US3514236A - Rotary engine with epicyclic rotor - Google Patents

Rotary engine with epicyclic rotor Download PDF

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Publication number
US3514236A
US3514236A US712820A US3514236DA US3514236A US 3514236 A US3514236 A US 3514236A US 712820 A US712820 A US 712820A US 3514236D A US3514236D A US 3514236DA US 3514236 A US3514236 A US 3514236A
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US
United States
Prior art keywords
rotor
stator
engine
axis
cusps
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Expired - Lifetime
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US712820A
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English (en)
Inventor
Mihail Stoyanov Rashev
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
VISH MACHINNO ELEKTROTECHNITCH
VISH MACHINNO ELEKTROTECHNITCHESKI INST
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VISH MACHINNO ELEKTROTECHNITCH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • F02B53/02—Methods of operating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • F02B53/10—Fuel supply; Introducing fuel to combustion space
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • An improved rotary engine is provided with three combustion chambers each having a variable volume and relatively fixed angular bondaries defined by adjacent pairs of inwardly directed cusps spaced at 120 around the periphery of the engine stator.
  • the stator is drivingly coupled to the engine rotor in such a manner that the rotation of the rotor causes the cusps to oscillate over spaced portions of an epicyclic path identical to that defined by an epicyclic outer surface of the rotor, thereby maintaining the rotor surface in engagement with each of the three cusps at all times.
  • Several types of rotary internal combustion engines employ lobed pistons which respectively contact selected portions of a surrounding shaped stator through suitable seals to define combustion chambers, which are provided with suitable ignition means. Each chamber is supplied at appropriate intervals with an ignitable mixture. After ignition has taken place in one chamber the piston is driven away from its then-defined place of engagement with the stator periphery, and its lobed portion contacts a different predetermined place on the stator periphery to define the boundary of a new working space for the next portion of the cycle. Thus, as the piston goes through its revolution the position of the operative combustion chamber varies.
  • Each point on the stator engageable with a piston lobe to form a chamber boundary is subjected to a cyclical impact load as the chamber boundary associated with that point is established during the piston revolution. Such repeated impact loads fatigue the engine elements and the seals and cause premature failure.
  • the stator is provided with three combustion chambers of varying volume but relatively fixed angular position.
  • the chambers are peripherally bounded by successive pairs of three inwardly extending cusps disposed on the stator periphery and spaced at 120 angular intervals about the rotor axis, which is fixed with respect to the surrounding stator.
  • the stator is drivingly coupled to the rotor in such a way that upon the rotation of the rotor the three fixed cusps on the stator oscillate back and forth over spaced portions of a common epicyclic path relative to the rotor axis.
  • the rotor is provided with an outer epicyclic surface coincident with the path of oscillation of the cusps so that the moving rotor is always in contact with the stator at the three oscillating points defining the boundaries of the combustion chambers.
  • rotor is aflixed to a hollow engine shaft which rigidly carries a first gear coaxially therewith in spaced relation to the rotor.
  • Three rotatable non-orbiting planetary gears engage the outer periphery of the first gear at 120 intervals about the rotor axis.
  • Three stator projections extending from the respective cusps are eccentrically carried within the planetary gears to oscillate the cusps epicyclically with respect to the rotor axis as the rotor rotates.
  • Each chamber has a spark plug extending through the peripheral wall of the stator intermediate the bounding cusps.
  • Four-cycle operation of each chamher is accomplished by providing the rotor with spaced radial intake and exhaust channels communicating with a carburetor and the outside air, respectively, through the hollow engine shaft.
  • the driving coupling between the rotor and the stator is operative outside the combustion region of the engine so that vibration, weight and cooling requirements of the engine are minimized.
  • the rotor and stator are finned and are air-cooled by suitable means carried on the engine shaft.
  • FIG. 1-4 are simplified end views of the combustion chambers disposed in a rotary engine constructed in accordance with the invention, depicting the relative volumes of the chambers at successive portions of the rotor cycle;
