fig. 90D shows the enlargement of the connecting rod on which the piston
is
mounted, based on Fig. 14G,
when the piston is positioned at a second
circular position.
together with CT and/or ES VT-systems
Fig. 90E shows the construction of Fig. 90A where the channel in the
axle is
communicating with a CT ¨ pressure management system according to
Fig. 11A, and Fig. 11D for the joint of the connecting rod to the axle.
Fig. 90F shows the construction of Fig. 90A where the channel in the
axle is
communicating with a ESVT ¨ pressure management system according
to Fig. 11G, and Fig. 11T for the joint of the connecting rod to the axle.
Fig. 90G shows the construction of Fig. 90A where the channel in the
axle is
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communicating with a ESVT ¨ pressure management system according
to Fig. HI, and Fig. 11T for the joint of the connecting rod to the axle.
Fig. 90H shows a preferred embodiment based on the construction of Fig.
90G in
combination of a camshaft, which is controlling the timing of the ESVT
¨ system, while the energy comes from a combustion motor, driven by
H2, derived from electrolyses of H20.
Multiple moving pistons in a chamber (at the same circular position)
Fig. 901 shows 4 moving pistons in a chamber, of which the space within
each
piston is communicating with the enclosed space in each connecting rod,
which are communicating with the enclosed space of the axle, around
which said pistons are moving.
Fig. 90J shows an enlargement of the joint between the connecting rods
and the
axle of Fig. 901.
together with an ESVT-system
Fig. 90K shows the construction of Fig. 901, where the channel in the
axle is
communicating with an ESVT-pressure management system according
to Fig 111, and a joint based on Fig. 11T and Fig. 90J.
Fig. 90L shows a preferred embodiment of the motor, based on the
construction
of Fig. 90K in combination of a camshaft, which is controlling the
timing of the ESVT ¨ system, while the energy comes from a
combustion motor, driven by H2, derived from electrolyses of 1120.
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Single moving chamber around a piston
Fig. 91A shows a rotating circular chamber, in which a piston is
positioned, where
the piston is connected to the axle by a connecting rod, said axle and
connecting rod are comprising a channel.
Fig. 91B shows an enlargment of a detail of the assembling of the
connecting rod
and the axle of Fig. 91A, the bearing between the axle and the
connecting rod, and said channels, communicating intermediate with
each other ¨ this construction may preferably be combined with a CT-
system.
the same combinations are possible with the CT and/or
ES VT-systems
as shown for Figs. 90K-90L (incl.).
Fig. 91C shows the cross-sections of the hub comprising the channels of
the
connecting rod and the axle, and a bearing with a hole, and teeth and
grooves for securing the position of the non-moving piston.
Fig. 91D shows a cross-sections as designated in Fig. 91C, where the
rotation of
the bearing is provided by a rotation of the hub of the spokes of said
chamber.
Fig. 91E shows the cross-section of the hub comprising the channels of
the
connecting rod and the axle where a reduced axle diameter provides a
constant communication between said channels. (FROM 19619-EP)
Multiple rotating pistons in parallel chambers
Fig. 92A shows a 3-cylinder motor, where the pistons are rotating around
a main
centre axis ¨ the chambers are interconnected and a gearbox is mounted
on said assembly, its main axle is communicating with said main central
axle of said pistons ¨ this construction may preferably be combined with
an ES VT-system.
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Fig. 92B shows the 3 cylinder motor of Fig. 92A ¨ on said main axle, on
each side
of said motor is a variable pitching wheel assembled, which are
communicating to comparable pitching wheels on a wheel axle of a
vehicle, shown is the low pitch mode (Variomatie): low speed ¨ this
construction may preferably be combined with an ES VT-system.
Fig. 92C shows the same as Fig. 92B, but where the pitches of said
wheels have
been reversed: high speed.
Multiple moving chambers transferring the torque to a central axle
Fig.93A shows a 3-cylinder motor, where the chambers are rotating, the
torque is
being transferred to a main central axle, and an external gearbox is
communicating with said axle ¨ this construction may preferably be
combined with an ES VT-system.
Fig. 93B shows an enlargement (4:1) of the left corner of the building
up of the
central axle of said motor.
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207 BRIEF DESCRIPTION OF THE DRAWINGS
In the following, preferred embodiments of the invention will be described
with reference to the
drawing 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. 100 shows a so-called indicator diagram of a one-stage single
working
piston pump with a cylinder and a piston with a fixed diameter.
0 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. 102B shows an indicator diagram of a pump according to the invention
where
the transversal cross-section increases again from a certain point of the
pump stroke, by still increasing pressure.
Fig. 103A shows a longitudinal cross-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 stroke.
Fig. 103D shows a longitudinal cross-section of a chamber of a floor 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.
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Fig. 104A 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/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 stroke.
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 arrangement 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 pressurizing chamber of Fig. 105A with a piston
means with
sealing means which is made of a composite of materials.
Fig. 105G 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, both while it is still under pressure and while it is not anymore
under pressure.
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Fig. 106A shows a longitudinal cross-section of a pump with fixed
different areas
of the transversal cross-sections of the pressurizing chamber and a
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 pump 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 pressurizing 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 arrangement 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 with 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 arrangement of Fig. 105A at
the end
of a stroke.
Fig. 107D shows section E-E of Fig. 107B.
Fig. 107E shows section F-F of Fig. 107C.
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Fig. 107F shows 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. 107G shows a variant of the pressurizing chamber of Fig.107A, 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
circumference of it approximately remains constant or decreases in a
lower degree during a pump stroke.
Fig. 107H shows transversal cross-section G-G (dotted lines) and H-H of the
longitudinal cross section of Fig. 107G.
Fig. 1071 shows transversal cross-section G-G (dotted lines) and I-I of
the
longitudinal cross section of Fig. 107H.
Fig. 107J 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 constraints.
Fig. 107M shows an example of an optimized non-convex shape of the
transversal
cross section under certain constraints.
Fig. 108A 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.
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Fig. 108C shows an enlargement of the piston arrangement of Fig. 105A at
the end
of a stroke.
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. 109B 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. 109B with a different tuning
arrangement.
Fig. 110A shows a nineth 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. 110B shows an enlargement of the piston of Fig. 110A at the
beginning of
a stroke.
Fig. 110C shows an enlargement of the piston of Fig. 110A at the end of a
stroke.
Fig. 111A shows a longitudinal cross-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. 111A at the
beginning of
a stroke.
Fig. 111C 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
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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 stroke.
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.
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653 BRIEF DESCRIPTION OF THE DRAWINGS
In the following, preferred embodiments of the invention will be described
with reference to the
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. 202B 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, the 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 longitudinal cross-section of a non-moving piston
according to the
invention in a non-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.
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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.
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
pressurized, subjected to a pressure from the cylinder.
Fig. 205D shows the 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 - the 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,
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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. 206H 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 unpressurized 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
stroke.
Fig. 208A shows a longitudinal cross-section of a chamber with fixed
different areas of
the transversal cross-sections having different circumpherical 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 unpressurized 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
in
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
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outside the central axis of the piston - left: at the first longitudinal
position,
right: at the second longitudinal position.
Fig. 208F shows a top view of the piston alike 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 cross-section of a chamber with fixed
different areas of
the transversal cross-sections having different circumpherical 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 -
presssurized - where it has unpressurized its production size.
Fig. 209B shows an enlargement of the piston of Fig. 209A at the first
longitudinal position
of the chamber.
Fig. 209C shows an enlargement of the piston of Fig. 209A at the second
longitudinal
position of the chamber.
Fig. 210A shows the embodiment of Fig. 206 where the pressure inside the
piston may
be changed by inflation through e.g. a Schrader valve which is positioned in
the handle and/or e.g. a check 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
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pressure releave 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 boxes.
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 outlet valve
of the chamber may be 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. 211C 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 inflation arrangement of the piston
of Fig. 211A
at the end of the stroke.
Fig. 211E shows an enlargement of the bypass arrangement for the valve
actuator for
closing and opening of the outlet valve.
Fig. 211F shows an enlargement of an automatic closing and opening
arrangement of
the outlet valve - a comparable system is shown for obtaining a
predetermined pressure value in the piston (dashed).
Fig. 211G shows an enlargement of an inflation arrangement of the piston
of Fig.
211A, 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. 211H 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.
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Fig. 212 shows an arrangement where the pressure in the container may
depend
of the pressure in the chamber.
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 at
the end
of a pump stroke.
Fig. 214 shows a longitudinal cross-section of a chamber having an
elastical 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 beginning, during and at the 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, while 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
circumference 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
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longitudinal cross section of Fig. 215C.
Fig. 215E 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. 215F shows an example of an optimized convex shape of the
transversal
cross section under certain constraints. -
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.
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507 DESCRIPTION OF THE DRAWINGS
The foregoing features and other aspects of the invention are explained in the
following
description in connection with the accompagning drawings, wherein:
Figure 301 shows a first 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 Figure 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 302B 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.
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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. 4013 shows a back view of the floor pump of Fig. 401A.
Fig. 402A shows top view of a pump of a floor pump type of Fig 402B,
where the combination can move in 3 dimensions in relation to
the surface, 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 pump of Fig 402B, 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 moved 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 2B, 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. 403A shows a side view of a floor pump with a flexible transition
between the
chamber of the combination and the basis.
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Fig. 403B shows an enlargement of the transition of Fig. 403A.
Fig. 403C shows a back 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. 403C.
Fig. 404A shows a back view 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 enlargement of a transversal- - cross-section of the
cab of
Fig. 404A 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 o 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
rod is not pulled out, with a transversal translation of the piston
rod 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 1800.
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 406B, 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.
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19627 DESCRIPTION OF PREFERRED EMBODIMENTS
In the following, preferred embodiments of the invention will be described
with reference to the
drawings wherein:
10
20
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Fig. 1-3 deal with the limitation of the stretching of the wall of the piston.
This comprises a limitation of
the stretching in the longitudinal direction when the piston is 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.
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.
The expansion behaviour of the wall of the container may be depending on the
type 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 use 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 subjected to external
forces.
All kinds of fluids _may be used - a combination of a compressable and a non-
compressible
medium, a compressable medium only or a non-compressable medium only.
As the change of the size of the container may be substantial from the
smallest cross-sectional
area, where it has its production size, and expanded at the biggest cross-
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 least the
first enclosed space may be needed.
Fig. 1A shows a longitudinal cross-section of the chamber 186 with a concave
wall 185 and an
inflatable piston comprising a container 208 at the beginning (= first
longitudinal position in the chamber
186) and the same 208' at the end of a stroke (= second longitudinal position
in the chamber 186).
Central axis of the chamber 186 is 184. The container 208' shows its
production size, having a textile
reinforced 189 in the skin 188 of the wall 187. During the stroke, the wall
187 of the container expands
until a stop arrangement, which may be the textile reinforcement 189 and/or a
mechanical stop 196
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outside the container 208 and/or another stop arrangement stops the movement
during the stroke. And
thus the expansion of the container 208. Depending on the pressure in the
chamber 186, there still may
occur a longitudinal stretching of the wall of the container, due to pressure
in the chamber 186. The
main function however of the reinforcement is to limit this longitudinal
stretching of the wall 187 of the
container 208. 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
circumferential 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. 1B shows a first embodiment of the expanded piston 208 at the beginning
of a stroke. The
wall 187 of the container is build up by a skin 188 of a flexible material,
which may be e.g. a rubber
type or the like, with a textile reinforcement 189, which allows expansion.
The direction of the textile
reinforcement in relation to the central axis 184 (= braid angle) is different
from 54 44'. The change of
the size of the piston during the stroke results not necessarily in an
identical shape, as drawn. Due to
the expansion the thickness of the wall of the container may be smaller than
that of the container as
produced when positioned at the end of the stroke (= second longitudinal
position). 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 can 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 of the container may move 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 tuning of the
sealing force may comprise a combination of an incompressable fluid 205 and a
compressable fluid 206
the wall 185a of the chamber 186 which is parallel to the centre axis 184. It
is positioned approx. at the end of
the stroke at first longitudinal positions.
