Note: Descriptions are shown in the official language in which they were submitted.
9~6
UNIDI~ECTIONAL ENERGY CONVERTER ENGINE
13ACKGROUND OF THE INVENTION
As is known, systems have been proposed in the
past to convert one type of energy into another type by using
various thermodynamic cycles, such as the Otto, Rankine and
Brayton cycles. Most of these systems employ reciprocating
pistons; although some, such as those shown in Dutch Patent
65,164 and German Patent 842,845, employ one or more pistons
which are forced to travel in one direction in a continuous
closed-loop by the expansion of a gaseous medium in one region
of the closed loop. In the closed-loop systems of the prior
art, each piston is coupled to a mechanical element which moves
with it, the kinetic energy of the moving piston being converted
directly into mechanical energy. These systems, however, require
complicated mechanisms for coupling the piston or pistons to
an associated mechanical element.
In U.S. Patent No. 3~859~789/ a method and apparatus
are disclosed for converting one form of energy into another
form of energy through the use of a single continuous, closed~
loop passageway contalning a plurality of freely-movable,
mechanically-unrestrained bodies which travel around the
passageway in one direction only. Acceleration of the bodies
````` 1~9~2~i
is effected by means of an expanding fluid medium supplied exte~lally to the
closed-loop passageway or by means of internal combustion. The kinetic energy
of the bodies is extracted by a variety of methods including causing the pro-
pelled bodies, when formed from magnetically permeable material, to pass
through an electromagnetic field to convert some of the kinetic energy into
electrical energy. ~inetic energy is also extracted by compressing the fluid
between the bodies to provide energy in the form of compressed fluid. When the
expallsion of a gas is used to propel the bodies in *his type of energy con-
verter, the bodies pass through a region where the gas between them is com-
pressed preparatory to a succeeding cycle o operation. In all such prior
art systems of this type, the closed-loop passageway itself remains stationary.
SUM~RY OF T~ INVENTION
According to the present invention there is provided apparatus
for converting a first form of energy into a second form of energy con~rising
a platform, support means for carrying said platform for rotation about a
central axis, at least one continuous, closed-loop passageway carried by the
platform in a plane extending perpendicular to said central axis, a plurality
of freely-movable pistons contained within the passageway, at least one
region in the passageway in which the pistons move inwardly against centri-
2~ fugal force as said platform rotates~ at least one other region in the passage-
way where said pistons are moved outwardly ~mder the influence of centrifugal
force, means for imparting a force to successive ones of the pistons to move
them against centrifugal force in said one region, and means for converting
the energy of pistons moving outwardly undeT the influence of centrifugal
force in said other region into another form of energy.
The energy of the pistons moving outwardly against centrifugal
force may be converted into rotational energy, and means may be provided
forcoupling the rotational energy to the platform to rotate it.
Such an apparatus may comprise a platform, support means for
caTrying said platform for rotation about a central axis, at least one
~ 2-
~9~
continuous, closed-loop passageway carried by the platform in a plane extend-
ing peTpendicular to said central axis, a plurality of freely-movable pistons
contained within the passageway, means for applying a force to successive ones
of the pistons in a first region of the passageway extending along the periph-
ery of the rotating platform to thereby propel each piston in one direc~ion
around the passageway and increase its kinetic energy, a second ~egion of the
passageway being shaped to cause the pistons, a~ter being propelled, to work
against centrifugal force to thereby convert ~he kinetic energy of the pistons
into potential energy as they approach the center of rotation of the platform,
a third radially-extending region of the passageway where said pistons are
moved radially outwardly back to said first region under the influence of
centrifugal forceJ means for converting the energy of pistons moving radially
outwardly in said third region into rotational energy, and means coupling said
rotational energy to said platform to rotate the same.
Preferably, there are two closed-loop passageways located at
diametTically-opposite locations on the rotating platform. Each passageway
includes two arcuate segments, each having a di.fferent radius, and a linear
segment interconnecting the two arcuate segments. When the apparatus of this
type is adapted for operation according to the Rankine cycle, a rotary union
communicates with a duct extending coaxially along a support shaft for the
platform; while conduits extend from the duct to the first region of each
passageway to supply Steam or the like as the expansible fluid from a
stationary boiler. A second duct can be connected by conduits to each second
Tegion of the passageways for exhausting steam therefrom. The rotatable means
for each passageway may include at least one and preferably two pocketed
wheels disposed at opposite sides of the passageway for receiving the pistons
as they are moved radially outwardly along the linear regions of the passage
ways under the influence of centri~ugal force. These pocketed wheels also
serve to feed the pistons into the first region where ~hey are propelled by
3~ expansion of a fluid. The pocketed wheels are secured to arbors which are,
5~i
in turn, rotatably supported by the platform and coupled ky gears in a
stationary gear which is coaxial with the central axis o~ the platform. The
rotational movement of the pocketed wheels is thereby converted into rota- r
tional movement of the platform. Typically, the pocketed wheels at opposite
sides of thR linear region of the passageway include circumferentially-
spaced peripheral pockets to pass the pistons between the wheels. Alter-
natively, the wheels may have spaced-apart magnets on their peripheries~ all
of the magnets carried by one wheel having magnetic south poles and those
carried by the other wheel having magnetic north poles at their respective
peripheries.