  • FIG. 5 is an end view, partially broken away, of a rotary engine embodying the combustion chambers shown in FIGS. l-4;
  • FIG. 6 is a longitudinal view, partly broken away, of the engine of FIG. 5, illustrating the rotor-stator coupling and the engine lubricating system;
  • FIG. 7 is a longitudinal view, partly broken away, of the engine of FIG. 5, illustrating the components mounted on the engine shaft and the engine air-cooling system;
  • FIG. 8 is a perspective view of the sealing arrangement for the engine of FIG. 5;
  • FIG. 9 is a fragmentary view of a portion of the stator wall of the engine of FIG. 5, illustrating alternative forms of several of the packings supported therein;
  • FIG. 10 is a sectional view taken on line 10-10 of FIG. 9;
  • FIG. 11 is a sectional view taken on line 11--11 of FIG. 9;
  • FIG. 12 is a fragmentary view of the sealing arrangement of FIG. 8, illustrating details of a corner packing and its means of retention;
  • FIG. 13 is an enlarged fragmentary view of a portion of the arrangement of FIG. 12.
  • FIG. 14 is a fragmentary longitudinal view of the shaftmounted components of an engine similar to that of FIG. 5, illustrating fuel injection passages in the rotor.
  • FIG. 1 illustrates a combustion portion 69 of an illustrative rotary engine, constructed in accordance with the invention.
  • the portion 69 includes an essentially annular stator wall 32 supported as described below around a fixed engine axis 70.
  • the axis 70 extends in the direction perpendicular to the figure.
  • An inner periphery 32a of the stator wall includes three essentially identical arcuate portions bounded by three inwardly extending cusps a, 75b, and 75c.
  • the cusps 75 are respectively disposed at angular intervals around the stator wall 32 with reference to the fixed engine axis 70.
  • Each of the cusps 75 carries a suitable packing (not shown) for forming a fluid-tight seal with a rotor 10, as described below.
  • a planetary gear arrangement consisting of a central gear 6 mounted coaxially with the engine axis 70 and three non-orbiting planetary gears 21 externally engaging the the periphery of the gear 6 at 120 angular intervals around the engine axis 70.
  • the planetary gears 21, each of which is associated with a separate one of the cusps 75, are mounted for rotation about individual fixed axes 74 respectively parallel to the engine axis 70.
  • the stator is eccentrically supported for oscillation about the engine axis 70 by three projections 2323 extending from each cusp 75 perpendicular to and inwardly of the plane of the drawing and rigidly received in a separate one of the planetary gears 21 at an off-axis location spaced a predetermined distance A from the axis 74 of the planetary gear.
  • each projection 23 will drive the associated cusp 75 joined thereto in an oscillatory path about, rather than a rotational path about, rather than a rotational path around the engine axis 70.
  • Each cycle of rotation of a plantary gear 21 causes a corresponding cycle of oscillation of the associated cusp 75. Since every off-axis point on the gear 21, including the point of contact with the projection 23, will describe an epicyclical path as it rotates about its fixed axis on the periphery of the gear 6, the associated cusp 75 will likewise describe an epicyclical path as it oscillates.
  • the relative angular positions of each of the projections 23 on the radius A of the planetary gears are chosen so that the oscillations of all of the cusps 75a, 75b, and 750 are in phase, i.e. so that the entire stator 32 is oscillated through a total angular sector a about the axis 70 along the common epicyclic path in a nonbinding manner once during each cycle of rotation of the nonorbiting planetary gears 21.
  • the resulting oscillation of the stator is shown in FIGS. 1-4 with particular reference to the position of the cusp 750.
  • the projection 23 on the gear 21 is initially directly below the axis of such gear, and the cusp 75c is in alignment with a reference vertical axis 110.
  • the gear 21 has rotated through a quarter of a revolution to one of its maximum displacement positions, and the projection 23 has correspondingly moved the stator counterclockwise from the axis 110 through the angular sector a/Z with respect to the engine axis 70.
  • the gear 21 has rotated another quarter of a revolution and the stator has moved back clockwise through the angular sector oz/Z to its initial position.
  • the gear 21 has rotated through another quarter of a revolution to its opposite maximum displacement position, and the stator has moved clockwise from the axis 110 through an angular sector 06/2 with respect to the engine axis 70. It will be evident that, during the final quarter of revolution of the gear 21, the stator will move back counterclockwise through the angular sector a/2 to its initial position shown in FIG. 1 to complete its cycle of oscillation. It is seen, therefore that the stator has a zero net angular displacement during each cycle of rotation of the gear 21.
