Note: Descriptions are shown in the official language in which they were submitted.
~9lOgl
The present invention concern~ a novel structural
form for a rotary engine or pump having rotating energy chambers
whose size is modified by oscillatory movement of symmetrically
supported radially extending movable walls toward and away from
one another in the course of rotation. The structure is simple
in form and symmetrically oriented about the axis of rotation
of the drive shaftn It employs translational means to translate
the oscillatory movement of the movable walls into a rotational
movement to drive the drive shaft.
While rotary engine technology is newer in many respects --~
than piston and cylinder engine technology, the development of
the Wankel and similar so-called "rotary" engines has produced -~
a great deal of knowledge about problems which would be common
to rotary engines. The present invention is able to employ
much of the technology that has been developed in connection ~
with the Wankel or other rotary engines and can use a similar ~ ~`
block or housing and some of the sealing techniques, but employs
~ a rotary structure which is radically different in its approach
'~ from known "rotary" engines and adds some structural modifications
to the block as well. In particular, the present invention
employs movable walls which are radially directed and axially
oriented to define the bounds of energy chambers in which
adjacent walls bounding an energy chamber oscillate toward and
away from one another circumferentially around the axis of the -
drive shaft to change energy chamber size. In the course of
oscillation, at some stage, energy is imparted to the movable
walls to drive them apart. The driving force provides the
primary means of driving the drive shaft through coupling means
which translates the oscillating movement of the movable walls
into a rotational movement to ~rive.~the d`ri*e shaft.
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1091V91
Couplings may vary in form but preferred arrangements
include a crank connection at a radial extension of the shaft
permitting oscillation of each movable wall, edge wall assembly
relative to the crank support on the shaft extension. That
crank support is a planet gear shaft that carries a pinion which
meshes with a sun or ring gear on the housing and, as the crank
arm rotates about this gear shaft, it turns the shaft extension
and hence the shaft, thus tending to keep rotation smooth and
assuring that the movable walls have repeatable patterns of
movement which are the same for every rotation. In essence,
the motion is a harmonic motion, the nature of which can be
varied somewhat, depending on the coupling employed. The
coupling is simple and uses conventional techniques relatively
easily adapted to the present structure. The parts employed can
be rugged and the structure lends itself to design which enables
i! distribution of load and evenwtar, thereby providing long life.
Moreover, the structure permits direct transfer of much of the
force directly to the shaft extension rather than through gears
with the gears acting primarily to assure proper timing or
synchronism.
The symmetrical nature of the engine structure and
its movement promotes an even smoother rotational movement than
is possible in presently known rotary engines. Furthermore,
the expected efficiency of this engine should be high compared
to known rotary engines. Seals between relatively movable
parts may be made using known rotary engine techniques but the
seals are not subject to as severe forces as those in a Wankel
` engine, for example, and the movable walls may be constructed
with broad faces, opposed to the block cavity wall, to permit
multiple parallel sealing elements, if desired.
Having the pattern of movable wall movement the same
from one revolution to the next, it is possible to precisely
predict where each movable wall will lie at each successive
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lWlOgl
shaft position~ This, in turn, permits location of fluid
inlet and outlet ports on the cavity wall of the housing in
proper position to achieve maximum efficiency. The nature of
the movable walls makes it unnecessary in most cases to employ
valves. Opening and closing of ports is automatically a function
of the movement past such ports of movable walls and their
associated sealing means. I~e port iS effective for a given
energy chamber between the time the leading wall exposes the ~ -
port and the lagging wall closes it. Timing may become a
factor as in any engine or pump and in accordance with the ~
present invention provision is preferably made so that inlet, -
outlet or both ports may be circumferentially moved relative
to the cavity wall to permit optimum timingu
More specifically, a rotary engine in accordance with
the present invention includes a block providing a cylindrical
cavity. A cylindrical drive shaft is supported on the block
coaxially within the cavity to permit rotation of said shaft
Parallel edge walls are located within said cavity axially
spaced apart from one another and extending to the cavity wall.
These edge walls are rotatable relative to said shaft, but designed
to rotate with it, and define between them the bounds of the
energy chambers. An even number of outwardly directed imperforate
movable walls extend to the cylindrical cavity walls and extend
axially between said parallel edge walls with alternate movable
walls moving with one edge wall and intermediate movable walls
moving with the other edge wall. Essentially separate and non-
intercommunicating energy chambers are formed between said
movable walls. The movable walls are rotatable about the axis
of the drive shaft with the unattached end edge of each movable
wall maintaining sliding contact with the edge wall to which
it is not attached.