~hen this type of apparatus is adapted for operation according to
the Brayton cycle, liquid fuel is fed from a stationary tank through a
coaxial pipeline to the rotating platform. An inlet manifold and an exhaust
manifold communicate with only part of opposite sides of the aforesaid
second arcuate region of each passageway. The remaining part of the second
region is used to compress air between the bodies. The co~pressed air is then
fed to a combustion chamber where it is heated and used to propel the pistons
i31 the first region of each passageway.
Another apparatus for providing rotational energy comprises a
2~ platform, support means for carrying said platform for rotation about a
central axis, a continuous, closed-loop passageway carried by the platform
in a plane extending perpendicular to said central axis, a plurality of
freely-movable pistons contained within the passageway, said passageway
having essentially straight portions on opposite sides of said central axis,
said straight portions being interconnected at their opposite ends by curved
portions also on opposite sides of said central axis, means for applying a
force to successive ones of the pistons in one region of each of said straight
portions to propel them inwardly on the rotating platform against centrifugal
force, said pistons being moved radially outwardly in another region of each
o~ said straight portions under centrifugal force, means for converting the
52;
energy of pistons in said curved portions which have been moved outwardly
under centrifugal force into rotational energy, and means or coupling said
rotational energy to said platform to rotate the same.
The means for converting the energy of the pistons into rotational
energy may comprise pocketed wheels having their peripheries coinciding with
the inner peripheries of the curved portions of the passageway to convert the
energy of the pistons in the curved portions, which have been moved outwardly
under centrifugal force, into rotational energy. As previously described,
these pocketed wheels may be coupled through a gear ~rain mounted on the
platform wllich meshes with a stationary gear carried beneath the platform to
cause rotation of the platform about its rotational axis.
By drivillg the rotating platform in reverse, appropriate embodiments
of the apparatus can be used as compressors rather than engines. In this
case, rotational energy is converted into co~pressed gas.
Such an apparatus may comprise a platform, support means for
carrying said platform for rotation about a central axis, at least one
continuous, closed-loop passageway carried by the platform in a plane extend-
ing perpendicular to said central axis, a plurality of freely-movable pistons
contained within the passageway, at least one region in the passageway in
~0 which the pistons move radially inwardly against centrifugal force as said
platform rotates, at least one other region in the passageway where said
pistons are moved radially outwardly under the influence of centrifugal force,
port means in said otheT region for drawing a gas to be compressed into said
passageway, means for imparting a force to successive ones of the pistons to
~ove them against centrifugal force in said one region of the passageway,
said gas drawn into said other region being compressed by the kinetic energy
of pistons moved outwardly under the influence of centrifugal forceJ me~ns
for withdrawing said compressed gas from said passageway, and means for
rotating said platform.
~o The means for imparting a force to successive ones of the pistons
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~399S;~6
to propel them against centrifugal force in the one region may involve the
aforesaid pocketed wheels.
In the use of such an apparatus as a compressor, the pistons are
forced radially inwardly in the closed-loop passageway and are then forced
radially outwardly, while air is drawn into the passageway through the ducts
which function as exhaust ports during operation as an engine. The radially-
propelled pistons then move back to the pocketed wheels while they compress
air which is expelled through the duct which acts as an intake port during
operation as an engine.
It is to be understood that a nu~ber of rotating platforms of the
type described above can be coaxially mounted on, and secured to, a single
shaft such that a number of energy converters effectively operate in parallel.
- ~ -Sa-
s~
The above and other ob~ec~s and fea~ures of the
invention will become apparent from the ~ollowing detailed
description taken in connectlon with the accompanying drawings
which form a part of this specification, and in which:
Figure 1 is a plan view of ~he rotating engine
according to one embodiment of ~he present invention for convert-
ing, according to the Rankine cycle, one ~orm of energy into a
second form of energy;
. Fig. 2 ~s an enlarged plan view of ~he pocketed wheels
of the invention for feeding pistons forming part of the apparatus
shown in Fig~ l;
Fig. 3 is a cross-sectional view taken along line
III-III of Fig. 2;
Fig. 4 is a sectional view taken along line IV-IV
of Fig~ l;
Fig. S is a sectional view taken along line V-V
o Fig. 4;
Fig. 6 is a plan view similar to Fig. 1 but
illustrating the apparatus o~ the present invention for
operation according to the Bray~on cycle;
Fig. 7 is an illustration, in partially broken-away
plan view, of another embodiment of the invention wherein a
single loop passageway extends around the axis of rotation of
a platform, there being two regions in the passageway where
plstons are propelled against centrifugal ~orce;
F~. 8 is a side view of the embodiment of ~he
~nvention shown in Fig. 7; and
~395J~;
Figs, 9A ~nd 9B ~llus~xate ~lterna~ive forms of the
pistons wh:lch can be u~ed in the two embodimen~s of the invention.