  • the rotor 10 is disposed within the stator and, like gear 6, is mounted coaxial with the engine axis 70.
  • the rotor 10 is provided with an epicyclical outer surface 76 that is coincident with the epicyclical path traversed by the periphery 32a of the stator during each cycle of oscillation thereof.
  • the outer surface 76 thereof will always abut the cusps 75 on the stator. It will be noted from FIGS.
  • This rotor-cusp arrangement divides the working space inside the stator wall 32 into three combustion chambers 71, 72, and 73. These chambers are angularly bounded by adjacent pairs of the cusps 75 and radially bounded by the stator wall periphery 32a and the outer surface 76 of the rotor 10.
  • Each of the chambers 71, 72, and 73 will vary cyclically in volume as the rotor 10 revolves about the axis 70.
  • the upper chamber 71 is shown at approximately its minimum volume position in FIG. 1.
  • the volume of the chamber 71 increases and reaches its maximum when the rotor is in the position shown in FIG. 3.
  • Further rotation of the rotor as depicted in FIG. 4, will decrease the volume of the chamber 71 until the rotor again reaches the position shown in FIG. 1, at which time the cycle starts again.
  • Corresponding volume changes of the chambers 72 and 73 are identical in amplitude to that of the chamber 71, but are out of phase therewith; that is, the chamber 73 reaches its minimum volume position when the rotor is in the position shown in FIG. 2, i.e., sometime after the chamber 71 reaches its minimum position.
  • the chamber 72 reaches its minimum volume position in the position shown in FIG. 4, i.e., at a point of time later than that of the chamber 73. It will be noted that the overlapping volume changes in the several chambers 71-73 are similar to those experienced in the operation of the cylindrical chambers in a reciprocating piston engine having overlapping power strokes.
  • each of the chambers 7173 are fitted with a spark plug 33 extending through the stator wall 32 at a position intermediate the chamberbounding cusps 75.
  • the rotor 10 is provided with a first radial channel 11 that communicates with a suitable carburetor in the manner described below for supplying an ignitable fuel mixture into the then-opposed one of the chambers 71-73.
  • the rotor is further provided with a second radial channel 12 angularly spaced from the channel 11 for scavenging the exhaust from another one of the chambers 71-73.
  • an ignitable charge is being supplied by the rotor channel 11 to the chamber 72, Whll e tl'l6 channel 12 is scavenging exhaust from the charfiber 73.
  • the chamber 71 which is at its minimum volume position, is being ignited by a spark from the plug 33, which, is energized from a suitable distributor (not shown). Expansion of the chamber 71 because of the ignition of the compressed charge, which expansion takes place at the point in time depicted in FIG. 2, imparts rotary motion to the rotor 10.
  • scavenging of the expanded charge in the chamber 71 by the rotor channel 12 in preparation for the receipt and compression of the next charge therein is shown in FIGS. 3-4.
  • FIGS. 1-4 Similar four-stroke operations or the chambers 72 and 73 are shown in FIGS. 1-4, with the ignition strokes of the chambers 73 and 72 occurring successively later than the ignition strokes in the chamber 71.
  • each chamber will occupy an essentially fixed angular sector around the engine axis, so that problems of ignition and of supply and scavenging of the ignitable fluid are minimized.
  • FIGS. 5-7 illustrate, in more structural detail, a rotary engine whose combustion portion functions as described above in connection with FIGS. 1-4.
  • the rotor is afiixed, as by a plurality of bolts 57-57 (one of which is shown) to a pair of flanges 7A- 7A on a main engine shaft 7 for rotation about the engine axis 70.
  • the shaft 7 is supported for rotation on both sides of thet rotor 10 by a pair of bearings 9-9 suitably carried in a housing 58.
  • the central gear 6 is affixed to the shaft 7 at a location axially remote from the rotor 10.
  • An ignitable mixture is supplied from a carburetor 17 to the radial channel 11 of the rotor 10 via a hollow inlet passage 80 supported coaxially within the shaft 7 by a plurality of ribs 81-81 (FIG. 5).
  • exhaust gases entering the radial channel 12 are vented by means of (1) an outlet passage 82 isolated from the inlet passage '80 by a rotor bifurcation 83, and (2) a centrifugal wheel 4 communicating with the passage 82 and mounted on the shaft 7.
  • FIG. 5 which corresponds to the instancous rotor position shown in FIG. 3, a head packing 42 forming a seal between the rotor surface 76 and the cusp 75A is depicted.