--4--
109109~
The present invention lends itself to many types of
engine and pump applications. When used as an engine it derives
its force output at the shaft as the result of force applied in
an energy chamber acting to move the movable walls apart. In
a hydraulic engine the force of incompressible fluid under
pressure pressure produces this effect, with the fluid being
drained to sump. In a steam engine the force in expanding steam
drives the walls apart after which the spent steam is squeezed
out. In the case of a smooth burning fluid fuel, ignition is
also required and the resulting explosion forces drive the walls
apart. Two or four stroke cycle engines, carburetor or fuel
injection techniques, Diesel or spark ignition techniques and
many other variables are possibilities. Pump uses may have
fewer practical possibilities but at least one of these is a
metering pump wherein the output is monitored by the shaft posi-
tion and rate is monitored by and directly proportional to shaft
speed.
Por a better understanding o~ the present invention
reference is made to the following drawings in which:
Fig. 1 is a perspective drawing showing a rotary engine
of the present invention with its block broken away to show the
rotary interior structure;
Fig. 2 is a sectional view of the rotary engine taken
along lines 2-2 of Fig. 1 with selected parts of the structure
shown in elevation with portions thereof broken away and in
section;
Fig. 3 is a sectional view taken along lines 3-3 of
Fig. l;
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B
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1091091
Fig. 4, located on the same sheet as Fig. l, is a
i partial sectional view taken along lines 4-4 of Fig. 3;
Fig. 5 is an exploded view of half the rotating parts
of the rotary engine showing the shaft withdrawn from the sun
gear and structure coupling to the wall portion withdrawn from
that wall portion;
~2 Fig. 6 is a diagram showing the driven crank pins'
positions at eight successive equal time intervals representative
of a total shaft rotation;
Figs. 7A, 7B, 7C, 7D, 7E and 7F are diagrammatic show-
ings of the use of the engine as an internal combustion engine
in which the movable walls of the engine are shown in successive
positions during rotation; and
Figs. 8A and 8B, located on the same sheet as Fig. S,
are diagrammatic showings of the use of the machine somewhat
modified as a steam or hydraulic motor or as metering pump.
Fig. 9, located on the same sheet as Fig. 1, is a view
showing the edge of movable wall provided with a plurality of
sealing means; and
Fig. lO, located on the same sheet as Fig. 1, is a
partial sectional view showing a sealing member which is an inte-
; gral part of a resinous movable wall.
l Referring to Figs. 1 through 5, it will be seen that
the engine block, or housing, provides a frame of reference as
in other engine structures relative to which other parts of the
~ engine move. The bloc~, generally designated lO, is divided into
,j~ ,
`~ a pair of similar cylindrical pieces 12 and 14 and generally
- 6 -
~: ~B~
, !
, . ` - ` .
,i,~- ' ' ` " :
" - - ,
~, ` '
'",~ ' '
~09109~
planar end closures 16 and 18. Circumferential flanges 12a and
14a enable bolting of the end closures 16 and 18 to the cylindric-
al pieces 12 and 14, respectively, and cylindrical flanges 12b
and 14b enable the cylindrical pieces to be bolted together
with divider ring 20 between them.
Within block 10 is a cylindrical cavity or bore 22 in
which the rotating parts of the engine are housed. The cavity
22 is preferably a right circular cylinder in form. The end
closures 16 and 18 support bearings 24, 26, respectively, which,
in turn, support drive shaft 28 which passes through the cylin-
drical cavity 22 along its axis. Energy chambers within the
cylindrical cavity at its axial center are bounded and defined
by the walls of the cylindrical cavity, the shaft
- 6a -
B'1
l(J910~1
and two similar but oppositely oriented wall structure sub-
assembliesO In the preferred structure shown, each of these
wall sub-assemblies consists of an edge wall and a pair of
movable walls (see Figo 5)O The edge walls 29 and 30 are
each generally circular in shape and preferably thick flat
discs and are oriented caxially on the drive shaft. While
~ they normally move with the shaft, the edge walls 29 and 30 are
i rotatable relative to the drive shaft 28. In the embodiment
- shown, the edge walls extend outwardly from the shaft to the
bounding wall of the housing defining the cylindrical cavity
; 22. The edge walls 29 and 30 are parallel to one another and
define the bounds axially of the energy chamber. In the con-
figuration shown, attached to each of the edge walls, and
mechanically forming an integral part of and moving with the
edge walls, are a pair of movable walls which, like the edge ji-
walls, are imperforate in their extent from the shaft to the
cavity wall and from the edge wall to which they ar~e attached
to the other edge wall with which they make sliding movement.