W~th reference now to Figs. 1-5, the rotatlng engine
shown includes a platform 11 in the form o~ two disc-shaped
S plates llA and llB (Fl~s. 3 and 4) wi~h mutually-engaging
face surfaces maintained in contact by fas~ening members, not
shown. The platform is adapted t~ rotate about a central
vertical axis 12 (Fig. 4) and is secured by fasteners to R
centrally-arranged shaft 13 extending downwardly rom the bottom
of plate llB of the platorm. Bearings 14 support the shaft 13
for rotation wi~hin a support rame 15. A stationary main gear
16 is keyed to a j~urnal surace provided on frame 15 . As is
perhaps best shown in Flgs. 1 and S 7 the diameter of gear 1~ is
selec~ed so that it meshes with two separate gear trains, each
being iden~ical and including a first idler gear 17 and a ~econd
idler gear 18. The gears 17, for e~ample, are supported by
bearings on arbor shaf~s 19 (Figs. 4 and S) carried by pla~e llB.
As shown in Figs. 2, 3 and 5, each idler gear 18
is secured to the lower end of an arbor shaft 20 which extends
through an opening in the platform 11. Above gear 18, the
arbor sha~ 20 carries a timing ~ear 21 located within a recess
in plate llB. In this re~ess, the timing gear 21 meshes with a
second timing gear 22 secured to an arbor shaft 23, Bo~h arbor
shafts 20 and 23 ro~ate in suitable bearings supported by the
25 platform as shownO The uppe~ ends of arbor shafts 20 and 23
carry pocketed wheels 24 and 25, respec~ively. As shown in
Figs. 1 and 2, the pocke~ed wheels have cireular recesses uni-
ormly ~paced about their outer periphery which are adapted to
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~9~526
receive ln succession pi~ton6 27 which are ~ypically
spheroids.
The respective palrs o~ pocketed wheel assemblies
24, 25 are arranged a~ generally, diametrically-oppos1te
locations on the platform 11. Each pair o~ pocketed wheels
forms par~ o~ an independent, unidirectional energy converter
loop that includes a continuous, closed loop passageway 30.
The two loop passageways ~ake the form of machined slots in each
o~ the mutually-engaging face surfaces of the plates llA and llB
of the plat~orm 11. In other words, the passageway 30 is defined
by aligned slo~s having walls which are preferably smooth and
formed from me~al. The passageways are located at mutually-
exclusive sectors which lie at opposite sides of a vertical plane
passing through the axis 12. The pis~ons 27 are freely-movable
bndies which pass in succession through each passageway. The
tolerances or clearances be~ween the suraces of the pistons 27
and the walls of the passageway 30 are such as to permit the
p~stons to move freely therealong. Fluid flow past the pistons
wi~hin the passageways is substantially prevented since the
20 plstons have a spheri.cal shape which is substantially c~mpl~-
mentary to the cross-sectional shape of the passageways. If
desired, a tube can be used as a liner in each passageway.
As shown in Fig. 1, each passageway 30 is made up of
three regions 32, 33 and 34, Region 32 extends along the
periphery of the platform 11 ~or a distance of approximately
90. This region forms an expanding section wherein a fluid
medium, such as steam, is used to ~reely accelera~e the pistons
in succession. Region 33 is curved inwardly toward the center of
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Z~
rotation o the pla~form 11 and 18 provided with one o~ more
ports 31 in the upper plate llA to bleed off fluld between
~uccessive pi~tons. It ~hould be under8~00d, however~ ~hat ~he
ports 31 could b~ replaced by a plenum chamber whl~h collects
5 the steam, condenses and returns it to a boiler.
As the pistons 27 move radially lnwardly in the region
33, they must work against centrifugal orce; and in this process
the kinetic.energy of thP moving pistons in rcgion 32 is converted
into potential energy as they approach the oenter of rotation
10 of the platform. Finally, when ~he pis~ons are ~n region 34 ln
closely-abutting relationship, they are urged radially outwardly
under the influence of oentrifugal orce. In thls process, they
pass through the pocketed wheels 24 and 25, thereby inducing
rotation which is tr~nsmi~ted through idler gears 18 and 17
lS to central gear 16, thereby causing the entire platform 11 and
the elements carried thereby to rotate in the direction indica~ed
by ~he arrow A in Fig. l. As the pocke~ed wheels 24 and 25
rotate, they ~eed successive ones of the pistons 27 to the 1rst
or expànder region 32 where they again are propelled in ~he same-
direction as the direction of rotation of the platform 11.