  • the packing 42 is held in place by a retainer 39.
  • a pair of corner packings 38-38 (FIG. 8) are disposed on either side of the head packing 42.
  • each corner packing 38 is supported between the retainer 39 and a side wall 31 of the stator by means of a plurality of blade springs 43-43.
  • the side wall 31 is joined to the peripheral wall 32' (FIG. 6) of the stator by means of a plurality of bolts 5252, one of which is shown.
  • Each corner packing 38 (FIG. 8) is joined, via an elastic ring 45, to a pair of side packings 46-46, which may be supported on each stator sidewall via a blade spring (not shown).
  • the packings 38 and 46 provide a fluid-tight seal between each side wall 31 (FIG. 6) of the stator and the stator and the adjacent one of a pair of opposed sidewalls 77-77 (FIG. 7) of the rotor 10.
  • FIGS. 9-11 Alternate forms of side packings are shown in FIGS. 9-11.
  • the side packings include a plurality of circumferential segments 47-47 received in a ciroumferentially grooved member 62, which may be affixed to or form part of the sidewall 31.
  • the side packing is shown as a circumferential packing rim 63, which may be lubricated via a passage 50. In each of these two cases, the side packing is held in place by a blade spring 49.
  • a counterweight (FIG. 5) is aflixed to each of the planetary gears 21 in a position diametrically opposed to the offset position of the stator projection 23 received therein.
  • the sidewalls 77 of the rotor 10 are provided with a plurality of ribs 8-8 for purposes of air cooling.
  • each stator sidewall 31 is provided with a plurality of ribs 34-34 and the outer surface of the stator peripheral wall 32 (FIG. 6) carries a plurality of circumferential cooling ribs 35-35.
  • stator projections 23 are affixed, as by a plurality of bolts 41 (one of which is shown) to the sidewall 31 of the stator. Angular adjustment of the point of receipt of the projection 23 in the associated planetary gear 21 is facilitated by means of an eccentric sleeve 26 carried in the projection 23 and in the sidewall 31.
  • Each planetary gear 21 is supported for rotation on its axis 74 by means of a pair of bearings 18 and 19.
  • Lubrication of the bearings 18 and 19, the mated gears 6 and 21, the engine packings 38, 42, and 46 (FIG. 8), the projections 23 (FIG. 6) and the engine shaft bearing 9 is accomplished by oil suitably pumped from a crankcase 30 to a channel 59.
  • the latter channel distributes the oil to the various elements to be lubricated via suitable passages e.g. 22, 24, and 25.
  • the oil is then collected in an oil sump 29 and routed back to the crankcase 30.
  • a pair of bafile plates 27 and 28 are provided for restricting the oil path from the sidewall 31 of the stator.
  • the rotor 10 is air cooled by means of a plurality of running blades 15A which direct the air around the rotor cooling ribs 8 and radial ribs 8A via a plurality of passages 14 in the engine shaft 7.
  • the air is removed from the rotor through the passages 14 and a fan 5 mounted on the shaft 7.
  • the centrifugal wheel 4 is cooled in two ways: 1) by the fan 5 and (2) through air vented fom the interior of an output shaft 1 through an axial passage 3 and a radial passage 2.
  • the stator is cooled by means of a fan 13 mounted on the engine shaft 7.
  • the fan 13 directs air through the channels 36 (FIG. 6) to cool the stator ribs 34 and 35 in the respective areas of the three spark plugs 33.
  • the air leaves the stator through a plurality of apertures 37-37 (FIG. 5).
  • the rotor 10 may be adapted for gasoline injection or Diesel applications in the manner shown in FIG. 14. This may be accomplished by passing fuel from an axial conduit 56 associated with a suitable source (not shown) to a radial nozzle 53 in the rotor 10.
  • the fuel flow path through the rotor 10 includes a radial passage 54 terminated by the nozzle 53, and an axial passage 81 communicating at opposite ends with the conduit 56 and the radial passage 54.
  • N second gears in external engagement with the first gear at equal angular intervals around the first axis, each of the second gears being supported for nonorbital rotation about individual second fixed axes disposed parallel to the first axis;
  • a hollow stator having an inner peripheral surface including N inwardly projecting cusps spaced at equal angular intervals around the inner peripheral surface;
  • each chamber being bounded angularly by an adjacent pair of the cusps, whereby each chamber occupies a fixed mean angular sector of 360/N around the first axis.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • General Details Of Gearings (AREA)
  • Supercharger (AREA)
  • Ignition Installations For Internal Combustion Engines (AREA)
US712820A 1967-03-13 1968-03-13 Rotary engine with epicyclic rotor Expired - Lifetime US3514236A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
BG749367 1967-03-13