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(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 communicating with a third chamber
(see Fig. 12), 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. Comparable stops may be positioned elsewhere on
the piston rod, depending
on the demanded movement of the wall of the container. The contact area
between the wall of the
container and the wall of the chamber is 198.
Fig. IC shows the piston of Fig. 1B at the end of a pump stroke, where it has
its production
size. The cap 191 in the top is moved over a distance a' from the stop 196.
The spring-force operated
valve piston 126 has been moved over a distance b'. The bottom cap 192 is
shown adjacent to the stop
197 - when there is pressure in the chamber 186, then the bottom cap 192 is
pressed against the stop
197. The compressable fluid 206' and the non-compressable fluid 205'. The
contact area 198' between
the container 208'and the wall of the chamber at the second longitudinal
position.
The wall 185b of the chamber 186, which is parallel to the centre axis 184. It
is positioned approximately at the
end of the stroke at second longitudinal positions
Fig.2A 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 second longitudinal position. The container 217' shows its production
size, having a fiber reinforcement 219
in the skin 216 of the wall 218 according to the Trellis Effect . During the
stroke the wall 218 of
the container expands until a stop arrangement, which may be the fiber
reinforcement 219 and/or a mechanical
stop 214 inside the container and/or another stop arrangement stops the
movement during
the stroke. And thus stops the expansion of the wall 218 of the container 217.
The main function of the
fiber reinforcement is to limit the longitudinal stretching of the wall 218 of
the container 217. During the
stroke the pressure inside the container 217, 217' may remain constant. This
pressure depends on the
change in the volume of the container 217, 217', thus on the change in the
circumferential length of the
cross-sections of the chamber 186 during the stroke. It may also be possible
that the pressure changes
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during the stroke, depending or not of the pressure in the chamber 186. The
contact area 211 between
the container 217 and the wall of the chamber at the first longitudinal
position.
Fig. 2B shows a second embodiment of the expanded piston 217 at the beginning
of a stroke.
The wall 218 of the container is build up by a skin 216 of a flexible
material, which may be e.g. a
rubber type or the like, with a fiber reinforcement 219, which allows
expansion of the container wall
218, and thus the direction of the fibers in relation to the central axis 184
(= braid angle) may be
different from 54 44'. 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 end of the
stroke (= second longitudinal position). 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 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 thickness of the wall of the
container. Both caps 191,192
can 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 can 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 - this embodiment is thought
to be used in a piston
chamber device which has pressure in chamber 186. 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 tuning of the sealing force may comprise a
combination of an
incompressable 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 third chamber (see Fig. 10), 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.
The wall 185a of the chamber 186, which is parallel to the centre axis 184. It
is positioned approximately at the end
of the stroke at first longitudinal positions
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Fig. 2C shows the piston of Fig. 2B at the end of a pump stroke, where it has
its production
size. The cap 191 is moved over a distance c' from the stop 214. 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 cap 192 is pressed against the stop
197. The compressable fluid
206' and the non-compressable fluid 205'. The contact area 211' of the
container 217'and the wall of
the chamber 186 at the second longitudinal position.
The wall 185b of the chamber 186, which is parallel to the centre axis 184. It
is positioned approximately at the end
of the stroke at second longitudinal positions.
Fig. 3A,B,C show an inflatable piston comprising a container 228 at the
beginning and 228' at
the end of a stroke. The production size is that of piston 228'at the second
longitudinal position in the
chamber 186. The construction of the piston may be identical with that of Fig.
7A,B,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. 3B shows the wall 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
impervious layer 226.
Fig. 3C shows the contact area 225 ' between the container 228' and the wall
of the chamber at
the second longitudinal position.
Fig. 3D shows a top view of the piston 228 and 228', respectively with the
reinforcement means 227,
and 227' respectively.
Fig. 3E shows a top view of the piston 228 and 228', respectively with the
reinforcement
means 229, and 229' respectively.
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Fig. 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 to a first position
has an angle a with the centre axis 184. The projection 1000 of the middle
point (centre) 1001 of the
elastically 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 movable
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, instanteneously non-moving, and thereby
expanding, so
that the contact area 225" of the piston wall 187 with the 185 wall of the
chamber 186 increases at
second longitudinal positions of said contact surface 225" ¨ the movable cab
191 is currently non-
moving. The contact surface 225" is 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 elastically
deformable wall of the piston ¨ its projections 1010 (old) and 1011 (new) on
the centre axis 184
respectively. The distance f. The force 1012 from the piston wall 187 on the
wall 185 of the chamber.
The direction of movement 1013 of the force 1012. The movement 1014 of the
movable cap 191.
Fig. 5C shows the piston of Fig. 5B, instanteneously non-moving, and thereby
expanding, so
that the contact surface 225" of the piston wall 187 with the wall 185 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. The centres 1015 (old) and 1016 (new) of the elastically
deformable wall of the piston
¨ its projections 1017 (old) and 1018 (new) on the centre axis 184
respectively. The distance g'. The
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direction of movement 1019 of the reaction force 1020 of the chamber wall 185
on the wall 187 of the
piston. The direction of the movement 1021 of wall 187 of the piston.
Fig. 5D shows the piston of Fig. 5C, where the non-movable cap 192 is
instanteneously
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 deformable wall
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 due to a
increasing contact area 225 ". The projection 1027 on the centre axis 184 of
the centre 1028 of the
elastically deformable wall of the piston. The moving direction 1029 of the
movable cap 191. The
moving direction 1030 and 1031 of the wall of the piston.
Fig. 6A shows an expandable piston 898, moving engagingly or/and sealingly 900
in a cone-formed
chamber 899,comprising a reinforced (not shown) wall 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
mixture of fluids in the piston. 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. The contact
area 905 between the wall 901 of the piston 898 and the wall 897 of the
chamber 899. The existence of
fluid at both sides of the piston may cause the piston move in a different
manner than desired.
Fig. 6B shows the piston 898 of Fig. 6A moving engagingly or/and 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
the cone formed chamber 896 at 1 st longitudinal positions is a tube 911,
which allows communication
between the space 908 with the atmosphere 910 of the surroundings,while tube
912 is assembled in the
wall 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 wall
901 of the piston 898
and the wall 897 of the chamber 896.
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the 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 or/and sealirigly
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 1st 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 wall 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 communi-
cating 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. 6F 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
communication 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 force 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. 6F
and the view on the
actuator piston 925 from a 1st longitudinal position. The chamber wall 922.
The movable cab 930. The
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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 at the 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
first position, because the mid
point of its flexible wall is above the contact surface with the wall.
15
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Fig. 7D 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 53 44'.
When the material type and thickness is the same 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
tt, 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. 7B.
Fig. 7E is a 3-dimensional drawing and shows the reinforcement matrix of Fig.
7D 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. 7D.
Fig. 7F 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 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.
Fig. 7G is a 3-dimensional drawing and shows the reinforcement matrix of Fig.
7F 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. 7F.
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Fig. 8 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
a taper wall 373
e.g. shown here 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
chamber (372') and at the first 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 the solution
for the problem of jamming.
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Fig. 9A shows a longitudinal cross-section of the chamber with a
convex/concave wall 185 and
an inflatable piston comprising a container 258 at the beginning and the same
238' at the end of a
stroke. The container 258' shows its production size.
Fig. 9B shows the longitudinal cross-section of the piston 258 having a wall
251 and a
reinforced skin 252 by a plurality of at least elastically deformable support
members 254 rotatably
fastened to a common member 255, connected to the an skin 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
member 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. 9C shows the longitudinal cross-section of the piston 258'. The contact
area 253'.
Fig. 9D shows the longitudinal cross-section of the piston 258" with a common
area
253". The centre 1020 of the elastically, deformed wall 251 of the piston. The
projection of the centre
point 1020 on the centre axis 1022.
20
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Figs. 10A-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. 10G-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 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,
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
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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. 10B or Fig 10C,
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' may be 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 2nd longitudinal
position and is 'b' at a 1 st
longitudinal position, wherein a = b.
Fig. 10B 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 postion
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
from 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 still 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
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non-engaging the wall 185. As a comparison: the same size of said piston 217B"
is obtained further
away to a 2' longitudinal position than when the piston is (sealingly and/or
engagingly) moving
2003 from a 2nd longitudinal position 2000 to a 1st longitudinal position
2001. Said pressure drop
may also be obtained already at a first longitudinal position 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. 10A 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. 10C shows the alternative solution for changing the internal pressure of
the piston 217,
and shall be regarded together with Fig. 10A, where in this case the valve 126
is lacking and instead
may an inlet/outlet configuration 2020 be present ¨ e.g. please see Figs. 210A-
F (incl.) and Figs.
211A-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. 10A. 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. 10C. 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.
10A, resulting in piston 217'. The wall 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 208 to piston 217" Or 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 1st longitudinal
position 2001 to a 2'd
longitudinal position 2000.
The wall 185 of the chamber 186 in the drawings 10A-L at the second and first
longitudinal
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positions may be not parallel to the centre axis. No channels as shown in
Figs. 4, 5A-E (incl.),
Figs. 10D-F show the analogue process of that shown in Figs. 10A-C, now with a
sphere
shaped piston 208.
Figs. 10G-I show an analogue process of that shown in Figs. 10A-C, with the
difference
that the pressure may be maintained more when the-piston 217' is moving from a
2n1 longitudinal
positions 2000 to a first longitudinal position 2001, wherein the valve 126 is
not so much removing
from the bottom end of the piston, as shown in Fig. 10A. 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 1st
longitudinal positions this length has been decreased to T and at a 1st
longitudinal position said
length is further decreased to `g', wherein e> f> g.
Figs. 10J-L show the comparable process of that shown in Figs. 10D-F, wherein
pressure is
maintained as described in Pig. 10G, 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 2nd and 1st longitudinal positions this length has been decreased to T
and at a 1st
longitudinal position said length is further decreased to T, wherein h> i > j.
The process called the E(nclosed)S(pace)V(olumechange) T(echnology) shown in
Figs. 10A,10B or
Figs. 10D,10E are being used in a motor according this invention, shown in
Figs. 11F,G (crankshaft)
and in Figs, 13F, 13G, 14A-H (incl.) (rotational).
The process called C(onsumption) T(echnology) shown in Figs. 10A,10C or Figs.
10D,10F
and in Figs. 210A-F (incl.) and Figs.211A-F (incl.) are being used in a motor
according this
invention, shown in Figs. 11A-C (incl.) (crankshaft) and in Figs. 12A-C
(incl.), 13A-D (incl.).
Fig. 10M 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 1 piston 968 positioned, shown on two
important positions,
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namely position 968' when at a 1st 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 1st 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
holes 970 for assembling
said chamber 960 on axle 966.
Fig. 10N 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. 10G and 10H may comprise a chamber 860 of which,
at least a part, may
be parallel to the centre axis of said chamber (not shown).
The circular chamber, comprising identical sub-chambers may comprise an
actuator piston in each of
the sub-chambers, wherein all actuator pistons are located at the same
circular point of each sub-
chamber
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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. 11F, 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 for controling said valves, and this could very well come
from an 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. 13F references 1093 and 1094 may be used here.
Addition to the description of preferred embodiments for Fig. 11F
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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
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Regarding the pressure management system for Figs. 11A, 11B, 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. 11A,
11B, 11D), 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
1() 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
continuously 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 ellipsoide with a smaller
circumference to an ellipsoide
with a bigger circumference / ellipsoide ¨ 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
continuously.
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. Just 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.
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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. 11A, 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 11C
20
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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. 11A, 11B, 11D), similar solutions may be valid in said circular
chambers, but in a bit
adapted way.
In case of 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 acle 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 lifted 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 subchamber, 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
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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 conaical
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.
1B, 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.
1B, 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) through 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.
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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).