In Figs. l-5, s~eam is used ~or the opera~ion of the
rotary platform according to a Rankine cycle. The steam is fed
from a stationary boiler, not shown, to the rotating platform 11
by means of a duct 40 ~Fi~. 4) extending through the support
~haf~ 13. The steam is delivered by a sta~ionary conduit 41
through a rotary union 4~ and into ~he duct 40. Duc~ 40
communicates wlth a chamber 43 located in the plate llB below
~he con~inuous, closed-loop passageways 30. Radially-extending
~9 _
s~
~lots 44, machlned into the mutually-engaglng face surfaces of
plates lLA and 11~, del~ver the 8team from chamber 43 to supply
chambers 45 (see al~o Figs. 1 and 2). Disposed within the
chambers 45 are bushings 46 with portal open~ngs to deliver
5 steam from the slots 44 into ~he expander region 32. ~8 shown,
~he expansible steam is iniected i,ltO the expander region at
the point of iuncture between the expander region 32 and the
radially-extendi.ng region 34. The force exerted b~ the expanding
ste~.m propels` the pistons along the expander region to the polnt
10 where they enter the combined coasting and steam exhaust section
formed by region 33. In region 33, the steam i~ exhausted through
ports 31 to ~he atmosphere as described above or ~ if desired,
a system o~ ducts may be used to oonduct the steam and~or con-
densate from region 33 ~hrough a pipe within duct 40 in sha~t
13 for return to the boiler.
In the operation o the invention, the steam injected
into the expander region 32 will propel each of the pistons 27
along the periphery of the platorm 11, thereby converting the
thermal energy of the steam lnto kin~tic energy of the pl~tons 27.
As eaeh of the plstons 27 ls propelled forwardly, an equal and
opposite reaction is induced tending to rotate ~he platform in
; the direction o arrow A. However, as the pistons 27 enter the
region 33~ their direction of movement changes, there~y
producing a force on the platorm 11 tendin~ to ro~ate it in
a direction opposlte to the direetion of arrow h. The two orces
thus produced essentia~Ly cancel each other ~o tha~ as the
pistons are propelled around the passageway 30, the net torque
on the platform 11 is essential~y zero. As the plstons pass
~0-
5~i
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- through region 33 and work against centrifugal ~orce, their
kinetic energy is converted into potential energy as -they enter
the radially-extending region 34~ Now, and assuming that the
platform 11 is rotated, the abutting pistons 27 in region 34 will
be urged radially outwardly by centrifugal force; and as they pass
through the pocketed wheels 24 and 25, torque will be imparted
to the pocketed wheels which is coupled through gears 21, 17 and
18 to the stationary gear 16. The energy of the pistons,
which are urged radially outwardly by centrifugal force in
region 34, is thus converted into rotational energy used to
drive the platform 11 in the direction of arrow A as shown in
Fig. 1. It will be appxeciated that a starter motor or some
other device to initially rotate the platform may be required to
initiate centrifugal force on the pistons in region 34.
In addition to converting the energy of the pistons
into rotational energy, the gear system just described has two
other functions. The second function is to maintain the entire
rotating system of the rotating energy convexted at a desired
velocity. The third function of the gear system is to feed the
pistons into the expander region 32 and provide thrust to overcome
frictional drag of the pistons in the loop passageway.
The two unidirectional energy converter loops according
to the invention are disposed at mutually-exclusive sectors which
are spaced 180 from each other and supported by the platform 11.
While it is possible to use a single closed-loop passageway, it
is obviously preferable to use at least two diametrically-opposed
passageways in order that the rotatiny pla-tform 11 will be
balanced rotationally. Furtherrnore, it will be appreciated tha~
~9S2~;
a series vf platforms such as that shown herein may be gtacked
ln spaced-apar~ relation for rota~ion about a common axis 12.
A practlcal engine incorporating the principles of
the inventlon may, ~or example, employ a three-foot diameter
platform having a thickness twice the diameter of ~he pistons 27.
The rotating engine may incorporate ten unidirectional energy
conversion loops having pistons with diameters of 1-1/8 inches.
Such an engine will develop approximately 50 horsepower while
the overall size of the engine will be about three feet in
diamete~ and about one foot long, not including ducting for the
steam and exhaust. Under these circumstances, ~he frequency of
the pistons in the passageways would be about 100 per second
while the platform rotates at a spPed of about 650 revolutlons
per minute. Such a concept for a rotating engine has a signi-
icant potential for practical low-temperature steam engines
based on a 66 psia a~ 300F steam inlet pressure and a 3 psla
at 140 steam outlet pressure.
