US3919980A - Rotary engine - Google Patents

Rotary engine Download PDF

Info

Publication number
US3919980A
US3919980A US342940A US34294073A US3919980A US 3919980 A US3919980 A US 3919980A US 342940 A US342940 A US 342940A US 34294073 A US34294073 A US 34294073A US 3919980 A US3919980 A US 3919980A
Authority
US
United States
Prior art keywords
stator
rotor
rotary engine
vanes
axis
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US342940A
Other languages
English (en)
Inventor
Franklin Veatch
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.)
Standard Oil Co
Original Assignee
Standard Oil Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Standard Oil Co filed Critical Standard Oil Co
Priority to US342940A priority Critical patent/US3919980A/en
Priority to BE160137A priority patent/BE833528A/fr
Application granted granted Critical
Publication of US3919980A publication Critical patent/US3919980A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
    • F01C1/356—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F01C1/3562—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F01C1/3564—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • 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
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
    • F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into cylinder
    • 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
    • F02B2053/005—Wankel engines
    • 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
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • 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

  • the present invention is a new rotary engine consisting of a stator with a cylindrical cavity, a hollow cylindrical rotor located within the cylindrical cavity of the stator, a power shaft along the axis of the stator and an eccentric mounted on the power shaft.
  • a plurality of spaced vanes are mounted in the stator for reciprocal movement with respect to the stator to provide working chambers between adjacent vanes, the stator, and the rotor so that rolling movement of the rotor around the interior of the stator in response to combustion of explosive charges in the chambers causes the eccentric to roll around the inner surface of the rotor and thereby rotate the power shaft.
  • the present invention is a new rotary engine.
  • This rotary engine comprises: a stator having spaced end walls and a peripheral wall interconnecting the end walls to form a cylindrical cavity having an axis, the inner surface of the peripheral wall having a substantially circular profile; a hollow cylindrical rotor having an outer and inner surface, each having a substantially circular profile, and supported in the cavity for rolling motion with respect to the inner surface of the stator about an axis spaced from but parallel to the stator axis; the rotor having an internal diameter such that the stator axis is located inside the inner surface of the rotor and an external diameter that is less than the diameter of the inner surface of the stator; means for sealing the outer surface of the rotor with respect to its inner surface; an eccentric mounted within the inner surface of the rotor for rotation about the stator axis and in rolling contact with the inner surface of the rotor, whereby in operation the rotor axis describes a substantially circular path around the stator
  • ignition of the fuel causes the rotor to roll around the inner surface of the peripheral wall of the cylindrical cavity of the stator.
  • This rolling movement of the rotor causes the eccentric, which is in rolling contact with the inner surface of the rotor, to revolve around the axis of the stator describing the path traced by the axis of the rotor and thereby rotate the power shaft.
  • FIG. 1 is a cross sectional view through the rotary engine of this invention
  • FIG. 2 is a sectional view takenn along the line 22 of FIG. 1;
  • FIGS. 3-12 are schematic views illustrating the cycle of the rotary engine of this invention through two revolutions.
  • the rotary engine of this invention consists generally of a stator located within a housing 22 and a rotor 24 rotatably supported within stator 20.
  • stator 20 com prises a pair of spaced end walls 26 and a peripheral wall 28 interconnecting end walls 26 to form a cylindrical cavity 30 having an axis 32.
  • the inner surface 34 of peripheral wall 28 has a substantially circular profile.
  • rotor'24 is a hollow cylinder supported in stator cavity 30 for rolling motion around the inner surface 34 of the stator about an axis 36 spaced from, but parallel to, stator axis
  • the outer surface 38 of rotor 24 has a substantially circular profile and a diameter less than the diameter of the circular inner surface 34 of stator 20.
  • the diameter of outer surface 38 is at least about and more preferably from about to about of the diameter of stator cavity 30.
  • the inner surface of hollow rotor 24 also has a substantially circular profile and a diameter that permits the stator axis 32 to be located inside the inner surface 40 of the rotor.
  • means are provided for sealing the outer surface 38 of rotor 24 with respect to its inner surface 40.
  • this means comprises an annular sealing ring 42 journaled in a groove 44 extending around the outer edges 46 of both sides of rotor 24.
  • These sealing rings 42 are biased against end walls 26 of stator 20 to movably seal the volume inside of rotor 24 from the volume between rotor 24 and stator 20.
  • a power shaft 50 Inside of rotor 24 and along stator axis 32 is mounted a power shaft 50 that is journaled in bearings 52 in end walls 26 and extends out through housing 22.