Specifically, the two alternate movable walls 32 and 34 are
attached to edge wall 29 (providing a movable wall assembly,
as seen in Figo 5) and the two intermediate movable walls 36
and 38 are attached to edge wall 30 to form a second movable
wall assembly. Expressed another way, movable walls attached
to one edge wall alternate with movable walls attached to the
other edge wall.
It will be clear to those skilled in the art that
the form of the structure shown is illustrative and may be
~ subiect to wide variationO It is possible that in another
; application, the number of movable walls employed might vary
provided that there are always an even number with alternate
and intermediate movable walls, respectively, being attached
at opposite ends to different edge walls. The edge walls
,
1(~91(~91
themselves might take other forms and the shape of the movable
walls might be considerably varied. It is even possible that
instead of edge walls as shown, extensions of the movable walls
closing against adjacent movable walls in a sliding relationship,
or any other suitable way of forming an enclosed and isolated
energy chamber between adjacent movable walls might be substituted.
The edge and movable wall piece assemblies, as shown
in Fig. 5, must be coupled to the shaft to drive the shaft through
suitable coupling means. As shown in Fig. 2, this is preferably
done by connecting edge wall 29 and its connected movable walls 32
and 34 through coupling structure, generally designated 40, to
shaft 28. Coupling structure 40 is located at one end of the
cavity 22 axially outside of the energy chambers. Edge wall 30
and its connected movable walls 36 and 38 are coupled to the
shaft 28 through the other coupling structure 42 at the other
end of the cavity 22 outside the energy chambers. It will be ~ ~-
observed that the coupling structures, like the movable wall ~-
sub-assemblies, are preferably identical to one another and
designed to run in this particular construction 90 out-of-phase
with one another. At each end, rigid extension means effectively
extending the shaft radially outward is requiredO In this
particular e~bodiment, the coupler structure is mounted on a
single linear mechanical arm extending equal distances both
sides of the shaft and sufficiently heavy and of sufficient
strength to take the forces involved. Each of the respective
arms 44 and 46 extends equal distances on each side of the
drive shaft 28. Arms 44 and 46 are pinned or otherwise rigidly
fixed to shaft 28 by suitable means 44a and 46a~ respectively,
(Fig. 2) assuring that the arm moves at all times with the
shaft and forms an extension thereof and maintaining their 90
separation from one another.
_~_
109109~ '
It will be clear that in other embodiments, shaft
extension means could be of an entirely different form, including
a wheel of perforate or imperforate form. Furthermore, a single
arm extending radially out one side of the shaft will work.
However, the symmetrical structure shown preserves better
balance, tends to divide the load and, therefore, tends to
be less subject to rapid wear than a single radial arm. Mounted
in suitable bearings 48a in arm 44 are identical gear shafts
50a and 50b each having its axis parallel to the axis of the
drive shaft 28 and equally spaced radially therefrom. Gear
shafts 52a and 52b, respectively, in arm 46 are not shown but
their positions may be inferred. Gear shafts 50a and 50b carry
! planetary gears 54a and 54bo Similar gear shafts 52a and 52b,in
similar bearings i;n the arm 46 carry planetary gears 56a and
56b. Each of the gear assemblies is identical to the others,
is pinned or otherwise fixed to its gear s~aft on the side of
the arms 44 and 46, respectively, axially removed from the
energy chambers in position such that the planetary gears 54a
~)
and 54b engage sun gear 58. Sun gear 58 is fixed to the end
closure 16 of block 10 so that planetary gears 54a and 54b
must revolve around it. Similarly, sun gear 60 is fixed to
end closure 1~ causing planet gears 56a and 56b to revolve
around it. In this particular embodiment the sun gears have
twice as many teeth as each of the planetary gears. It will
be clear to those skilled in the art that in some embodiments
of the invention a stationary ring gear could be used in place
of the sun gear.