Fig. 6 illustxates another embodiment of the invention
incorpora~ing the principles of the Brayton cycle. Because of
the simil-arity between the parts forming the rotating engine for
a Brayton cycle and the parts forming a rotating engine for
operation according to the Rankine cycle as just described,
elements of Fig. 6 which correspond to those of Flg. 5 are
identified by like reference numerals. The expander region 32
of each continuous, closed-loop passageway 30 curves along a
90 circumferential part of the platform 11. A combined exhaust
and intake section 50 receives the pistons ~rom the expander
region 32. An exhsust mani~old 51 delivers the exhausE gases
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~95;~
carried be~ween successive pistons. The ~xhaust ga~es arereplaced by fr~sh air from an inlet manifold 52. From region 50,
the pi5ton5 pass into a compres~ion reg1On 53. The gases com-
pressed between the pistons are delivered by a manifold 54 a~
an increased pressure through a check valve 55 and into R
combustion chamber 56. The compressed alr is heated ln the
combustion chamber and introduced into the unidixec~ional energy
conversion loop by an inlet condui~ 57. The heated air
accelerates ~he pi~tons .in succession along the expander règion
32. Liquid fuel is fed from a ~tationary tank on the rotating
platform through a coaxial pipe in shaf~ 13 with a rotating shaft
seal. The fuel is then ed ~y a conduit 58 into the conbustion
chamber 56~
. ~s each piston exits from ~he expander region 32 in
succession, the velocity of the piston is at a maximum relative
~o the unidirectional energy conversion loop formed by its
passageway 30. The kinetic energy of the piston is thus converted
into potential energy as the pistons approach the center o the
rotating platform ll ~n passing thrcugh arcuate regions 50 and 53.
The L;inetic energy of the piston is also expended by compression
of air to form the compressed air supply which is fed into the
com~ustion chamber and then, when heated, fed into the expander
~nlet. In the radially-extending region 34 of the passageway,
the pistons apply centrifugal force to the pocketed wheels. The
mechanical power formèd by the unidirectional energy conversion
loop is the net centriugal orce imparted to the platform
through ~he sprocket-gear ~rain.
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~ ~9 ~S 2~
The seeond unidirec~ional energy conversion loop
supported by the platform 11 ln Fi~. 6 i~ iden~ical to the first
and positioned diametri.cally opposi~e the fir8t loop. It is
again apparent that a series of pla~forms 11 may be 6tacked
S in superimposed spaced-apart relation along the same ~xis 12.
Thus, the unidirectional energy conversion engine operating
. according to the Brayton cycle may consis~ of multiple uni-
directional energy conversion loops as was thc case with the
embodiment o~ Figs, 1-5.
Figs. 7 and 8 illustrate another embodiment of the
invention wherein a single passageway is utiliæed on a rotating
platform rsther than two passageways as in ~he embodiment of
Figs. 1-6. Since many of the parts forming the rotating engine
of the embodiment of Figs. 7 and 8 are the same or similar to
those of Figs. 1-6, certain elements of Figs. 7 and 8 which
correspond to those of Figs. 1-6 are identified by like reference
numerals.
In the rotating unidirectional energy converter shown
in Figs. 7 and 8, a platform 100 is provided which rotates about
a central axis 102. The platform 100 is elongated but sy~metrical
about the axis of rotation 102 and is, therefore~ balanced about
the axis of rotation. The platform 100 can be formed from upper
and lowex halves lOOA and lOOB as shown in Fig. 8. Formed in
the upper and lower halves lOOA and lOOB is a 6ingle continuous,
closed-loop passageway lQ4 having two s~raight portions 106 and
108 on opposite sides of the axis of rotation 102. The opposite
ends of the straight portions 106 and 108 are ~nterconnected by
curved portions 110 and 112, respectivelyJ the portions 110 and
~l~t-
112 also be~ng on opposite ~ides of the Mxls o~ ~otation 102
of th~ plat~orm 100. Thus, opposi~e ~ide~ of the pas8ageway
104 are arranged ~ymmetrically, and bal~nced, abou~ the axis of
rotation 102. The pl~tfo~m 100 ~B generally ell~ pt~eal in
shape, meaning that it i~ long as compared to its width, having
~emicircular end portlons connected by ~tralght portions.
Instead of forming the passageway 104 from upper and lower
pla~es lOOA and lOOB, it is also possible to form the passageway
from a tube which is rigidly mounted on a rotatabl~ platform,
not shown. Other orms of construction will be readily apparent
to those skilled in the art.
The loop passageway 104 is made up of four regions.