10
20
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19627 - based on 19618 - updated Figs 11A-Z based on 19617 (in main document
19601)
Fig. 11A 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 "L" 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 continuously 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 axel 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 pump), which is connected by a piston rod 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 with contraweights 834. 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
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was pressurized at a first 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], or 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. It may also be possible
to repressurize said pressure storage vessel, 814, through a hose 2701, which
is communicating with a
pressure source. 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 by a wire [1069] with an electrical
storage, e.g. an accumulator (or
a condensator ('capacitator') storage type) 832, which is connected to a solar
cell 833. The electric motor
830 is capable of being used 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) ¨ said 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 842.The
configuration 851 of auxilliarly power sources is shown in Figs. 15A, 15B ,
15C or 15E. It may also be
that this battery 832 is charged by an external electrical power source 2700
through e.g. a cable.
Fig. 11B shows schematically the control devices for the motor of Fig. 11A.
The electric starter
motor 830 is comprising a clutch (not shown), connecting the axle 831 and/or
852 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
833. Said motor 830 will also be 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 840 more up causes the
crankshaft 801 to rotate
more quickly, screwing the reduction valve 840 down causes the crankshaft 801
to rotate slower. Closing
the reduction valve 840 completely will stop the motor. The speeder 841 is
communicating with the
reduction valve 840. The alternator 850 is communicating with the main axle
852, and is charging the battery
832 through connection 842. The configuration 851 of auxilliarly power sources
is shown in Figs.
15A, 15B, 15C or 15E.
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Figs. 11A-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 11B.
At the point of
time when the piston has arrived from a 1st longitudinal position at the final
2nd longitudinal position of
the chamber ¨ thus 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 hole 1101, so that the
piston pressurizes to the
maximum pressure rate. Due to its pressuration will the piston beginning to
move to a 1st longitudinal
position, thereby turning the crankshaft and closing said hole, so that said
communication stops. Said
movement is reducing its internal pressure due to its increased inside volume,
due to the fact that the
ellipsoide shaped piston is beginning to transform itself into the shape of a
sphere. When having arrived at
the 10t longitudinal position there is still a medium rate of pressure left in
said piston and the enclosed
space within the piston rod. When said piston has arrived at the primo lot
longitudinal position on its way
back to a 2nd longitudinal position ¨ thus just after having reversed the
direction of its motion, the enclosed
space within the piston rod will begin to communicate through a hole 1102 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
inertia 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 reach 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 g
longitudinal position, and may be returning a bit on its way to a second
longitudinal position due to
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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.
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 1st 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 U-bend axle 801 are
shown in Fig. 11D. Details
of the joint of the piston rod 805 and the connecting rod 925 are shown in
Fig. 11E. Details of the
assembly of the piston rod 819 of the pump 818 with the crankshaft 820 are
shown in Fig. 11.T. 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 be a combined assembly comprising two
check valves with each a
valve actuator according to preferably Fig. 210F or optionally Fig. 210E from
the 2i'd enclosed space 822 of
the crankshaft 800 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 2nd enlosed space 822 of the crankshaft 800 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 rod
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
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(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,
which is separating the second enclosed space 815 and the third enclosed space
816. At another point of
time is the current hole 1102 becomes a blind hole, while the current blind
hole 1101 has become a hole.
Said holes 1101 and 1102 are never commnicating with the enclosed space 813 at
the same time. The base
926 of the piston rod 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 930 and rings 931
on each side of the piston rod 805 are holding the two parts 927 and 928
together.
Fig. 11E shows a detail of the joint of the piston rod 805 and the connecting
rod 925 (805'),
shown in Fig. 11C. Piston rod 805 is having an end 932, which is comprising a
channel 933 which is
communicating with the 2nd enclosed space 815 and the 3rd enclosed space 816
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 0-ring 939, which is sealing said end 942 to the said end 932 of
said piston rod 925. 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. 11F shows a detail of the U-shaped axle 801, and a channel (e.g. 823)
inside said crankshaft,
which is shown in Figs. 11A-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 952 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
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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.
Figs. 11G-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' comprising 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 a 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. Reduction valve 1057 is communicating by channel 3300 with one
side of 2-way actuator
1053, and reduction valve 1058 communicates by channel 3301 with the other
side of 2-way actuator
1053. Said reduction valves 1057 and 1058 are interconnected preferably
electrically (and optionally
mechanically ¨ other solutions exist but are not shown), 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
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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.
Said channel 1050 is additionally constantly communicating with the piston rod
805 of an ESVT-
pump 1056 ¨ please see Fig. 11T 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 a conical chamber 1060 is driven by a 2-way actuator 1072 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. 10A-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 1053.
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 [1069] with
the battery 832.
Fig. 11H shows the configuration of Fig. 11G (with components with references
for which is
referred 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 3rd enclosed space, at the right point of time, enabling depressurization
of the actuator piston 806, but
may not needed for the currently used ESV Technology. The outlet [1070] of the
2-way actuator 1072 is
communicating with the pump 820, but can be connected to the feederline [825]
of the piston pump 826,
when the pump 820 is not present. 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
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the pressure 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 for a schematic view
inside the 2-way actuator
1053'). The necessary check valves are not shown. Said reduction valves 1057-
1058 and 1051-1052,
respectively, are related to each other, in such a way that if one valve is
being opened more, the other
valve is simultaneously closing more. The valve means 840' of the reduction
valve 1057 is being activated
by a speeder 841, while the reduction valve 1051 is activated by sensor 1064
with communication [1054].
The reduction valves are being electrically activated through wire [1069].
The alternator 850 is communicating with the main axle 852, and is charging
the battery 832
through connection [842]. The configuration 851 of other auxilliarly power
sources is shown in Figs. I5A,
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
optionally non-sustainable
power sources.
Figs. 111 ¨ 1 IN (intl.) show a one (Figs. 111, 11K, 11M) and a two cylinder
motor (Fig. 11J,
11L, 11N), 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.
Ill, 11J) according to the configuration shown in Fig. 11H, a crankshaft
(Figs. 11K, 11 L) or a camshaft
(Figs. 11M, 11N), 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, 15B, 15C, 15 E, 15F and optionally non-
sustainable power sources.
Each drawing which is comprising a two cylinder motor is consisting of a
"left" and a "right" scaled up
drawing.
Figs. 11! ¨ 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
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controlling the pressure rebuild of the actuator piston(s) by either wires, by
a camshaft or by a crankshaft
which may be communicating to the power delivered. In order to enhance the
efficiency of the power
delivered, Figs. lb o ¨ 11R show a small combustion motor, using preferably H2
as power source
(preferably derived from hydrolyses of H20), which is directly communicating
with a camshaft or a
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 (incl.) 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 (incl.) the
power strokes of the two
cylinders of the same motor are functionning 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) may be combined.
Fig. 111 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 ESVT-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 regarding 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 1050 of the axle
852 and the chamber
1062 can be 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. 11H,
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.
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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 are communicating with said reduction
valves 1058 and
1057, respectively. Said chambers are additionally communicating with each
other through valve actuator
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-B.
The ESVT-pump 1056 is comprising a chamber 1060 and a piston 1059, has been
mounted on
the main axle 852 ¨ please see Fig. 11U 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. Reduction
valve 1051 is activated by communication line [1054] and powerline [1069]
through electric regulator
1065.
The pump 826 of Fig. 11H has been worked out in detail in Fig. 11V. It gets
its energy from an
electric motor 830', which receive electricity through an electric
communication [1080] from a battery
832. The circular movemenf of the axle of said motor 830', 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 826.
Compressed fluid is coming
from said pump 826 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 1077. It delivers
electric power to the battery 832, through the electric communication 842.
Electrical drive system 830 is
similar to said elements of Fig 11A.
30
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Fig. 11J is showing an overview of a two cylinder motor, while particulars are
shown in the
scaled up Figs. 11J left and 11J right.
Fig. 11J 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 (asynchrone crankshaft design)
according to Fig. 17B. Each
"cylinder", better designated as 'chamber' has an enclosed space comprised in
its crankshaft, hereinafter
designated as 'sub-crankshaft', which have been separated from each other by
e.g. a tightening rod 1270
(Fig.11X) in 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 be moving
(a)synchrone, may it be necessary that the pressure reduction valves of each 2-
way-actuator are
communicating with each other 1066 for synchronisation purposes, e.g.
electrically. However, it may also
be that said pressure reduction valves are communicating through the sub-
crankshafts, each by its sensor
measuring the rotation of each sub-crankshaft 1064. 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
1067. 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 1057. Whether or not the two
2-way actuators may be
combined into one, cannot be concluded without substantial investigations:
please see Fig. 17C-17H
(incl.).
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 832, which has been charged
Ex.Works, may be recharged
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during operation by an alternator 850, communicating with the main motor axle
852. 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 890 through a hose,
which is communicating with a
pressure source, such as preferably a medium pressure canister or optionally a
high pressure canister, or an
external pump (e.g. driven by a windmill ¨ most efficient). Auxilliarly power
sources are according Figs.
15A,B,C,E,F, of which at least one may charge said batteries.
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-
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. 11W, 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. 11J left shows a scaled up of the left part of Fig. 11J.
Fig. IIJ right shows a scaled up of the right part of Fig. 11J.
Fig. 11K is showing a one cylinder motor, which is based on the concept shown
in Fig. 11H,
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
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
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each other by wire [3501] through an electric/electronic regulator 3502. The
motor 3500, also shown in
the following Figures IlL, 11M and 11N, 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.
The fact that a (auxilliarly) 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. 11C for the actuator piston) or
that said connecting rod is
missing, and that a similar the oscillation construction of the pump shown in
Fig. 11V 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
auxilliarly
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 ii!. This is a preferred solution, while a
solution of having a pump 820,
while pump 826 has been redundant is an optional solution.
Fig. 11L is showing an overview of a two cylinder motor, while particulars are
shown in the
scaled up Figs. 11L left and 11L right.
Fig. I IL is showing a two cylinder motor, based on the concept shown in Fig.
11K, where each
cylinder has an enclosed space, and thus 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
3500 are 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 may be made as one piece due to the fact that the assembly
of the connection rod and the
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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 111. 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. 1 1L left shows a scaled up of the left part of Fig 11 L.
Fig. 11L right shows a scaled up of the right part of Fig 11 L.
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 height of the cam 3516 to lift the piston rod
of the ESVT-
pump1056, and that means that the ESVT-pump has a decreased stroke length, and
an increased width of
aid chamber than that of Figs. 11K and 11L, 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 ES VT-pump has been exchanged by an
auxilliarly
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 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. 11N is showing an overview of a two cylinder motor, while particulars are
shown in the
scaled up Figs. 11N left and 1 IN right.
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Fig. 11N 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
3500 are communicating with each other by wire [3501] through an
electronic/electric regulator 3502,
when both ESVT-pumps are using the same camshaft axle.
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 pump 826
may be smaller than the one
shown in Fig 111. 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. 11N left shows a scaled up of the left part of Fig 11N.
Fig. 11N right shows A scaled up of the right part of Fig 11 N.
Figs. 110,P and 11Q,R (incl.), respectively concern the configurations of
Figs. 11K,L
(crankshaft) and Figs. 11M,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 H20 (and from a canister under pressure ¨ cooled and liquified
or not), is directly
communicating with the ESVT pump which is controlling the volume of the
enclosed space. Instead of the
configuration in Fig 15C different configurations, such as the configuration
of Fig 15D, may be used. The
fact that said combustion motor directly drives the power lines (ESVT-pump(s),
crankshaft/camshaft,
instead of first generating electricity, which drives an electric motor, means
that it is approximately 4 times
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.
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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:
= the electrolyses of H20 which results in a certain volume of H2 and 02 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, 11L, II M and 11N.
the motor is also driving the pump 826 shown in Fig. 11V, for repressuration
of the pressure storage
vessel 890, through a tooth belt and wheels
The configuration (according Fig. 15C) of the auxilliarly H2 combustion motor
is comprising a
storage tank 1612 for conductive 1-120 1613 (which may be H20 from the tap and
a conductor, e.g. salt, or
just sea water), with a filler opening 1614 and an outlet channel [1615] to
the vessel 1616 wherein the
electrolyses 1617 of said water 1613 is taking place. Wire [3547] is
connecting the speeder 841 with a
regulator 3509, controlling the production level of H2 and 02 through
electrolyses. No check valves have
been shown. The electric power line [3547] from the battery 832 to the vessel
wherein the electrolyses is
taking place. The resulting H2 is transported [3545] by a pump to said motor ¨
the very necessary check
valves have not been shown. The resulting 02 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 H2 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. 11P left and 11P right.