; Fixed by suitable means to the gear support shafts
50a and 50b, axially on the opposite side of the arm 44 from
;- 30 the gears, are eccentrics 62a and 62b. Similar crank arm
members provided by eccentrics 64a and 64b, are fixed to the
gear shafts 52a and 52b supported by arm 46. Completing the crank
structure or drive crank pins 66a and 66b supported in theeccentric
_g_
. .. . : . . -.
10~10~1
crank arms 62a and 62b, respectively, and, in turn, rotatably
supporting drive bushings or bearings 68a and 68b7 Similarly
drive crank pins 70a and 70b on eccentric crank arms 64a and 64b
rotatably support bushings or bearings 72a and 72b. These crank
pins and bushings extend parallel to the gear shaft 50a. The
rotatable bushing 68a and 68b, 72a and 72b, on their respective
drive crank pins, extend into the movable wall structure in this
particular embodiment, preferably into closely confining radially
extending slots 74a and 74b, 76a and 76b, respectively, which
slots are sufficiently long to accommodate the total radial
component of movement of these bushings and supporting crank pins.
(See discussion below of Fig. 6.) As seen in Fig. 2, the design
is such that each of the bushings on a particular arm lies in the
corresponding end of each slot at the same time. In Fig. 2 the
pin bushings 68a and 68b are shown simultaneously in the outer
ends of their respective slots 74a and 74bo In Fig. 3 pin bushings
72a and 72b are shown simultaneously in the inner ends of their
respective slots 76a and 76b. Due to the sy~metry of the structure
the respective pin bushings will arrive at the opposite ends of
their respective slots simultaneously, as well, when shaft 28
has rotated 90O The crank mechanism, therefore, provides a
translation element for effectively translating the lateral or
arcuate oscillation movement of the movable walls into a rotational
movement of the shafts of gears 54a, 54b, 56a and 56b. Because
sun gears 58 and 60 are both fixed, movement of the walls causes
a progression of the planet gears 54a,54b and 56a, 56b around
their sun gears, which, in turn, drives the arm extensions 44 and
46 rotationally in alternation but in the same direction and,
j therefore, drives rotationally the shaft 28 to which the arms are
pinned. In the example illustrated, it is necessary for the sun
gear to have two times as many teeth as a planet gear in order
for the resultant movement of two complete cycles of the cranks
to cause the main shaft to turn one full revolutionO
-10-
1~910gl
In addition to modifications using other gear arrangements
and shaft extension means, it is possible to construct engines in
accordance with the present invention using chains and sprockets
or timing gears and belts in place of gears. In fact, any positive
means of transfer of motion might conceivably be used in certain
applications.
In any type of engine or pump arrangement contemplated
by the present invention, fluid must be introduced into the energy
chamber region through some sort of inlet port and must be exhausted
through some sort of an outlet port~ These ports may be openings
through the walls of a housing of simple or complex shape. They
may be connected to whatever type of apparatus is needed for
generating the selected fluid condition for a given mode of opera-
tion and for moving the fluid toward or away from a port in the
engine cavity~ In all cases the inlet port and the outlet ports
are circumferentially displaced from one another with the inlet
port occurring in the direction of rotation prior to the outlet
port. In some cases more than one inlet and more than one outlet
port may be provided. In other cases inlet ports and outlet ports
may be repeated at different circumferential locations around
the cavity.