These comprise a ~irst expander region 114, a first thruster
region 116, a second expander region 118 and a second thruster
xegion 120. Rota~able thruster wheels 122 and 124 are mounted
for rotation on the platform at the respec~ive axes of the two
curved end portions 110 and 112 of passageway 104. The thrus~er
wheels 122 and 124 are provided with pocke~s 126, uniformly
spaced`about their outer peripheries, which are adapted to
engage successi~e pistons 27 through the open inner faces of
the curved end portions 110 and 112 of the passageway 104. As
the pocket thruster wheels 122 and 124 rotate7 they serve to
move ~uccessive pistons through the curved end portions 110 and
112 and into the respective expander regions 114 and 11~, The
rotating thruster wheels also serve to drive the rotating pla~-
orm 100 and the shaft 13 connected thereto through central,
stationary main gear 16 and appropriate idler gears 17 and 17'
located beneath the platform 100. Xdler gears 17 and 17'~ in
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5 ~6
turn, mesh wlth gears 18 and 18' connec~ed to the rotatable
pocket wheels 122 and 1249 respectlvely, as best shown in
Fig. 8. Thus, as the pocket wheels 122 and 124 rotate in the
direction of the arrows shown in Fig. 7, torque will be ~rans-
mltted to the shaft 13 to cause it and the platform 100 connected
thereto to rotate in t.he direction of arrow 128. The shaft 13
may be conveniently journaled in bearings 130 and 132 as shown
in Fig. 8.
In the operation of the embodiment shown in Figs. 7
and 8, an ideal diatomic gas (e.g., air or steam) a~ a pressure
elevated above ambient (i.e., from a compressor, boiler or the
like) is introduced into the passageway 104 via inlet port 45
located between the second thruster region 120 and the irst
expander region 114, and via inlet port 45' loca~ed between the
firs~ thruster region 116 and second expander region 118. Gas
is exhausted from the pass~geway via a venting port (or ports)
134 located between the firs~ expander region 114 and the first
thruster region 116, or via port ~or ports) 136 located between
the second expander region 118 and the second thruster region
120. The pistons 27 act as porting valves at the inlet and venting
ports as in the embodiment of FLgs. l-6. Passageways or s~ots
44 and 44' can be provided to deliver steam or another expan~ible
fluid from chamber 43, similar to chamber 43 shown in Fig. 4, ~o
the inle~ ports 45 and 45'.
The pressurized gas entering the first expander region
114 through inlet port 45 drives successive pistons 27 through
the expander region 114 against the centriugal force fi~ld
generated by rotation of the platform 100. That is, the pistons
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~95~6
must work again3~ centrifugal ~orce a~ they approach the center
of rotatl.on of platform 100. ~hen the next piston close~ o~
the inle~ port 45, the unit cell of gas between the pistons ~s
closed off from the inlet por~ 45 and expands adiabatic~lly as
the lead piston m~ves through the expander re~ion. When the
piston ahead of the piston in the expander region 114 traverses
venting port 134, the unit cell of gas ahead of ~he piston
still in the expander reg~on 114 is exhausted through the venting
port. The piston in ~he expander re~ion then arrives at the
beginning of the thrus~er region 116 and closes off the venting
port 134; while the ensuing piston is driven ~hrough the expander
region in accordance with ~he cycle just descri~ed.
Upon leaving the expander region 114, th~ piston enters
the thrus~er region 116 which is filled with pistons. When the
plstons are in ~he thruster region, in closely-abutting relation-
~hip, ~hey are urged toward the curved end portion 112 of the
passageway 104 under the in~luence o~ centrifugal force. That
is, they are urged outwardly in relation to the axis of rotat~on
102 of the platform 100 by centrifugal force. In this process,
they engage the pocketed thruster wheel 124 and impart torque
thereto, causing it to rotate with the rota~ion being ~rans-
mitted through gears 18' and 17' ~o central gear 16, thereby
caùsing the entire platform 100 and the drive sha~t 13 to rota~e
~n the direction indicated by arrow 128 in bearings 130 and 132
25 (Fig. 8) . The energy of the pis~ons, which are ur~ed ou~wardly
by centrifugal force in regions 116 and 120, ls thus converted
~nto rotational energy of the platform. Instead o using gears
as ~n the embodiment shown ~n Flgs. 7 and 8, lt is, of course,
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9~
also possible t:o utllize dr:Lve chalns or other ~ultable means
in accordance wlth well-known ~echn~ques.
As the ~hrus~er wheel~ 122 and 124 ro~ate, ~hey feed
success~ve ~nes of the pistons to the expander regions 114 and
118 where the cycle deseribed above ls repeated. In addition
~o convèrting the energy of the pistons 27 lnto rotational
energy, the gear system described above has two other functions.
The second function is to maintain the entire rotating system
. of ~he rotating energy converter at a desired velocity. The
third func~ion o the gear system is ~o feed the pistons in~o
the expander regions 114 and 118 and to provide thrust to over-
come ~rictional drag of the pistons in ~he loop passageway.
It can thus be seen that the rotating passageway 104
of the embodiment of Figs. 7 and 8 comprises, in series 9 a
first expander regi~n 114, a first thruster region 116, a second
expander region 118 and a second thruster region 120, This
is in contrast to the embodiments shown in Figs. 1-6 wherein
each passageway comprises only one expander region and one
thruster region. However, except as noted above, ~his
embodiment functions in a manner generally similar to ~he
embodiments previously discussed. A starter motor or some other
dev~ce to initially rotate the platform 100 m~y be required to
initiate cen~rifugal force o~ the pistons in regions 1~6 and
120.