Fig. 11P is showing a two cylinder motor, based on the concept shown in Fig.
110, where each
cylinder has an enclosed space, and thus an ESVT- pump, which both are driven
by the same crankshaft,
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and two speeder actuators, but one auxilliarly motor. The crankshaft is
directly driven through gear wheels
3526 by a liquid cooled combustion motor, using H2, derived by the
electrolyses of H20. Said crankshaft
is driving the ESVT-pumps, and the pump 826 which is repressurating the
pressure storage vessel 890.
The shown toothed belt 3527 may be exchanged by gear wheels.
There is a water pump 3528 for circulation of the cooling water 3529 from the
air cooled radiator 3530,
and to another radiator 3531, which may warm up air from the surroundings for
warming up e.g. the cabin
of a car. Said water 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 a scaled up of the left part of Fig 11 P.
Fig. 11P right shows a scaled up of the right part of Fig 11 P.
Fig. 11Q is showing a one cylinder motor, based on the above mentioned
concepts,
using a camshaft for driving the ESVT pump. The principle of the camshaft in
Fig 11Q is equal to that of
Fig 11M. The camshaft is is directly driven by the auxilliarly power from a
forced gas (e.g. air) cooled
combustion motor. The pump, which is repressurising the pressure storage
vessel, is directly driven by said
combustion motor. The batteries 832 are being charged by an alternator, which
is mounted on the main
motor axle, or according to Fig 15.D.
Fig. 11R is showing an overview of a two cylinder motor, while particulars are
shown in the
scaled up Figs. 11R left and 11R right.
Fig. 11R is showing a two cylinder motor, based on the concept shown in Fig.
11Q, where each
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. 11R left shows a scaled up of the left part of Fig 11 R.
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Fig. 11R right shows a scaled up of the right part of Fig 11 R.
10
20
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Figs. 11S-W (incl.) show specifics of several construction elements, which has
been used in the
Figs. 11A-R (incl.).
Fig. 11S shows a detail of the joint of the pump 1061 of the piston-chamber
combination
according to Figs. HI - 11 R 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 852 with an appropriate
fine fit. Said base part
1141 is bolted on the motor housing 1145, which has a bearing 1146 around the
main axle 852, which is
turning around. Said motor housing is shown as a hatch 5000. 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 3rd enclosed space 1150.
The bolt 1151 and the
washer 1152.
Fig. 11T 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. 110 ¨ 11R,
using a continuous
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. 11G
¨ 11R 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
bearings 1100 and
1100", and the 0-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.
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, 1107 and 1108 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 1110 and rings 1111 on each side of the piston
rod 805' are holding the two
parts 927' and 928' together.
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Fig. 11U shows a detail of the joint of the pump 1060 of the piston-chamber
combination
according to Figs. 111 - 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 5000. The base parts 1181 and
1182 have an 0-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 mechanism driving a pump, e.g. 826, of Figs. 11H ¨ 11R, 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
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-centrally
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-centrally rotating
in a plane perpendicular to said
disk 1217, around said axle 1220. This means that the piston rod 1214 is in a
translating 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
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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. 11W shows the connecting joint between the two crankshafts of the 2-
cylinder motor
according to Figs. 11J, 11L, 11N, lip, 11R. The shown connecting joint is an
improved version of the
version shown in the drawings Figs. 11J, I 1L, 11N, 11P, 11R. In this drawing
is the version of this
connection 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 functioning as (2nd
) 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, within the
flanges 1256 and 1257,
resp. of both crankshaft ends 1253 and 1254, resp. The last mentioned
crankshaft 1252 is comprising a
channel 1265, which is functioning as (3'1) 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 flexible cylinder
1259 enables a very small
difference in angle position of the two assembled crankshafts 1250 and 1252,
which may arise from dis-
synchronisation, due to asynchrone motion of the actuator pistons (not shown).
The washer 1261 and the
nut 1262.
Fig. 11W' 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 flat.
Fig. 11X shows the same as Fig. 11W, 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 common channel parts 1273 and 1274, resp. of each have a larger
diameter, in order to obtain
a shoulder 1275 and 1276. The tightness of said tightening rod 1270 in one of
the channels 1273 or 1274
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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. 11W'.
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.
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Fig. 12A shows the configuration 800 of the motor according to Fig. 11B, 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 [ ...... ], 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 1st 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 1st 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 holes 967 for
assembling said chamber 960 on
axle 966.
Fig. 12C (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, where it is sealed
with two 0-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 or
rotational).
The electrical signal 1076 is communicating with an electrical/electronical
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 thus 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
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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 0-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 electrical/electronical
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. 11A, where the crankshaft
arrangement 800 has been
exchanged by the rotational motor of Fig. 10B.
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'.
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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 be
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. 11F. Each enclosed space (e.g.1090) of each pistons
is communicating with a
piston-chamber combination 873, 872,874,876,875, while 873 is comprising an
actuator piston 1091 of
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which its position in the chamber 1092 is controlled by the position of a
camwheel 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. 11F, and
another controlling actuator
1056' (as 1056) and reduction valves 1057' and 1058' (as 1057, 1058), while
additonally 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).
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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 / 2nd circular position 1705 to a 1st
longitudinal / 1st circular
position 1706. The actuator piston 1700 has been pressurized to e.g. 3Y2 Bar
at said 2nd longitudinal
/ 2nd 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 31/4 Bar at a second a 2" longitudinal / 2"
circular position
1705 until depressurized to e.g. Y2 Bar when moving from said 1st longitudinal
/ 1st circular position
1706 ¨ the actuator piston 1709 at said 1 st longitudinal / 1st circular
position has now a much
bigger diameter that said piston at said 2nd longitudinal / 2nd 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" longitudinal position - the V2
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 smaller than the diameter of said actuator piston 1700,
which had been pressurized
to 3Y2 Bar at said 2nd 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 2" longitudinal position
1714 can take place,
pressurizing said actuator piston to 3V2 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. The
piston 1722 is positioned at a 2" longitudinal / circular position and the
fluid 1723 inside said
actuator piston has been pressurized to e.g. 3V2 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 2nd 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" longitudinal / circular position to a 1st longitudinal / circular
position in said sub-chamber
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1720, where the fluid 1723 is reducing its pressure to Y2 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 a 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 f3 (>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 actuator
piston remains a contact with the wall 1748 of said chamber 1720.
Fig. 14C shows the configuration of Fig. 14B which enables an injection of
fluid into
the actuator piston, when ii is at a 2"1 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 2'1 position (Fig. 14B ref. nr. 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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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
2' 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 1955 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 a part 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 end 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
scematically as e.g. rotor 1928 which is fastened on the outside motor wall
1929, which is comprising
said cam 1926. The anker 1930 is fastened in said main 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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in a groove, which is parallel with the centre axis 1934 of said pump 1913,
such that a translating
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 1st 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 wall 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 centre axis 1934 of the chamber 1914 of said pump
1913. Said piston
rod 1942 can translate within the cylinder 1950, and is sealed by two 0-rings
1951 and 1952,
respectively. The distance an 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 same 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"d 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 an (Fig. 14F)
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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).
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DESCRIPTION OF PREFERRED EMBODIMENTS updated from 19622
Fig. 141 shows that part of a pressure management system of a motor 1970, and
1971,
resp. each mounted on at least two parallel positioned wheels 1972 and 1973,
resp. of e.g. a car. The
back wheels 1974 and 1975, resp. Said car is turning in a left corner, around
a circle centre 1976.
The left wheel 1972 closest to said center 1976 is turning with a smaller
radius 1977, than the right
wheel 1973, which has a radius 1978. The left wheel 1972 is turning with an
angle 'a' and the right
wheel with an angle `1:1', where 'a' > `1)'. Consequently needs the left wheel
turn slower than the
right wheel, and these signals 1981 and1982 have to be send to the relevant
motors 1972 and 1973.
This is done by a sensor 1979 and 1980, sensing said different angles 'a' and
'b'. These signals
1981 and 1982, resp. are being transferred to a computer 1983, and being
worked with, resulting in
control signals 1984 and 1985, resp., so that said motors 1970 and 1971, resp.
are changing each
their speed accordingly.
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Figs. 15A-E show several auxiliary power sources working together with the
motor.
The shown electric power lines have been carefully chosen.
Fig. 15A shows a H2-fuel cell which delivers electricity to a motor, which is
driving
an ESVT-pump. Today (February 2011) is this solution very costly, but just on
the website 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 difficult
and energy unfriendly.
Fig. 15B shows a solution which is a solution for the H2 storage problem,
because H2
is stored as H20, and is coming free through electrolyses. Because the
feasibility study showed that
to less than 10% of the current energy is necessary for driving, e.g. a
car, in this way of generating and
using H2 in a combustion motor, which may result 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 electrolyses of conductive H20, may be used in
the combustion
motor, so that the burning Of H2 is still more efficient (turbo-effect). The
H20 which comes free
from the burning process in the combustion 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
combustion 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 by a rotational ES VT-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 capacitor is used as the power source
for the
ESVT-pumps. The big advantage is that this capacitor can be charged in a few
minutes, and a car
may drive say 500 km, when the capacitor has the 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 H2-fuel cell 1606. Another storage tank 1600 for H2
(1601), which may be
cooled and may be pressurized, using electricity through an 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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the outside (1604) of said motor. Said storage tank 1600 is communicating
through a channel
[1605] to a H2-fuel cell 1606 wherein H2 and 02 are being transformed into
electricity, which is
charging through electric communication [1607] either start battery 832B
(short term, high current),
or service battery 832C (longduring, medium current). Said channel [1605] is
comprising a non-
return valve 1608 (not shown). The potential difference required for operating
the fuel cell 1606 is
established by said electrical communication [1602]. The start battery 832B is
electrical
communicating [1609] with the starter 830 of the motor, while the service
battery 832C is
electrically communicating [1610] with a pump 820/826 of said motor. The
motor, of which
selected elements are rehearsed here, is treated in depth in Figures 11
A,B,G,H,I,J,K,L,M,N and
Figure 12 A and Figures 13 A & B. Said motor is further comprising a pressure
vessel 814/890,
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 voltaic solar cell 833, which is
additionally charging
battery 832. The pressure storage vessel 814/890, which is being charged by a
pump 820/826. The
piston actuator module 800 of the motor, alternatively reduction valve system
1057 and 1058, as
explained earlier e.g. Fig 11G, drive the main axle of the motor 852.
Fig. 15B shows schematically a tank 1612 for (conductive) H20 (1613),
which has been filled up through a channel [1614], which is connecting said
tank 1612 with the
outside (1629) 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 H2 generated in vessel 1616 , 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 by electric communication line [1619] 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 [1611], which is communicating with the main axle 852
of the motor. Said
battery 832A is giving power through electric communication [1626] for the
electrolyses 1617 in
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vessel 1616. The battery 832C is giving power through electric communication
[1627] to pump
820/826 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 voltaic solar cell 833, which is additionally charging
battery 832. The pressure
storage vessel 814/890, which is being charged by a pump 820/826.. The piston
actuator module
800 of the motor.
Fig. 15C shows schematically the process according to Fig. 15B, where
additionally a
piston pump 1625 of the repressurisation cascade, so either 820 or 826, is
directly communicating
with the main axle 1621 of said combustion motor 1620 through a crankshaft
1636 and piston rod
1637. The photo voltaic solar cell 833 which is charging the battery 832,
besides the alternator 850,
which is communicating with the main axle 852. The battery 832 is electrically
connected to the
motor 1623 through an electric communication [1628]. The exit of the pump 1625
of motor
function 820/826 is communicating by channel [828] with the motor, and
particularly the pressure
storage vessel 814/890, according to Figs. 11A,BõG or Figs. 12A, 13A,B. In
this figure the electric
output [1628] by the battery 832 provides electric communication to other
functions of the motor,
presented in previous figures.