Whatever the port configuration arrangement, it is often
desirable that a port be repositionable circumferentially in order
to control the effect of timing upon the engineO In the embodi-
ment shown in the drawings, the cylindrical wall members 12 and 14
are not of uniform diameter, but are provided with two diameter
sections, the larger of which is provided beneath the fl~nges 12b
and 14b and adjacent to the divider ring 20. The divider ring
itself preferably has the same inner diameter as the smaller
diameter portionsO The larger diameter portion is provided to
accommodate snugly ring channels 78 and 80, respectively. Ring
channels 78 and 80 are identical and provide outwardly facing
channels of "U" cross-section, as seen, for example, in Fig. 2,
T~e inside surface of the bottom of the channels is cylindrical
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lO91~g~
snd of the same diameter as the smaller diameter portion of the
cylinder walls 12 and 14, and the ring channels are preferably
adapted to fit snugly against the shoulder at the end of the
smaller diameter portion which serves as as stop. The channels
are also of such an axial width dimension that they extend to
the divider ring 20 so that in assembly, as shown in Fig. 2, the
entire structure presents a smooth continuous diameter cavity 22,
at least across the width of the energy chambers. An inlet port
78a into the energy chambers is provided through the bottom of
channel 78, for example, as seen in Fig. 3. An outlet port 80a
is seen as offset circumferentially from inlet port 78aO Each of
these ports communicates, respectively, through its channels to
an opening through cylindrical housing sections 12 or 14, respect-
ively~ For example, through cylindrical housing wall 12 extends
a threaded opening 82 which receives a threaded nut 84 holding
tubing 86 communicating with the fluid supply (not shown). Sin~læ
a threaded outlet port from the channel 80 through cylindrical
housing wall 14 receives a threaded nut 90 holding tubing 92 in
place, the tubing leading, in turn, to suitable exhaust means
(not shown). Some of the complexity in certain parts probably can
be greatly si~plified by careful design.
The purpose of providing circumferential channels pro-
viding ports into and out of the energy chambers is to permit
repositioning of the ports 78a and 80a. ~his can be accocplished ~n
various ways, but, in accordance with the disclosed embodiment each
of the channels is provided with a ring of gear teeth 78b, 80b,
on the outer sidewall of its channel and projecting axially outward
generally parallel to the axis to provide a toothed rack. Cooper-
ating with the rack 78 is a pinion 94 supported on and rotated by
a radially directed shaft 96 with respect to the cylindrical
housing wall 12 so that the pinion's teeth engage the rack. A
similarly arranged pinion 98 rotated by shaft 99 engages and drives
rack teeth 80b. In each case rotation of the pinion 94, 98 will
drive the rack 78b, 80b and cause rotation of the channel 78, 80
-12-
.~ .: . ,
1091091
with respect to the housing, relative to which it is snugly retained.
This rotational movement enables repositioning of the ports 78a,
80a to whatever circumferential position may be advantageous in
a particular application.
Because the ports may be traversed by sealing means on
the outer edges of the movable wall members, it is sometimes prefer-
able to provide them with a smooth, elongated, out-of-round shape,
such as shown in Figo 4, in order to minimize the effect of wear.
It will be clear that the selected port size and shape will depend
upon a given design, and where desirable, nozzle or other orifice
modifications, or additions to the orifice, may be employed, as
desired. Valves, although preferably and advantageously eliminated,
may be employed in various s'napes and forms as required in oonnection
with ports in a particular application. It will also be apparent
that the ring channels, while of particular advantage, need not
be provided in the form shown which permit repositioning through
360. Very often only a small arcuate section of the circumference
need be coveredO A segment of a ring in channel form and having
closed ends provided with suitable sealing means might be employed
instead of the complete ringO Non-arcuate movable pieces might
also be employed in a given application and considerable variation
could be provided in the means of Moving various ports. To have
the ports arranged so that they may be moved manually or auto-
matically from the outside, of course, is a major advantage avoiding
the need to disassemble the machine to change its timing. The
geared nature of the device shown will also hold the channels in a
; position, once selectedO However, if a position changing device
does not provide it, separate stop means will have to be employed
to hold the port in selected position. Other means of adjusting
.., 30 port positions without disassembly are contemplated as is the simple
ability to change port position by disassembly loosening the port
carrying piece and reassembling, for example, thereby locking the
piece in its newly selected positionO
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10910~
The diagram of Fig. 6 is provided as an aid to
understanding the force and motion transfer mechanism. Solid
radial or diametrical lines through the axis at eight equal
angular intervals represent selected positions of the respective
arms 42 and 44, and the circles therealong at equal radii from
axis 28 represent successive positions of each of the gear
shafts 50a, 50b, 52a and 52b. Since it will be understood that
the view represents in effect an axial view similar to Fig. 2,
or more properly, a projection onto a com~on plane along the
axis showing pin and shaft extending arm positions superimposed
in that common plane. Since the pinion gear shafts are all at
the same radius, their coincidence in the projection can be
readily understood. It will be understood, however, that, since
the arms 44 and 42 are in reality 90 out-of-phase with one
another, the positions of their crank pins 66a and 66b for
arm 44 and 70a and 70b for arm 42 will differ. Since pins 66a
and 66b travel the same path represented by the solid line, a
common designation 66 will be understood to designate the
solid line path, including the eight designated successive pin
positions. 6imilarly, a common designation 70 is used for the
dashed line path of crank pins 70a or 70b. Considering crank
pin path 66, for example, it will be observed that in a full
revolution of shaft 28, crank pin 66 moves from a maxim radius
in line with its arm to a minimum radius in line with its arm
back to a maximum radius and back to a minimum radius. The
change in radius is, of course, two times the length of the
crank arm. It will also be observed that in the intermediate
positions shown the crank pin achieves the same radius as
the gear shaft, but it is offset to one side at the full length
of the crank arm, thus producing a pattern of movement somewhat
like the figure traced in solid lines. The same observations
apply to crank pin path 70.