In the embodimen~ shown in Figs. 7 and 8~ steam may
be used ~or ~he opera~ion o the rotatlng pLatform 100 in
accordance with the Rankine cycle as in the previously-described
embodimentsO When ~team is used, the force exerted by the
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S2~
expanaing steam, which enters -the passageway 104 through ports
45 and 45', propels the pis-tons 27 through -the expander regions
114 and 118. The steam is exhaus-ted ~hrough venting ports 134
and 136 as the pistons enter the thruster regions 116 and 120.
Venting ports 134 and 136 may be open to the atmosphere or, if
desired, a system of ducts, not shown,may be used to return
the steam and/or condensate to the boiler in a manner similar
to that of Fig. 4.
While the rotating engine as shown in Figs. 7 and 8
may operate in accordance with the thermodynamic principles
of the Rankine cycle as described above, this embodiment of the
invention, appropriately modified, may also function in accordance
with the principles of -the Brayton, Diesel, or Otto cycles as
briefly described below.
In the operation of the embodiment of Figs 7 and 8
according to the Brayton cycle, compressed gas (typically air)
is heated in a combustion chamber rotating on the platform as
in Fig. 6, or by a heat exchanger rotating on -the platform, with
the heat exchanger being connected to a stationary external heat
source via a coaxial duct. The heated, compressed gas is then
introduced into the expander regions from appropriate conduits
via the inlet ports. After expansion, th~ gas is exhausted at
ambient pressure via the venting ports 134 and 136 either directly
to the atmosphere or through a coaxial duct. The compressed
gas may be obtained via conventional compressor means, either
stationary or rotating on the platform; however, it is preferred
to obtain the compressed gas from a separate unidirectional energy
converter loop which is rota-ting about the same axis of rotation
_~ g_
~9s~
(i~e., stacked above or below the plat~orm), and which 1~
adapted to function as a compres~or in the mann~r describe(l
in connection with Figs. 7 and 8 he~eir,after cr as described
in U.S. Patent No. 3,859 9 7~9, Fawcett ~t al,
In the opera~ion of the el~bodiment of Figs. 7 and 8
in accordance with the principle.s o the Diesel cycle, an erpand-
ing gas is provided in the expander regions by way of internal
combustion within these regions. Compressed a~r (typically from
one of the sources described above in reference to ~he Bray~on
cycle) is introduced into the regions via the inlet por~s 45 and
45', Liquid or gaseous uel is fed into the expander regions
114 and 118 when ~he inlet ports are closed off by the pistons
leaving the thruster regions. Combustion takes place in the
expander regions and is cycled to effect expanding gas behind
each piston as it enters the expander regions 116 and 120. That
isj combustion takes place periodic~lly to propel successive
ones of the pistons through the expander regions. As with the
Brayton cycle, the combustion gases may be exhausted at ambient
pressure via the venting port directly ~o the atmosphere or
through a coaxial duct.
The operation of the embodiment o~ Figs. 7 and 8
according to the Otto cycle is similar to that described above
regardin~ the Diesel cycle. The fuel and air may be separately
introduced into the expander regions, as in the Diesel cycle,
or ~che fuel may be mixed with the incoming air before vr after
it is compressed. Ignitlon of the uel-air mixture is efected
in the expander regions 114 and 118 by means of a conventional
spark system located in an approprlate recessed area in these
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~9~s~
re~ions. As in the Diesel cycle, cornbustion ~ cycled to
effect expanding gas successively behind each pi6ton as it
passes so as to propel successive ones of the pi~tons ~hrough
the expander regions.
If the platform 100 shown in Figs, 7 and 8 is rotated
by a motor or some other external power source in a directi.on
opposite that shown, gas at ambient pressure will be taken into
~he passageway 104 via ports 134 and 136 and will be exhausted
at an elevated pressure via ports 45 and 45'. In this regard,
the system can function as a compressor. If the platform 100 is
rotated by a motor, the system of gears int~rconnecting the
thruster wheels 122 and 124 to the central shaft 13 will act to
rotate the thruster wheels. The rotating ~hruster wheels will
then move the stacked pistons 25 in the thruster regions toward
the axis o~ rotation of the platform, so that upon passing ports
134 and 136, the pistons will travel through the expander regions
114 and 118 under ~he influence of cen~rifugal foree. The gas
between the pistons will be adiabatically compressed by the
moving pistons in ~he expander regions 116 and 120 which would
more properly be termed "compressor regions" in this mode.