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 1635, which
is
communicating with said motor 1620 by axle 1621. Said rotational pump 1635 is
communicating
with pressure storage vessel 814 of Fig. 13B by channel [828]. The start motor
1623 is
communicating with axle 1621 and gets its power from battery 832 through wires
[1628] The
battery 832 is being charged by photo solar cells 833' and alternator 850
through wires [1611], and
is communicating with axle 1621. The battery 832 is connected to the motor
functions 800 by wires
[1627]. The photo solar cells 833' are providing directly H2 to the 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. In this figure
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the electric output [1628] by the battery 832 provides electric communication
to other functions of
the motor, presented in previous figures.
Fig. 15E shows schematically a capacitator 1641 for instant storage of
electricity
1642, which has been filled up through an electric wire [1643], which is
connecting said capacitor
1641 with the outside (1644) of said motor. Said capacitor 1641 is
communicating through a
channel [1645] 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 and
1621, respectively, which are communicating with an alternator 850 or 1624.
Said battery 832 is
electrically connected by wires [1611] 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 capacitor 1630
connected to said battery 832 by wires [1646] 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
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 0-rings
3312 and 3313,
between said piston 3311 and the wall 3314 of said actuator.
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.
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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. 10A-C. Even though only the ellipsoide-
ellipsoide/sphere type
piston is shown, any type of inflatable actuator piston may be used.
Figs. 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 2"d to
a 1st 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
1800 in relation to each other ('asynchrone'). The result is that the motor
delivers power at all times,
and this configuration may be used in a stand alone 2 cylinder motor, or in a
multiple (>2, and
preferably even number) cylinder motor. A flywheel may be redundant, omission
of 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.
said enclosed spaces may be separated, e.g. at the connection point of said
sub-
crankshafts (together comprising said crankshaft) by e.g. a tightening rod
1270 (Fig. 11X), which
may be positioned 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 with the
other enclosed space.
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There may be valves functioning 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 ES VT-pump and/or
by tappets, which
may be communicating with a camshaft (which may be communicating with the main
auxiliary
power line, e.g. an auxiliary H2 combustion motor) or may be communicating
with a computer (not
shown).
The change of pressure inside the actuator pistons is when said actuator
pistons are in
the 1st ,"/Lnd
longitudinal positions and in the 2n1i18t longitudinal positions,
respectively. When the
camshaft may be 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
ES VT-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 is thus 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 ESVT-pumps, whereby the
settings of the
piston-chamber combination is synchronous. The many valves may be making the
configuration
vulnerable for misfunction.
Instead of toothed belts at the power side of the auxiliary 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. 11W, 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-pump of that configuration of
the motor. It is
additionally possible that said double working piston is positioned outside
said crankshaft.
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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 1800 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
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 ESVT-pump and/or
by tappets, said tappets are-communicating with a camshaft, which is
communicating with the main
axle of an auxilliarly 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.
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.
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In Fig 17A the ellipsoide/ellipsoide-sphere actuator piston 217 is shown at
the first longitudinal position.
Said actuator piston is inflatable and runs in a chamber with different cross-
sectional areas at the first and
second longitudinal positions. The cross-sectional area and circumferential
length at the second longitudinal
position are smaller than the cross-sectional area and circumferential length
at the first longitudinal position.
Arriving at the first longitudinal position, the actuator piston is at the
final position of the power stroke.
During the power stroke the actuator piston moves from the second longitudinal
position to the first
longitudinal position under influence of the pressurised fluid inside the
piston container.
The enclosed space with which the fluid in the piston container is in constant
and open communication
remains equal during the power stroke. The enclosed space of the piston
actuator is communicating with a
channel in which a valve is controlling the volume of the enclosed space. At
the time of the power stroke the
valve is located closest to the actuator piston.
During the movement from the second longitudinal position to the first
longitudinal position a pressurised
ellipsoide shaped piston 217' has expanded into sphere shaped piston 217, and
with the expansion of the
piston container the pressure inside said piston gradually lowers. At the
first longitudinal position the fluid
inside said piston is still on a small overpressure to assure a good sealing
to the chamber walls. The shape of
piston 217 may also be ellipsoide.
Where the position of the valve remains unchanged during the power stroke, the
valve is retracted further
away from the actuator piston. Such that the volume of the enclosed space
increases and the internal pressure
drops to the pressure of when the piston was produced. The fluid in the
enclosed space and the piston
container are in constant and open communication with each other. Hence when
there is a pressure difference
between the fluid in the piston container and the enclosed space a new
equilibrium will be established.
In Fig 17A the valve moves from level "0" to "1" . The depressurised
production shaped piston 217",
located at the first longitudinal position, is ready for the return stroke.
During the return stroke the actuator
piston assembly is relocated to the second longitudinal position and the
volume of the enclosed space
remains equal, the valve setting "1" is maintained. When moving from the first
longitudinal position to the
second longitudinal position the piston is depressurised and might be free
from the wall or just engaging it,
but not seal the upper volume in the chamber from the volume underneath the
piston. The returned piston
217' " is now held by the wall of the conical chamber and keeps its shape when
pressurised to piston 217'.
Pressurisation is realised by changing the valve's position in the channel the
enclosed space is
communicating with. The valve is extended from level "1" to "0", by decreasing
the volume of the enclosed
space the pressure is increased. The pressurised piston will move from from
the second longitudinal position
to the first longitudinal position again, completing one entire cycle. The
piston expands, decreasing the
internal pressure, to the initial piston shape 217. The movement is driven by
the force on the wall of the
chamber due to overpressure in the piston and the reaction force provided in
response on the actuator piston.
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As the main axle, where the actuator piston is connected/attached to, receives
energy from the mechanical
movement it is called the power stroke. Next to a valve in the channel,
various configurations can manage
the pressurisations and depressurisation of the actuator piston.
In Fig 17B a 2-cylinder configuration is presented. Both cylinders are
identical to Fig 17A, only the internal
orientation is 1800 different. Such that when, for instance, the actuator
piston in cylinder assembly A is at the
start of the power stroke the actuator piston of cylinder assembly B is at the
start of the return stroke. In Fig
17B this is represented by rotating the cylinder configuration by 180 degrees,
but in the motor there are
multiple possibilities to realise this e.g. by placing the cylinders parallel
and rotate the crankshaft connection
for cylinder B over 180 with respect to the one of cylinder assembly A. The
cylinder pressure systems may
be communicating with each other or have their own support systems. The main
crankshaft of the motor
comprises two sub-crankshafts, one for each cylinder-piston assembly. The
cycle of the actuator piston in the
conical chamber has been explained in the description of Fig 17A and the
installation of the cylinders and the
processes in the motor are treated in Fig 17C-H.
In Figures 17C - 17H a process description is given of one complete cycle of a
motor configuration
consisting of two cylinders. The configuration of the 2-cylinder motor
disclosed consists of one main axle
comprising two sub-crankshafts, where the enclosed spaces of each chamber in
each sub-crankshaft have
been seperated by a tightening rod 1270. The cylinders run a-synchrone (180
degrees difference), so when
one cylinder starts the power stroke the other cylinder is at the start of the
return stroke, like was presented in
Fig 17B.
In the motor one ESVT pump is replaced by an inflow/ouflow connector, which is
connected to the
remaining ESVT pump. By means of valves 459/423 and 462/422 the flow to
pressurise and depressurise
both pistons is controlled. For each cylinder a set of valves is installed
according to the concept of Figs 210E
and 210F, hence one for the inflow and one for the outflow of the fluid. The
valves are controlled by
pressure and tappets in communication with the cams on a camshaft.
Both the crankshaft of the ESVT pump and camshaft are driven by an 112
combustion engine via gear wheels
and toothed wheel-belt configurations, enabling various speed (pre)settings.
In Figs 17 C-H the rotational
speeds of the camshaft, pump-crankshaft, and main axle are the same.
The remaining ESVT pump is of a special type where the volume atop the piston
is connected to one
cylinder assembly and the volume underneath the piston is connected to the
other cylinder assembly.
Because the cylinders run asynchronous, this arrangement provides the desired
pressurisation scheme; low
pressure at one side of the ESVT pump piston for the piston actuator which
needs to depressurise and high
pressure for the piston actuator that needs to be pressurised. The ESVT pump
8000 with special
configuration can be used for more motor configurations, and is for example
applicable in Figs 17C-1711.
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For each set of valves there is a cam installled on the camshaft. Each cam
provides two different signals
during one rotation, once for the inflow valve and the other time for the
outflow valve. The cams of each
valve set are installed identically on the camshaft, so that when the first
signals is provided by the first cam,
the second cam also gives the first signal, and half a rotation further both
cams give the second signal.
Because the cylinders run asynchrone: when the first signal from the first cam
is used for the inflow valve,
the first signal from the second cam is used for the outflow valve of the
other cylinder assembly, and vice
versa for the second signal. A different configuration of the cams is possible
as well, as long as it leads to the
desired functioning of the valves.
The valves are of a special type, as described in Fig 211E! Only when the
valve piston is closed and there is
an over-pressure in the direction of the valve actuator a flow is possible.
The over-pressure is with respect to
the outflow chamber of the valve plus the preset strength by the spring force
supporting the piston core. The
channel within the valve is in communication with the inflow chamber of the
valve. By equal pressure in the
inflow chamber and valve channel the valve actuator is kept in place, hence
closed position. When the valve
piston receives a signal by the appropriate cam and closes, the communication
between the valve channel
and inflow chamber is cut off. When in this setting an over-pressure occurs,
the valve opens. At the moment
the valve piston closes it does not only block the communication line of the
valve channel with the inflow
chamber, but also opens a channel for communication from the valve channel to
the outflow chamber. Such
that the pressure in the valve channel switches upon closure of the valve
piston from the inflow chamber's
pressure to the outflow chamber's pressure. The pressure in the valve channel
does not need to be overcome
as it is in equilibrium with the outflow chamber. Upon removal of the signal
from the valve piston by the
cam the valve actuator returns to its closed position, the communication by
the valve channel to the inflow
chamber is re-established and the communication to the outflow chamber is cut
off.
For the inflow valve of the valve set, controlling the pressurisation of the
actuator, the ESVT pump is the
inflow chamber side and the piston actuator with accompanying enclosed space
the outflow chamber side.
For the outflow valve it is the other way around. The valve piston is closed
by the cam signal, which is once
per rotation of the camshaft. When during such closure of the valve piston the
pressure difference over the
valve is positive a flow of fluid into or from the cylinder is possible.
Furthermore the motor is based on the configuration of Fig 11R and the
auxilliarly power source, a H2
combustion engine, is according to Fig 15D.
For Fig 17C the cylinder 800L is at the second longitudinal position and
cylinder 800R at the first
longitudinal position. The ESVT pump decreases the volume atop in the cylinder
and pressurises the fluid in
the channels of cylinder assembly comprising 800L. By decreasing the volume
atop, the ESVT pump
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increases the volume underneath and hence lowers the pressure in the 800R
cylinder system. The camshaft is
providing a signal to the inflow valve of the channel in communication with
cylinder 800L. The valve piston
closes, the pressure in the channel of the valve is brought in equilibrium
with the pressure in the enclosed
space associated with actuator piston of 800L. The pressure from the ESVT pump
builds up and is larger as
the pressure in the enclosed space in direct and open communication with
cylinder 800L. By the over-
pressure the valve actuator pushes the core pin aside and the fluid can flow
in the direction of the cylinder
800L, pressurising the piston and preparing it for the power stroke. The
outflow valve of 800L does not
receive a signal, hence the valve piston is open and no flow is possible.