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~9~Ogl
If one bears in mind that the movable walls are
effectively attached to the crank pins 66 and 70 insofar as
circumferential position is concerned, it becomes possible to
visualize movable wall positions relative to arms 42 and 44.
Thus it is possible to visualize the walls oscillating in
position from positions a crank's length ahead of the shaft-
extending arms 44 and 46 to positions a crank's length behind
the arms and back again. Two full oscillations occur each
revolution of shaft 28. With the arms positioned 90 out-of-
phase, the walls connected to one arm move in the oppositedirection from the walls connected to the other armO This
causes the walls to appear to alternately move toward and
away from one another, first increasing and then decreasing
the size of the chamber between the adjacent walls.
In certain parts of the path, wall movement is fast
relative to the speed of the arm movernent, and in other parts
the wall movement speed is slow relative to the speed of the
arm movement. The net effect is that sometimes the movable
walls appear to nearly stop movement and at other times they
accelerate where the distance which must be traveled is
greater than the distance traveled by the gear shaft. ~wice
each revolution the crank pin and its walls reach a minimum
speed and almost stand still as the crank pin reverses direction.
It will be observed that, when the wall is in one of these
minimu~ speed positions, crank pin movement is primarily radial
movement and there can be rela~ively little transfer of force.
On the other hand, there can be direct transfer of force in
; the opposite situation where the main component of motion of
the pin coincides with the wall even though the motion of
the arm may be effectively slowerO ~le pattern of movement
is a function of the gearing, crank dimensions, slot shape and
relative placement of the shaft extending arms, and is predeter-
mined for a given system. Functional use of the predetermined
-15-
~091091
movement and relative positioning of the movable walls, as
well as the variable design of such movement, is a basic
consideration in designing a given engine or pump for a
particular type of application. For example, variation from the
straight radial slot can give variations in movement pattern
which may prove highly advantageous in a given application.
The structure, as described thus far, could be used
for a variety of types of engines and pumps. The different
applications would, of course, call for use of various types
of fluid, as well as different operations of the fluid upon
the structure, leading to varying positions for the inlet and
outlet ports and possibly variations in port design. In
addition, the auxiliary equipment used with the engine would,
of course~ differ radically from one situation to another.
The structure was first conceived as an internal
combustion engineO With such use the fluid is ordinarily a
combustible vapor consisting of a mixture of air and fuel
part~cles such as vaporized gasoline. This fluid may be supplied
to the inlet port of the engine in a manner similar to and using
equipment conventionally employed in an internal combustion
engine for an automobile. That is, fuel may be fed in the
same way to a carburetor wherein it is mixed with predetermined
amounts of air and provided access or ducting to the inlet port.
The location of the inlet port is of some critical
importance in an internal combustion engine and, hence, the
repositionability of the port may be of great importance in
j such an application. Generally speaking, however, the
introduction of the air/gas mixture needs to be at a time
when the movable walls of the energy chambers are separating
so that the chamber is being enlarged which action creates a
partial vacuum which will tend to draw the fuel into the energy
chamber.
1091091
The Figures 7A through 7F illustrate various stages
in a four-stroke cycle version of an Otto cycle type internal
combustion engine employing ignition means such as a spark
plug 100 to produce an explosion of the fuel (i.e., air and
gasoline mixture) within the confined walls to drive the walls
apart and provide the force necessary to move the shaft through
the coupling, as previously explained.