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US3514236A true US3514236A (en) 1970-05-26

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US712820A Expired - Lifetime US3514236A (en) 1967-03-13 1968-03-13 Rotary engine with epicyclic rotor

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US (1) US3514236A (es)
BE (1) BE712090A (es)
DE (1) DE1601839A1 (es)
ES (1) ES351497A1 (es)
FR (1) FR1563240A (es)
GB (1) GB1218579A (es)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3685498A (en) * 1971-03-24 1972-08-22 Robert M Shrewsbury Rotary engine
US3797974A (en) * 1971-06-30 1974-03-19 Dornier System Gmbh Packing strip arrangement for rotary piston engines
US3883276A (en) * 1972-10-20 1975-05-13 Volkswagenwerk Ag Discharge arrangement for the exhaust gas from the work areas of a rotary piston combustion engine
US3885897A (en) * 1972-08-16 1975-05-27 Dornier System Gmbh Lubricating device for radial sealing strips of inner-axial rotary piston engines of trochoidal construction with sliding engagement
US3914075A (en) * 1973-02-12 1975-10-21 Andre Brulfert Sliding partition rotary engine with rectilinear seals
US3967594A (en) * 1975-01-27 1976-07-06 Campbell Donald K Rotary power unit
US4012181A (en) * 1973-02-12 1977-03-15 Andre Brulfert Engine with rotor, of new type
US20110171053A1 (en) * 2008-07-29 2011-07-14 Jiri Dvorak Rotary Motor for Compressible Media

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3545818A1 (de) * 1985-12-23 1987-07-02 Wankel Gmbh Kuehlsystem einer rotationskolbenbrennkraftmaschine
JPS62153502A (ja) * 1985-12-23 1987-07-08 ウアンケル・ゲゼルシヤフト・ミト・ベシユレンクテル・ハフツング 回転ピストンエンジンの偏心軸
US5127377A (en) * 1990-12-06 1992-07-07 Yang Chung Chieh Rotary machine with oval piston in triangular chamber
CN115539238B (zh) * 2022-10-28 2024-07-26 昆明理工大学 一种转子发动机径向密封系统快速更换装置

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US914627A (en) * 1907-10-15 1909-03-09 Cooley Dev Company Rotary engine.
US3244155A (en) * 1965-05-28 1966-04-05 Laudet Pierre Rotary engine with two concentric rotors
US3280802A (en) * 1963-10-26 1966-10-25 Nsu Motorenwerke Ag Fluid cooled housing wall for internal combustion engines
US3291063A (en) * 1964-03-16 1966-12-13 Edward J Carline Rotary piston pump with single chamber
US3306531A (en) * 1967-02-28 Rotary piston machine with rotary pistons one arranged within and eccentrically with regard to the other
US3348529A (en) * 1965-08-10 1967-10-24 Messerschmitt Ag Rotary piston machine
US3359951A (en) * 1964-11-05 1967-12-26 Sabet Huschang Sealing device
US3364907A (en) * 1965-04-27 1968-01-23 Ronald J St Onge Rotary piston mechanism

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3306531A (en) * 1967-02-28 Rotary piston machine with rotary pistons one arranged within and eccentrically with regard to the other
US914627A (en) * 1907-10-15 1909-03-09 Cooley Dev Company Rotary engine.
US3280802A (en) * 1963-10-26 1966-10-25 Nsu Motorenwerke Ag Fluid cooled housing wall for internal combustion engines
US3291063A (en) * 1964-03-16 1966-12-13 Edward J Carline Rotary piston pump with single chamber
US3359951A (en) * 1964-11-05 1967-12-26 Sabet Huschang Sealing device
US3364907A (en) * 1965-04-27 1968-01-23 Ronald J St Onge Rotary piston mechanism
US3244155A (en) * 1965-05-28 1966-04-05 Laudet Pierre Rotary engine with two concentric rotors
US3348529A (en) * 1965-08-10 1967-10-24 Messerschmitt Ag Rotary piston machine

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3685498A (en) * 1971-03-24 1972-08-22 Robert M Shrewsbury Rotary engine
US3797974A (en) * 1971-06-30 1974-03-19 Dornier System Gmbh Packing strip arrangement for rotary piston engines
US3885897A (en) * 1972-08-16 1975-05-27 Dornier System Gmbh Lubricating device for radial sealing strips of inner-axial rotary piston engines of trochoidal construction with sliding engagement
US3883276A (en) * 1972-10-20 1975-05-13 Volkswagenwerk Ag Discharge arrangement for the exhaust gas from the work areas of a rotary piston combustion engine
US3914075A (en) * 1973-02-12 1975-10-21 Andre Brulfert Sliding partition rotary engine with rectilinear seals
US4012181A (en) * 1973-02-12 1977-03-15 Andre Brulfert Engine with rotor, of new type
US3967594A (en) * 1975-01-27 1976-07-06 Campbell Donald K Rotary power unit
US20110171053A1 (en) * 2008-07-29 2011-07-14 Jiri Dvorak Rotary Motor for Compressible Media
US8721310B2 (en) * 2008-07-29 2014-05-13 Jiri Dvorak Rotary motor for compressible media

Also Published As

Publication number Publication date
ES351497A1 (es) 1969-06-01
FR1563240A (es) 1969-04-11
DE1601839A1 (de) 1971-01-21
GB1218579A (en) 1971-01-06
BE712090A (es) 1968-07-15

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