The camshaft has a second cam, which also gives the first signal, for cylinder
assembly 800R. As the
cylinders run asynchronous the communication of this first signal from the
second cam is with the outflow
'valve of 800R. The valve piston of the outflow valve of piston 800R closes
and hence a flow from the
actuator piston to the ESVT pump is possible. The inflow valve of 800R does
not receive a signal, and hence
no flow of fluid towards the actuator piston is possible. At the moment of Fig
17C the piston actuator of
800R is in the first longitudinal position, at the end of the power stroke and
starting the return stroke. The
piston container is still at a little over-pressure to assure good sealing and
contact to the wall. The ESVT
pump's lower end has increased its volume and hence decreased to low pressure.
By closure of the valve
piston the valve channel's communication switched from the actuator piston and
associated enclosed space
to the ESVT pump. The overall pressure situation is such that there is an
overpressure over the valve actuator
from the actuator pistonand associated enclosed spaces to the ESVT pump. A
flow will initialise from the
piston and enclosed space towards the ESVT pump, this flow will continue until
the pressures at both sides
of the valve are in equilibrium (neglecting the small force of the spring
supporting the core pin), or when the
valve piston opens again and interrupts the communication.
Fig. 17C left shows a scaled up left part of Fig.17C.
Fig. 17C right shows a scaled up right part of Fig.17C.
In Fig 17D the motor system axles have rotated one sixth of a rotation
further. In Fig 17C the ESVT pump
was decreasing the volume atop of the piston, and in Fig 17D the the piston is
staying in a position where the
volume atop is small and the volume underneath is large. By the rotation of
the crankshaft the fluid above the
piston is slightly more compressed, and underneath more expanded. The
pressurisation by the ESVT pump
could also be split in a top half with high pressure and a lower half with low
pressure, by which the shift
from one side to the other side is of importance to indicate the change with
the earlier situation. This split in
a top and lower half applies for the cylinder assembly 800L, and for cylinder
assembly 800R the situation is
opposite. Next to the crankshaft determining the volumes in the ESVT pump also
the camshaft has rotated.
In this new situation the cams provide no input signal to any of the valves.
Consequently the valve pistons
are open and no flow towards or from the actuator piston and enclosed spaces
is possible. The pressurised
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piston in cylinder assembly 800L is moving from the second longitudinal
position towards the first
longitudinal position by the resultant reaction force of the wall exerted upon
the piston.During the upward
movement the piston expands under influence of the piston internal pressure,
maintaining a good sealing and
contact to the chamber's wall. The piston of assembly 800R is depressurised
and moving downward with no
contact to the wall or just engaging the wall.
Fig. 17D left shows a scaled up left part of Fig.17D.
Fig. 17D right shows a scaled up right part of Fig.17D.
In Fig 17E the piston of cylinder assembly 800L arrives at the first
longitudinal position, the end of the
power stroke. The actuator piston of cylinder assembly 800R, still
depressurised, arrives at the second
longitudinal position, the end of the return stroke. The various shafts have
rotated 60 degrees further. The
piston of 800L has maximally expanded into the chamber and is still under a
little over-pressure to assure a
good sealing to the walls. The pressure inside the piston of 800L, and hence
the pressure in the channel
communicating with piston 800L is at its lowest value of the power stroke at
the highest position in the
chamber (or at the first longitudinal position). The camshaft is not providing
a signal to the valves and hence
the valve pistons are open and no inflow or outflow is possible. The ESVT pump
driven by a connector to
the crankshaft, is still oriented such that the volume atop the ESVT pump's
piston is minimal and
consequently resulting in a high pressure, and the volume underneath the
piston remains large with a low
pressure.
During the first half of the process in Figs 17C-17E the piston actuator of
cylinder 800L has performed the
power stroke, providing power to the main axle. The main axle rotates with the
same speed as the crankshaft
and camshaft. The piston actuator of 800R only translates, at the cost of
minimal work, from the first to the
second longitunal position. This required work is provided by the main axle.
Other elements requiring energy
are powered by the auxilliarly power source, for example the crankshaft and
camshaft.
Fig. 17E left shows a scaled up left part of Fig.17E.
Fig. 17E right shows a scaled up right part of Fig.17E.
In Fig 17F the cams on the camshaft are providing a signal again. The camshaft
has rotated further and
rotated up to here over 180 degrees, relative to the starting situation in Fig
17C. Also the signal by the cam is
the other one as the one effective in Fig 17C. The signal is closing the valve
piston of the outflow valve of
cylinder 800L. The pressure in the valve channel is equal to the little over-
pressure in the piston actuator at
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the end of the power stroke. With the closure of the valve piston the valve
channel exchanges fluid with the
ESVT pump to balance these two pressures. The ESVT pump piston has made a
stroke to enlarge the volume
atop of the piston and consequently decrease the pressure in this space. The
little over-pressure of piston
actuator 800L is having a positive pressure difference over the valve outflow
chamber's pressure, being
equal to that of the ESVT pump's top end. The positive pressure difference
will move the valve actuator,
pushing the core pin aside, and enable a flow of fluid from the actuator
piston towards the ESVT pump. This
depressurises the piston and prepares it for the return stroke, where it has
to be free from the wall or just
engaging it. As the valve piston of the inflow valve for 800L does not receive
a signal by the cam it remains
open, and does not allow a flow through the valve.
For the valve set controlling the pressurisation of the piston and associated
enclosed spaces of 800R, the
signal by the second cam closes the valve piston of the inflow valve. The
outflow valve's valve piston
remains open and hence does not facilitate a flow from the piston to the ESVT
pump. With closing the valve
piston of the inflow valve the valve channel's pressure is brought in
communication with the internal volume
of the depressurised piston, having just finished the return stroke to the
second longitudinal position. As the
ESVT pump had made a stroke and the volume underneath the ESVT pump's piston
has decreased and the
fluid in this volume is pressurised. The pressurised fluid in the ESVT pump
with which the cylinder
assembly 800R is in communication is resulting in a positive pressure
difference over the valve actuator.
This pressure difference enables a flow from the ESVT pump to the actuator
piston and associated enclosed
spaces. Bringing the piston container under pressure, which consequently wants
to expand, but as the
piston's outside is held by the walls of the conical chamber it instead exerts
a force on the walls, which
results in a reaction force on the piston. This reaction force has a component
in the chamber's longitudinal
direction and drives the piston. So by pressurising the piston of 800R it can
perform the upcoming power
stroke.
In Fig 17F the situation of cylinder assembly 800L and 800R is that of the
other cylinder assembly half a
cycle before in Fig 17C. The pressures, valve settings, longitudinal
positions, etcetera, are comparable to
what it was in Fig 17C for the other piston to have the motor operating
smoothly.
Fig. 17F left shows a scaled up left part of Fig.17F.
Fig. 17F right shows a scaled up right part of Fig.17F.
In Fig 17G and 17H the axles rotate each time a sixth rotation further,
completing the cycle. The cams on the
camshaft give no signal in these two steps. Consequently the valve pistons of
the inflow and outflow valves
of both valve sets remain open. As valve pistons are open the pressures
pushing on the actuator valves, from
each valve's inflow chamber, is counteracted by the valve channel's pressure,
which is in constant
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communication with the valve's inflow chamber. As the valve actuators remain
in position no flow between
the ESVT pump and piston actuators takes place.
Also the setting of the ESVT pump remains comparable to that of Fig 17F. The
volume above the piston in
the ESVT pump remains large resulting in a low pressure of the fluid atop,
this volume is communicating
with the cylinder assembly 800L. And the volume underneath the piston, in
communication with the cylinder
assembly 800R, is kept small, resulting in a high pressure. As there is no
flow of fluid in Fig 17G,H it is of
no further consequence, but for the transition again from Fig 17H to Fig 17C,
it is the pressure change by the
return stroke of the piston in the ESVT pump that is of importance to create
the positive pressure differences
for the appropriate valves.
In Fig 17G the piston assembly 800L is moving from the first longitudinal
position to the second longitudinal
position. The piston moves from the first longitudinal position to the second
longitudinal position. The piston
is in an unpressurised state and is free from the chamber's wall, or just
engaging the walls. At the same time
cylinder assembly 800R is performing the power stroke from the second
longitudinal position to the first
longitudinal position. Hereby the pressurised piston expands, lowering the
internal pressure and maintaining
a good contact to the conical chamber's wall.
In Fig 17H the piston actuator of assembly 800L finishes the return stroke and
arrives in the small end of the
conical chamber, here the cross-sectional area and circumferential length are
smallest. The pressurised
actuator piston of cylinder assembly 800R arrives at the first longitudinal
position, where the piston has
maximally expanded in the conical chamber's large end, where the large cross-
sectional area and
circumferential length are largest. There remains a little over-pressure in
the piston to assure a good sealing
to the walls up to the last movement of the power stroke. At this point the
normal direction of the walls is
perpendicular or almost perpendicular to the chamber's longitudinal axis.
Fig. 17G left shows a scaled up left part of Fig.17G.
Fig. 17G right shows a scaled up right part of Fig.17G.
Fig. 17H left shows a scaled up left part of Fig.1714.
Fig. 171-1 right shows a scaled up right part of Fig.17H.
The next step in the ongoing operation of the motor is the same as Fig 17C
again. Hence this cycle of six
intermediate steps of Fig 17C-H describe the full cyclus of the motor
comprising two cylinders operating
asynchronous.
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In Fig 171 an example is disclosed of how it could look when the ESVT pump is
installed at the connection
of the two sub-crankshafts. The motor elements are identical to the motor
described in Fig 17C-17H. The
ESVT pump may be operated by a mechanism inside the cylinder which is in line
with the crankshaft's axis
e.g. a worm wheel or an installation by springs. The piston inside the
straight channel forming the ESVT
pump may also be driven by an external system. The two-way piston is moving in
the chamber and thereby
enlarges the volume of the enclosed area it moves away from and decreases the
volume of the enclosed space
it moves towards. Respectively lowering and increasing the pressure in the
enclosed spaces. The piston
simultaneously seals both enclosed areas.
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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 0 from each other.
This is done by a configuration of two identical piston-chamber combinations,
where
the rd longitudinal position of one cylinder is at the same geometrical level
of the 2' 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 gap 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 ES VT-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 crankshafts 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. 11X). A power balance may arise in said motor, whereby the power
srokes of the
various actuator pistons are configured such that the motor provides a
constant power.
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In Figs 18B - 18G the pressurisation scheme of the motor during one cycle is
disclosed. The motor has
a two cylinder configuration as shown in Fig 18A. The piston actuators of each
cylinder assembly are
continuously at the same stage in the cyde, the piston actuators run in
parallel.
The motor is based on Fig 11R as well, as the motor of Fig 17C-17H was based
on this concept, the
major differentiation is in the piston pressurisation. The auxilliarly power
source is an H2 combustion
engine, which is forced liquid cooled. The mixilliarly power source provides
work for the pumps,
battery and crankshaft.
The two piston actuators installed on the crankshaft are connected to one ESVT
pump. As the
pressure scheme of both pistons is equal, the pressure settings required from
the ESVT pumps by the
pistons actuators are the same. This allows simple joining of the two ESVT
pumps for each actuator
piston independently into a single shared ESVT pump1055, only the size hereof
might possible be
adapted. Next to the ESVT pump also one piston chamber combination 1050 is
installed for the
= pressure/speed control in this 2 cylinder configuration. The
communication between the two actuator
pistons takes place at the connection of the two subcrankshafts, where the
second and third enclosed
spaces are connected as disdosed in Fig 11 W or W'.
No valves are installed between the ESVT pump and the enclosed spaces or
piston actuators of
assembly 800L and 800R. To interrupt the connection between the ESVT pumps and
the actuator
piston, the connector contains holes to enable a flow of fluid towards or from
the ESVT pump, or
block this communication and set the amount of fluid in the enclosed space and
associated piston. An
example of such a facilitating connection between the actuator piston assembly
and a crankshaft with
an enclosed space is given in Fig 11T.
In Fig 18B the communication line from the enclosed spaces in subcrankshafts
to the associated piston
actuator is open allowing a flow of fluid. The actuator pistons have just
finished the return stroke and
are at the second longitudinal position. The ESVT pump's crankshaft has made a
stroke upward
decreasing the volume inside the chamber and increasing the pressure of the
fluid in the ESVT pump.