Referring to Fig. 7A in the diagram shown, the view
is similar to that shown in Fig. 3. ~hile in these diagrammatic
showings the movable walls are labeled A, B, C and D, walls
corresponding to those shown in Fig. 3, for example, might be
as follows: movable wall 36 corresponds to wall A; movable
wall 32 to wall B; movable wall 38 to wall C; and movable wall
34 to wall D. These diagrams are used herein to describe the
effects occurring between the movable walls A and B in the
course of a revolution, it being understood that the space
between each of the movable walls experiences exactly the
same kind of sequence, but in different phasing. The action
of the engine and the transfer mechanism makes possible four
simultaneously occurring processes in the different energy
chambers, each of which lags the chamber ahead of it by 90.
Referring first to Fig. 7A, it will be seen that
as movable wall A passes the intake port 68a, that port is
opened to the energy chamber between walls A and B. The timing
of the wall movement is arranged such that as wall A passes
intake port 68a it will tend to move much more rapidly than
~ wall B, so that the net effect is for the chamber size to
; expand. Such expansion, in turn, tends to create a partial
vacuum drawing fuel into the constantly enlarging space, as
illustrated in Fig. 7B. Ultimately the walls must begin to
move together again and the wall B moves over the intake
port 68a to seal it off, as shown in Fig. 7C, before compression
begins by rapid movement of wall B toward wall A to compress
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1091091
the fuel in the compression phase of the four cycle program.
As compression is completed, or about to be completed, as seen
in Fig. 7D, the chamber passes the spark plug 100 which is
ignited. Exact timing as in the other engines of this type
may be either just immediately before or at, or slightly after,
the minimum size of the energy chamber between walls A and B
has occurred.
The effect of the firing of spark plug 100 is to
cause explosion of the fuel which will drive wall A away from
wall B because of the nature of the gear action and crank pin
positions at this point which permits free movement of wall A,
but not of wall 8r The crank pin and crank arm positions
relative to driven movable wall A in this position is also such
~` that the force of the explosion will drive the arm 46, effectively
transmsitting the force directly through the pin and crank
connections, rather than through the gears. Before the position
of Fig. 7E is reached most of the force from wall A has been
transmitted to the arm 42 and, as shown, wall B is in position -: -
to, in turn, transmit force through arm 44 to the shaft. As
seen in Fig. 7F, a~ter the wall A passes and exposes the
exhaust port, wall B begins to close into wall A narrowing the
energy chamber and forcing the exhaust from the explosion
through the exhaust port 70A. The exhaust port may, of course,
be connected to an exhaust system similar to that employed
in automobiles or other internal combustion engine systems.
Following the cycle shown the same cycle is repeated.
- Of course, as previously indicated there are four energy
chambers, all corresponding to cylinders in a conventional
internal combustion engine, each going through the same cycle
but at 90 intervals. The motion described for the chamber
between walls A and B repeats for B and C, C and D, and D and E
in succession, providing the same positioning of each of those
energy chambers relative to the intake port, the ignition
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means and the exhaust port. Thus, at four different time~
during each revolution of shaft 28 force is transferred to the
shaft from each of the four walls in succession as it is driven
by explosion. ~t all other times it is the walls which are
moved by some of that force fed back into the system by way
of the gear system.
The spark plug 100 may be supported within the cavity
on divider ring ~, or some other portion of the housing 10
~ relative to which the inlet and outlet ports are movable.
Wherever supported, it should be recessed from the cylindrical
surface of the cavity in order to avoid interference with the
movable walls or other portion of the rotor or its sealing
means. Electrical ignition means of a suitable known type may
be used to fire the spark plug.
It will also be appreciated that the design details
depend on application~ The engine can be designed for compression
ignition as well as spark ignition. An appropriate Diesel cycle
could be used. Design of a two cycle system requires design
of suitable scavaging ~echniques. ` `
Figs. 8A and 8B show an engine using the same
mechanism which employs input and output ports, but uses no
ignition means. Because there is no requirement of compression
and ignition of the fuel, this system involves only two cycles. A -
feeding in of the fluid which, when permitted, tends to drive
the walls apart and an exhaust of the fluid, once the walls
have been driven apart, as the walls are closed back toward
one another comprise the only two cycles required. As seen
in Figs. 8A and 8B, such a two-cycle system permits the
doubling-up of cycles, or two full two cycles, with the
~ 30 rotor construction shown.