It will also be appreciated that a series of uni-
directional ener~y conver~ers may be stacked in superimposed,
spaced-apart relation ~or rotation upon shaft 13 about the common
ax~s 102. In the embodiment of Figs, 7 and 8, ~he following
general observations can be made: (1) the change in enth~lpy
of the gas in the expander re~ions produces net work, which is
per~ormed on the thruster wheels 122 and 124 via the pistons 27, and
then transmitted to the rotating platform 100 and the shaft 13;
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~39~52~
(2) ~he cllange in en~llalpy o~ the ga~ in th~ expander regions
t~anafer~ encrgy via the centrifugal f1eld (potential) energy
~tored i~n the mass of the piston3 as they move through the
expander regions from a larger radiu~ of rotation ~.e., about
the axi~ of rotation o~ the platform 100) to a smaller radius
of rotation (i.e., nearer the axis of rotation); (3) the initial
and final velocities o~ the pistons traveling in the expander
regions rela~ive to the rotating platform are equal; and (4)
the inlet and venting ~as port sizes, the mass of the pi~tons, th(
speed of rotation of the thruster wheels and the platform, and
the inlet and exit states of the gas are all interrelated in the
operation of, and the net work produced in, this sy9tem. Under
some conditions of operation, the gas pressure ~n the expander
region during part of the operating cycle may be below ambient.
In Figs. 9A and 9B, alternative forms of the pistons
27 are shown. In Fig. 9A, the piston 27A comprises a body having
a central annular slot 140 and large diameter end portion~ 142
and 144 provided with spherically-beveled edges 146 which can
engage the periphery of the passageway 104 as the pistons 27A
pass around the curved portions 110 and 112. The large diameter
portions 142 and 144 are hollow as shown. The configuration showr
in Fig. 9A comprises, in effect, two interconnected pistons
~eparated by the reduced diameter portion 140 which receives the
radially, outwardly-projecting prongs on the pocketed wheels 122
and 124 as the pistons move around thé curved portions 110 and 11`
Lightly-loaded piston rings (not shown) may optionally
be located in recesses formed within the outer surface of the
pistons, 90 as to reduce losses due to leakage of the ~luid
medium around the pistons.
Fig. 9B i9 similar to that of Fig. 9A except that the
piston 27B in this case comprises two spherical end portions 148
and 150 interconnected by reduced diameter portion 152 which
again receives the radially, outwardly-projecting prongs on the
thruster wheels 122 and 124.
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s~
A piston such as that shown in Figure 9~, or some other con-
figuration having a cylindrical outer periphery (as contrasted ~o a sphere)
may be preferable in order that the cylindrical surface can m~re positively
close off thc ports 13~ and 136 as they pass thereby. In this respect, the
ports 134 and 136 should be as small in cross section as possible while
affording the requiTed flow volume therethroughO
The embodiments of the invention described above utilize an
arrangement wherein the pocketed thruster wheels are mechanically linked
ti~e. coupled) to both the rotating platform and the engine dri~e shaft via
a system of gears or drive chains, etc. In an alternative preferred embodi-
nent of the invention it may be desirable to decouple the thruster wheels
from the platform, and to provide a separate, external drive motor which can
be utili~ed to separately drive the rotating platform at a speed of rotation
which is independent from that of the pocketed thruster wheels. It is apparent
that the speed of rotation of the platform is related to the torque produced
by the rotating engine of the present invention, whereas the speed of rota-
tion of the thruster wheels is proportional to the rate of torque applied to
the engine drive shaft (i.e. shaft power). ~y providing a separate drive
~otor to independently drive the platform, the rotating engine of the present
invention can be utilized to produce torque independently from engine drive
shaft speed (i.e. high torque can be produced at low or variable speed).
As was explained in the introductory portion of the specification,
it is also possible to use the various embodiments of the invention previously
described as compressoTs. In the embodiment shown in Figures 1-5, for
example, the platform 11 can be rotated in a direction opposite to ~hat
indicated by arrow A, in which case the pocketed wheels 2~ and 25 will force
the pistons 27 radially inwardly along region 3~. In region 33, the pistons
are forced radially outwardly while drawing air into the passageway 30 through
ports 31. The pistons 27, propelled radially outwardly by centri~ugal force,
then travel through region 32 and in so doing compress the air between
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successive ones of the pistons such that their kinetic energy is converted
into compressed gas. The compressed gas then exits the passageway 30 through
the portal openings in the bushing 46 and is conveyed through slot 44 to the
duct 40.
The pla~form 11 may be driven by suitable gearing coupled to the
shaft 13, by gearing which meshes with a ring gear carried on the periphery
of the platform 11, or by a shaft which is coaxial with shaft 13 on the
opposite side of the platform 11. The same alternatives are possible to
derive rotary energy from the device when used as an engine. When plural ;
encrgy conversion devices are employed in superimposed spaced-apart
relation along the same axis 12, they may be interconnected by means of the
hollow shaft 13 from which rotary energy is derived by way of suitable gear-
ing. In the case of only two energy converters on the same shaft, it is
apparent $hat the platforms 11 could be directly interconnected in back-to-
back relationship.
Although the invention has been shown in connection with certain
specific embodiments~ it will be readily apparent to those skilled in the
art that various changes in form and arrangement of parts may be made to
suit requirements without departing from the spirit and scope of the
invention.
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