With the communication line to the actuator pistons being open the pressurised
fluid can flow into the
depressurised actuator pistons. During the return stroke the actuator pressure
are depressurised not to
touch the walls or just engaging it, not to seal the volume in the chamber
underneath the piston from
the volume above. And with the pressure in the ESVT pump being larger as the
pressure in the piston
actuator, the high pressure fluid flows into the piston actuator. The
pressurisation of the actuator
pistons establishes a good contact to the chamber walls and the overpressure
makes the piston actuator
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prone to expand, which is obstructed by the chamber wall, but due to the
conical shape the reaction
force results in the upward movement of the piston actuator towards the first
longitudinal position.
Fig. 18B left shows a scaled up left part of Fig.18B.
Fig. 18B right shows a scaled up right part of Fig.18B.
In Fig 18C the piston actuators are halfway the power stroke of the motor, the
crankshaft of the motor
is rotating upwards. The situation for both cylinder assemblies is equal, as
the piston actuators move
synchronous. The crankshaft of the motor has rotated a little further dosing
the communication line
between piston actuator and the enclosed space in the subcrankshaft, which is
in constant and open
communication with the ESVT pump. By the over-pressure the pistons expand into
the enlarged area
of the conical chamber. The piston's internal pressure decreases as there is
no communication with the
ESVT pump and the internal volume has increased. The ESVT pump maintains the
small volume in
the chamber, keeping a high pressure in the connected systems.
Fig. 18C left shows a scaled up left part of Fig.18C.
Fig. 18C right shows a scaled up right part of Fig.18C.
In Fig 18D the piston actuators arrive at the end of the power stroke. The
pistons have maximally
expanded in the conical shaped chamber. The pistons have moved to the first
longitudinal position in
the chamber. Although the volume in the actuator piston has increased, the
fluid inside the piston is on
a little over-pressure to establish a good contact to the chamber walls for
the whole power stroke. The
crankshaft of the motor where the pistons are connected to, comes at a semi-
rotation with respect to
starting situation in Fig 18B. The holes in the connector from the piston rod
to the enclosed space in
subcrankshaft are closed, consequently there is no communication between the
piston actuator fluid
and the ESVT pump, or other piston actuator, as the enclosed spaces of the
subcrankshaft are
connected at the . The amount of fluid in the piston remains the same. The
fluid in the ESVT pump is
at high pressure by the small volume in the chamber.
Fig. 18D left shows a scaled up left part of Fig.18D.
Fig. 18D right shows a scaled up right part of Fig.18D.
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In Fig 18E the crankshaft of the motor has turned a little further, whereby
the holes between the
enclosed space in the crankshaft and the piston rod open and a flow of fluid
is possible. The crankshaft
of the ESVT pump has made a stroke such that the connected piston in the the
ESVT pump is moved
away from the pump chamber's outflow and the volume in the ESVT pump is
enlarged and the
pressure decreased. The decreased pressure in the ESVT pump is less as the
little over-pressure in the
piston, and consequently the fluid from the piston will flow out in the
direction of the ESVT pump,
depressurising the piston. By loosing the internal pressure the piston changes
shape, from the sphere-
ellipsoide shape in contact with the walls at the first longitudinal position,
to an ellipsoide shape free of
the wall or just engaging it. The piston may also be of a different
configuration with an accompanying
shape scheme that can differ from this one. The piston actuators of both
cylinder assemblies 800L and
800R are at the start of the return stroke.
Fig. 18E left shows a scaled up left part of Fig.18E.
Fig. 18E right shows a scaled_up right part of Fig.18E.
In Fig 18F the actuator pistons 800L and 800R are in the middle of the return
stroke. The crankshaft of
the motor is moving downward, providing the work to move the depressurised
cylinders from the first
to the second longitudinal position. The actuator pistons remain depressurised
as the communication in
the connector is interrupted again. The amount of fluid in the piston systems
remain equal, and as the
volume remains the same the pressure is also constant. The piston stays in the
shape it has at the end of
the stage presented in Fig 18E. The volume of the chamber in the ESVT pump
remains large such that
upto closure of the communication to the piston the fluid in the piston flows
in direction of the ESVT
pump.
Fig. 18F left shows a scaled up left part of Fig.18F.
Fig. 18F right shows a scaled up right part of Fig.18F.
In Fig 18G the piston actuators complete the cyde and arrive at the second
longitudinal position. The
ESVT pump is slightly decreasing the volume in the chamber again, but the
pressure stays low. Also
the holes for communication between the ESVT pump and actuator piston are
dosed. During the
power stroke the piston actuators perform work on the crankshaft to power
connected systems, while
during the return stroke of both piston actuators the crankshaft is providing
work to move the piston
actuators, consequently the power supply by the motor is not constant.
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Fig. 18G left shows a scaled up left part of Fig.18G.
Fig. 18G right shows a scaled up right part of Fig.18G.
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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 auxiliary power source is e.g. chosen as a
combustion motor, which
is burning H2, derived from electrolyses of 1120. The water reservoir 1612 can
be filled with 1-120 1613
through filler opening 1614 by an external source. From said water reservoir
1120 can be transported to
vessel 1616 by channel [1615]. The power required to perform the electrolyses
1617 in said vessel is
provided by communication line [1069] which is in contact with the battery
832. Battery 832 may be
charged by solar voltaic cells 833 and receive energy by the alternator 850.
Said alternator is in
communication with the main crankshaft 852 of the motor by a toothed belt and
gear wheels. The
battery may be providing a signal to the electric starter motor 830. Another
communication line [1064]
from the battery may be giving input to the reduction valve 840, which
controls the fluid flow from the
pressure storage vessel 814 through channel 829 to the inflow connector of the
second enclosed space
of the piston cylinder assembly 800L. The setting of the check valve 840 is
controlled by speeder 841.
The output of the electrolyses process, H2, is fed by channel [3545] to the
combustion engine 3525.
Optionally the 02 is transported, by a separate channel [3546], to the
combustion engine 3525. In said
engine, under control of a signal by communication line [1069], the H2 and 02
are processed at the
creation of water, which may be fed in return (not shown) to said water
reservoir 1612. The
combustion engine can also generate heat which may be conducted away by a heat
exchanger and used
for a secondary application outside this motor. The combustion engine powers a
shaft to which piston
pump 826 is connected. Said piston pump pressurises the fluid that comes by
channel [825] from the
outflow connector on the crankshaft, connected to the third enclosed space of
the cylinder assembly.
The free end of crankshaft 852 can be connected a flywheel 835, clutch 836, or
gearwheel 837 (not
shown).
The piston assembly 800L operates according to the consumption technology as
described in Fig 11A.
The fluid in the second enclosed space in the crankshaft is at the pressure of
the pressure storage vessel
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814 or a reduced pressure after passing by reduction valve 840, while channel
[825] connected to the
outflow connector is at a low pressure, although the pressure can differ by
the one way direction valve
at the end of said channel controlling a positive pressure difference with
respect to the pressure of
piston pump 826. The piston actuator is connected to the crankshaft with a
connector described in Fig
11D. The second and third enclosed space are not in communication with one
another, as the channel is
interrupted in the connector. Said connector allows a flow of the fluid from
the second enclosed space
with the piston actuator at the second longitudinal- position. And between the
third enclosed and the
piston actuator when the piston assembly is in the first enclosed position. At
said first longitudinal
position the little over-pressure, still present in the actuator piston,
establishes a flow of fluid into the
third enclosed space due to the lower pressure in channel [825]. The piston
becomes depressurised and
free from the chamber's wall or just engaging it, not to seal the volume above
the piston from the
volume underneath. During the return stroke, by the rotation of crankshaft
852, the communication
between the second and third enclosed space with the piston actuator is
closed. And when the piston
arrives at the second enclosed space the communication with the second
enclosed space is open. Said
actuator piston is depressurised and the second enclosed space is at the
pressure by said pressure
storage vessel and said reduction valve, consequently the flow of fluid will
be in the direction of the
actuator piston. The pressurised piston expands in the chamber and by the
force on the wall receives a
reaction force in return. This force drives the actuator piston upward to the
first longitudinal position.
Said expansion of the piston and movement to the first longitudinal position
is the power stroke.
Fig. 19B shows a two cylinder motor, based on Fig. 19A with Consumption
Technology,
where the two cylinders have been positioned mirrored to the center line of
the connection of the sub-
crankshafts. The 314 enclosed spaces (exits) of the two piston actuators 800L
and 800R 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 (synchronous),
according to the principle
of Fig. 18A.
When more than two cylinders are needed in a motor according to this synchrone
principle, more
cylinders may be added, so that e.g. another 2'1 enclosed space may be
connected to the not yet used
end for a connection to the 2nd enclosed space of the added cylinder, so that
a 3-cylinder motor is
created. The then still free 3rd enclosed space of the added cylinder may be
connected to a 3rd enclosed
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space of another added cylinder, so that the motor may function with 4
cylinders. The now shown
closed ends of the channels of the sub-crankshafts may need than to open up to
establish
communication between enclosed spaces with equal pressure schemes.
Fig. 19B left shows an enlargement of the left part of Fig. 19B.
Fig. 19B right shows an enlargement of the right part of Fig. 19B.
Fig. 19C shows a two cylinder motor, based on Fig. 19A, which is in
pressurisation
process comparable to Fig 19B. Fig 19C depicts that the configuration of a
motor with synchronous
operated pistons may be differing from a motor where the pistons are instolled
in the same direction
(0 ). In the configuration of Fig 19C the power strokes of the piston
actuators occur at the same
moment, but the orientation of the actuator piston 800L is rotated over 180'.
Said re-orientation is both
in the connection to the crankshaft as in the direction of the conical
chamber, where the piston actuator is
moving in, and consequently the power stroke is oriented in the opposite
direction. Each second enclosed
space in the sub-crankshafts is connected to the pressure storage vessel by
channel [829] and the
enclosed spaces are communicating with each other by external channel [825].
The third enclosed
spaces are communicating with each other via the external channel facilitating
the flow from the
actuator pistons to the piston pump. At the connection of the two sub-
crankshafts, the enclosed spaces
are interrupted and there is no communication between the piston assemblies
800L and 800R.
Fig. 19C left shows an enlargement of the left part of Fig. 19C.
Fig. 19C right shows an enlargement of the right part Fig. 19C.
Fig 19D shows a two cylinder motor, based on Fig. 19A, where the piston
actuators run
asynchronous. When piston assembly 800L starts with the return stroke, piston
assembly 800R starts
with the power stroke. Consequently, one piston actuator is in the second
longitudinal position when
the other piston actuator is at the first longitudinal position, and vice
versa. The orientation of the
actuator pistons is in opposite direction ( 180 ). As there is at every moment
a power stroke and a
return stroke, the power supply by the motor of 19D is continuous and of a
rather constant level. The
enclosed spaces of each cylinder assembly are not connected via the sub-
crankshafts, the pressurisation
channel [829] communicates with both second enclosed spaces. The channel [825]
between the third
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enclosed spaces communicates also to piston pump 826. Because the openings in
the connector from
the second or third enclosed space to the actuator piston are differing half a
cycle between piston
assembly 800L and 800R, the communication by the pressure channels between the
piston assemblies
is limited to the enclosed spaces. As there is no communication through the
connections between the
sub-crankshafts the channels [825] and [829] are external.
Fig. 19D left shows an enlargement of the left part of Fig. 19D.
Fig. 19D right shows an enlargement of the right part Fig. 19D.
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.
20
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19620 DESCRIPTION OF PREFERRED EMBODIMENTS
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 1. 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 / 13 / 15 / 17 / 19 / 21 /
23 / 25 and
27, respectively, between the longitudinal cross-sectional sections 12 / 14 /
16 / 18 / 20 / 22 /
24 / 26 / 28 / 30 of the chamber 1 at a longitudinal position where 1 / 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 equation had been followed ¨
this is done for
design purposes, so as to avoid that the chamber is looking top 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 on the piston as a result of the shape of
the chamber in a
longitudinal direction, measured from a first to a second longitudinal
position). 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 longitudinal 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
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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 (250 N). The result is the characteristic shape 1
of the chamber
(WO/2008/025391).