.~
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lU91091
More specifically, with the engine used as a stesm
engine, the inlet port may be provided at approximately the
same position. When the movable wall A passes the port 102,
steam is permitted entry into the energy chamber between walls
A and B. The energy inherent in the steam causes the steam
to expand and, in doing so, drives walls A and B apart. When
wall B cl~s~æ off the inlet port, however, no further steam
can enter. ~all A shortly, thereafter, exposes outlet port 104,
which may be connected to a system for venting the steam to
atmosphere. As the wall B closes down toward wall A it drives
the steam out of the compartment. Shortly, thereafter, wall
A passes inlet port 106 exposing it to the energy chamber
between walls A and B. Again, the input of the steam into that
compartment and the addition of steam as well as the expansion
of the live steam will cause wall A to be driven away from
wall B. During the latter part of the period of greatest
expansion the inlet opening is closed. Meantime, outlet ~ -
opening 108 is opened by the passing of wall A to permit the
steam to be squeezed out as wall B closes toward the wall A. -~
Again, the cycle is repeated.
Although steam is a compressible fluid, it will be
readily apparent to one skilled in the art that the engine
without ignition means need not be~confined to a steam engine,
~ but even incompressible fluids, such as water or oil, can be
`!l used. In such cases pressure produced by pump or other means
is used to supply the fluid under pressure, which due to its
incompressible nature will cause the walls between which it
is fed to be driven apart. Again, when the outlet is exposed,
if the vent is to atmosphere the squeezing down of the
compartment by the movement of the chamber walls together will
cause the fluid to be forced OUto Again, a second full cycle
can be repeated during the other half of revolution.
'~
, ~ .
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Of course, instead of using the machine of the
present invention as an engine, it is possible to use it as
a metering pump. For example, as incompressible fluid is fed
through such a metering pump, it experiences a cycle similar
to that described in its use as an engine, except that instead
of using the shaft to drive a load, the shaft in such a case
is used merely as a means of measurement. The speed of the
shaft rotation in such an instance is directly proportional
to the pressure and is a measure of the volume of material.
The matter of sealing the individual firing cha~bers
from one another and maintaining good sealing contact between
the cavity and moving walls is a matter of known technology
in Wankel engines, and other rotary engines. This technology
may be adapted, as needed, for application to the present
invention. The greatest rotational speeds are encountered in
the interface between the engine block and the rotor parts
which simultaneously move relative to one another, so that the
most severe problems to be encountered can be solved by the
Wankel technology. Fig. 9, for example, shows a movable
wall 110 carrying in its broad arcuate outer surface a
plurality of sealing elements 112a, 112b, 112c and 112d which
may be of a type known through Wankel technology. Thus the
movable wall being broad at its outer edge in contrast to the
narrow edge in the Wankel can provide more sealing elements,
as shown, or use other techniques to achieve a better seal.
Less severe problems of relative movement, of course, are
; encountered between the moving wall assemblies and the shaft
and between one set of moving walls and the other edge wall
but lubrication and sealing problems are within the skill
of known engine technology. In fact, in applications where
incompressible fluid is employed and heats encountered are
not severe,as compared with internal combustion engines,
materials selected for parts may be made of molded resins or
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other materials not commonly encountered in engine technology.
In such event, the present invention contemplates the use
of integral sealing means in some cases. Fig. 10 illustrates
one such possibility wherein each movable wall 114 is cast
of resinous material with at least one integral sealing
element 116 for~ed in such a way that it remains relatively
resilient and flexible despite hardening of the rest of the
movable wall 1140 The sealing element in assembled position
will be resiliently displaced from an unstressed radially
outwardly position to the position shown in Fig. 10 upon
assembly against the housing wall 10. Modern plastic technology -
permits hardening of certain parts of a cast or extruded body -
and rendering flexible other parts. Sealing parts may be
formed of flexible portions and in some applications may be
thin flexible webs actually intended to be bent to accomplish -~
sealing as illustrated in Fig~ 10, although separate sealing
elements may alternatively be used.
Various modifications to the preferred embodiment
shown and described have been discussed. Other modifications
and variations will occur to those skilled in the art. All
such modifications and variations within the scope of the
claims are intended to be within the scope and spirit of the
present invention.
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