Fig. 21B shows the shape 1 (continuous 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 the maximum overpressure should be bigger than
10 Bar, e.g. 16
Bar. This may be accomplished by choosing a higher maximum work force, so that
the
circumference of a transversal cross-section may become bigger. This means
that the conical
shaped outer wall of the chamber can go nearer 2nd longitudinal positions,
before the
circumference reaches its minimum value in order to ensure, that a piston
would not jam,
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 circumference becomes smaller ¨ this
may also be the
case for other common borders as well.
A task to optimize the chamber to demands toward handpumps can be done in
similar ways, as those described above. The problem here to be solved is a
good compromise
between 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 maximum
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 the chamber 1 on the
foot 41. The
hose 43, which is connected to the exit 44 of the pressure expansion vessel 49
¨ this exit is
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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 atmosphere (48), and is opening towards the chamber 1, so as to fill
the chamber 1
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 1 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 0-ring 55, while the top end 53 and the
bottom end 54 are
sealed to the wall 52 of the expansion pressure vessel 49 by gas sealing
thread 58 and 59
respectively.
This is a preferred embodiment for very high pressures (e.g. 16 Bar), and 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 longitudinal
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 inner 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 of said
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
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parallel to the centre axis of said chamber may be chosen as a straight line,
but not necessarily
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 manchet 71 keeps the cone formed chamber 80 of Fig. 3 in place. The
inside wall 81
of the chamber 80 is parallel to the centre axis 85 of the chamber 80. The
inflatable piston 73.
The enclosed space 66. The tube 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 Bar overpressure chamber of the
chamber
1 of Fig.21. It's second longitudinal positions end with a common 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 gas thread
102, which makes a gas tight connection. In the bottom 103 of chamber part 100
is an exit 104,
in which a hose nipple 105 has been screwed. The chamber part 100 is
comprising a piston
106, which has been schematically drawn. The piston 106 is comprising a hollow
piston rod
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 hose 110 assembled with a hose clamp 111. The hose is
at its other
end connected to e.g. a valve connector 67. The hole 112 in hose 110.
30
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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.
Fig.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.
The
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 there, around the circumference of the chamber 1749, from both sides
(1786/7/8/9/90/91, 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.
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Fig. 32C shows the cap geometry ¨ for area and internal volume of the cap we
need values of a and h only - see 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. 32E shows the piston with end caps inside a transparent Fermi tube
hamber.
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.
Fig. 32H shows a section of the chamber wall. The chamber reaction force is
marked by gray (1800). 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 proportional to the
longitudinal width of the
section, which again is linear 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 plane
to have a linear (or just increasing) value as function of arc length along
the generator circle.
Fig. 321 shows the section of Fig. 32H, with an additional section in order to
provide an open view.
Fig. 32J shows Fig. 32H, and the red (1801) vector is the component of the
gray force
(1800) in the longitudinal direction.
Fig. 32K shows Fig. 323, 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 (1802) ¨ it is obtained by projecting the red (1801) vector
orthogonally to the chamber wall.
Fig. 32M shows Fig. 32L, with an additional section in order to provide an
open
view.
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19640 DESCRIPTION OF PREFERRED EMBODIMENTS
Fig. 40A shows a longitudinal cross-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 piston rod 1507
above the axle 1510, and at the other end on the -support 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. 40B, 41D,
41E), which has been vulcanized on a layer without reinforcements 1513. The
centre axis 1518 of
the chamber 1506. The angle a 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 flexible 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 0-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 0-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 0-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 together. The
angle f3 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
a 43
13 parallel to the centre axis
the foam may comprise stiffeners, which may be rotatably fastened to the
piston rod,
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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
bended flat surface
1516 at the end of the support means 1502, which is vulcanized on the 0-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
partially 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 spiral reinformcements 1522, 1523, 1524 of the flexible
impervious sheet 1504 ¨ the material is flexble. 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
elastically
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 angle a 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 with 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-E), while the bottom layer 1534 has no
reinforcements.
The angle l3 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.
180 -iz 110 (> 90 )
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Fig. 42C shows a longitudinal cross-section of the piston 1530 of Fig. 42A at
a
second longitudinal position. The angle between the flexible impervious
sheet 1531 and the
centre axis 1518 of the chamber 1506.
1800- rz 950( > 90 )
=
20
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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 bended 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 independant of
the pressure (see
19620). The wall 1207 of said shamber 1202. All stiffeners 1208, (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 bend
1217, (1218),
1219, repectively and a small bended end 1220, (1221) and 1222, respectively.
Said small bended
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 0-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 within a 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.
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19650-1 DESCRIPTION OF PREFERRED EMBODIMENTS
Fig. 55A shows a piston 1300 at a 1st 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 rod 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
aplication) ¨ the venting of said open cells is being discussed in Fig. 55B.
The holder 1308 has a
gland 1317 for an 0-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 2nd 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
1st 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 longitudinal position where
the piston has the
reference 1300'. The low pressure side 1315 of the piston 1300, and the
atmosphere 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.).
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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 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
off end 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 holder 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 1st
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
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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 551) 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 turn clockwise, when the piston is running to a 18t
longitudinal position.
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19660 DESCRIPTION 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 on the piston rod is
approx. even dureing the stroke. The shape of the piston at a second
longitudinal position is that of a
'starting' ellipsoide 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 ellipsoide 1404, which is almost a sphere
1405 (dashed). In between has
the piston 1400 the shape of an ellipsokle. The details of an ellipsoide
instead of a sphere at a first
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 ellipsoide or a sphere. At the bottom of the figure the non-
movable cap 1420, with a gland
1421 for a 0-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 of the
piston 1400 on a bolt (not shown)
which locks the bottom of the piston rod (not shown), through the hole 1432.
On top of the figure the
movable cap 1423, which is -movable on the piston rod (not shown). The gland
1424 for an 0-ring (not
shown), which makes the piston tight in the top of saud 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, respectively. 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 of the other layers
1428 and 1429, respectively,
which is only present on the position where said two layers 1428 and 1429,
respectively have been
vulcanized on the cabs 1420 and 1423. The centre axis 1433. The wall 1427 of
the piston 1400 is
approximately parallel with the centre axis 1433. The reinforcement strengs
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 off transition 1436 and
1437. These transitions 1436 and
1437 provide a stable transition of the wall, when the piston is being
stressed by inflation.
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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 the 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 the wall of the actuator
piston (not shown ¨
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 a
between the wall
2275 of the chamber 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 13 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 wall 2293 of said chamber 2291 has
an angle with the
centre axis 2292 and is drawn of 100. 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
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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 (1st, middle and 2"d,
resp.), the wall 2105 of said
piston 2104 is comprising a 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 scaled 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 bend more, which enables said separate wall part to
remaining sticking out
of the wall 2105, and arranging thereby a clearance with the wall 2103 of said
chamber 2101 with
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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 1st longitudinal position than when said piston is on a 2nd 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.
80B). 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 2" 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"
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
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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, specifically when said piston is moving from an extrimite
2" 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 1st
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. 81A 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" longitudinal position), concave-
(transition from extremite
2" longitudinal position to a position nearer a 1s1 longitudinal position),
and convex wall (from said
transition to a lst 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 1st 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 positioned 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
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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, with the goal to avoid a
continuous 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
to the wall 2136 of said piston 2140' and the wall 2103 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. 81B.
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 arrow 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 may be used) with a longitudinal 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 wall 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,
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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 1st longitudinal position is closest to the
wall 2103 of the chamber
2101, that the wall part 2148, which is nearest a 2' 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
the 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 1st 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 0 z, while the wall part 2148 has a wall
part 0 z-z1 (z1>0). The
transversal centre line 2153" of the piston 2145".
Fig. 83A shows the piston 2121" of Figs. 82A-D (incl.), as produced in a 2nd
longitudinal position, and the piston rod 2151.
Fig. 83B shows the piston 2121 of Fig. 83A at a 1st 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 1st longitudinal position,
where said
piston 2121 is being deflated ¨ arrow 2153 ¨ through its piston rod 2151,
after the position of the
movable cab 2154 has been secured on the piston rod 2151, by a clamp 2155.
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Fig. 83D shows the piston 2121 of Fig. 83C in a 1st longitudinal position,
where the
cavity (not shown) (2156) of said piston 2121 is being filled ¨ arrow 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 1st 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 1st
longitudinal position to a
2nd 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 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.
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
W02111/000578.
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.
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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 W02111/000578, 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 ellipsoIde 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 toratl, while the expansion of the
wall of the piston has
been remained. This means that when an inflated piston is pushed from a 1st
longitudinal position to
a Tid longitudinal position the rise 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 lot 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 (id). Said wall 2175 is
has on the inside a U-
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shaped vault 2177, in which an inflatable toroid 2178 is positioned, which has
a wall 2179 with an
reinforcement 2180, so that the circumferencial 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 2" 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 1st logitudinal position,
having a reinforcement 2180
which having an angle more than 540 44'. The flexible hose 2182 is through its
channel 2190
40
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 1st and 2"
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" to a 1st 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 2"
longitudinal position of a chamber. The cross-section of the flexible hose
2182 with its channel
2190. Said channel 2190 is at one end communicating 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 toroid
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.
8311/I.
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 in Fig. 84A.
Inside the wall 2202 of
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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 showri here). At the high pressure end of said piston
rod 2209 is a pressure
sensor shown which has been discussed in Figs. 83H/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 1st longitudinal position and
2230"
at a 2"d 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 2"d
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 1st 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.
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Fig. 84F shows a sphere shaped piston 2241 at a 1st longitudinal position and
2241" at
a 2nd 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 2nd
longitudinal position. The inflation of the toroid 2244 may be done as shown
in Figs. 84A or 84B.
15
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19690-2 (multiple) rotating pistons and chambers and vice versa ¨ gearboxes
Rotating Piston
Figs. 90AB are showing a piston which is turning around in a chamber, within
said
chamber, which may be fixed, but always able to counter the torque derived by
said piston. An
enclosed space (channel) may be part of the axle, around which its centrum
said piston is turning,
just alike a piston moving on a crankshaft ¨ based- on e.g. Figs. 11A (cT4),
11G (ESVT2), 111
(ESVT5). The centre of said axle may preferably be identical with the centre
of said chamber, and
the axis of the connecting rod may preferably be positioned perpendicular to
the axis of the axis of
the axle. A connecting rod between said piston and said axle may comprise the
enclosed space of
said piston, and this enclosed space may be communicating with the space
within said piston and
with said enclosed space in said axle. When e.g. a sphere shaped piston is
being used, may the
extension rod which is connecting said sphere with the channel in the axle, be
constructed alike the
rod shown in Figs. 14F and 14G, such that the length of the connecting rod may
constantly adapting
to the current distance between the centrum of said piston and the centrum of
said axle (Figs.
90C,D). It depends on how the connecting rod is being connected to said axle,
which pressure
management technology may be used: CT and/or ESVT, or a third type. The CT
demands a valve
function, which means a sequential open/close connection between the channels
in said connecting
rod, and the channel in said axle. The ESVT demands an open connection between
said channels.
The possibilities for the construction of the joint between the connecting rod
and the
axle depend additionally on how the torque is being transferred from the
piston, through the
connecting rod, to the axle, when the chamber may be fixed. Transferring the
torque from the piston
through the connecting rod to a rotating axle means that there is a fixed
connection between said
two construction elements. When an ESVT pressure management system is desired
may the
construction of said joint be relatively simple: a fixture (e.g. teeth
(connecting rod) + corresponding
grooves (axle)), and a channel through said fixture, which is constantly
communicating with the
channels in the connecting rod and the axle (Figs.
). When a CT pressure management
system is desired, may the construction of said joint be more complex. This
may be comprising a
serial- and/or a parallel solutions of the fixture and the rotating channels,
of which openings meet
openings of fixed channels during a part of the rotation. The serial solution
comprises a construction
4 Consumption Technology
21
5 Enclosed Space Technology
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