  • an eccentric 54 is mounted on power shaft 50 for rotation about stator axis 32.
  • Eccentric 54 supports rotor 24 in stator cavity 30 and is in rolling contact with the inner surface 40 of the rotor, so that as eccentric 54 rotates about stator axis 32 responsive to rolling movement of rotor 24 within stator cavity 30, the axis of rotor 24 describes a substantially circular path, as shown in FIG. 1, around stator axis 32.
  • a low friction bearing 56 is rollably mounted around the outer surface of eccentric 54.
  • the radial length 58 of eccentric 54 from stator axis 32 plus the distance between the inner surface 40 and outer surface 38 of rotor 24 is essentially equal to, but slightly less than, the radius of the circular inner surface 34 of stator peripheral wall 28 to provide for maximum compression and exhaust of the explosive charge in the engine.
  • vanes 60 are slidably mounted in the peripheral wall 28 of stator 20 for reciprocal movement with respect to the inner surface 34 of the stator.
  • vanes 60 reciprocate in a substantially radial direction with respect to stator axis 32 and move in sealing relationship with end walls 26 of the stator.
  • this guide means comprises slots 62 in end walls 26 that extend in a radial direction over the length of travel of the vanes.
  • vanes 60 are biased into sealing engagement with the outer surface 38 of rotor 24 regardless of its relative position within stator cavity 30, and means are provided for holding these vanes in sealing engagement with the rotor.
  • this means can include springs 64 as well as the pressure of the compressed gas in the working chambers.
  • vanes 60 provide a plurality of circumferentially spaced working chambers around the inner surface of stator 20, each working chamber being defined by adjacent vanes 60, the outer surface 38 of rotor 24, and the inner surface 34 and the end walls 26 of stator 20.
  • each working chamber there is also provided an intake port 70 for admitting fuel to the working chamber and an exhaust port 72 for discharging exhaust products from each chamber.
  • ignition means such as a spark plug 74, can be provided for each working chamber depending on the type of fuel being used, as is well known to those skilled in the art.
  • intake and exhaust ports 70, 72 are provided with suitable valves 76 for opening and closing such ports and means are provided for controlling operation of these valves.
  • the means for controlling the valves includes a cam-drive gear 78 affixed to power shaft 50.
  • Cam-drive gear 78 drives suitable cam gears 80 which, in turn, actuate the movement of valves 76 through lever arm 82.
  • An intake manifold 84 provides the necessary access for the combustion mixture to intake port 70 and a similar exhaust manifold 86 connected to exhaust port 72 provides for the necessary discharge of exhaust gases following combustion.
  • the rotary engine shown in the drawings, consists of five vanes 60 and five workingchambers with the necessary intake, exhaust and ignition means for each chamber, it can be readily understood by those skilled in the artthat any number of working chambers can be provided without departing from the scope of this invention.
  • the rotary engine has at least three vanes to provide at least three working chambers and, as more fully described below, it is preferred to use an odd number of working chambers.
  • the rotary engine of this invention will now be described as it relates to a typical four-cycle gasoline engine operation of combustion, exhaust, intake and compression. But, it should be understood that the invention'can also be used in a twocycle mode without departing from the scope of the invention.
  • FIG. 3 shows the beginning of the power stroke after firing of the explosive charge in working chamber A. At firing, the intake and exhaust ports are closed.
  • FIG. 4 shows the continuing power stroke and the resulting clockwise rotation of eccentric 54 and power shaft 50.
  • FIG. 5 shows the end of the power stroke of working chamber A and the start of the exhaust stroke in which the exhaust port is open and the intake port is closed.
  • FIG. 6 shows the continuing exhaust stroke, and by the time the rotor reaches the position shown in FIG. 7, exhaust is nearly complete. The exhaust port then closes, and the intake port opens so that when the rotor 4 reaches the position shown in FIG. 8 the intake of a combustible mixture into chamber A has begun.
  • FIG. 9 shows continuing intake of combustible mixture
  • FIG. 10 shows the completion of the intake stroke at which point the intake port closes and the compression stroke on the combustible mixture in working chamber A begins.
  • the stator can conveniently be made from a bored cast iron or aluminum block with end walls covering both ends.
  • the rotor can be a hollow metal cylinder of the appropriate diameter.
  • the power shaft can be a solid rod.
  • the eccentric may take many forms, but preferably it will not occupy the entire space defined by the inner surface of the rotor, but will leave more than half that space open. By having a substantial amount of the space defined by the inner surface of the rotor open, it is possible to pass a cooling fluid or gas through the center of the rotor to achieve extremely effective engine cooling, because the outer surface of the rotor forms portions of the working chambers of the engine.
  • the eccentric will also be designed in a shape whereby the bulk of its weight is located on the side of the rotor that is farthest from the inner wall of the stator and closest to the stator axis so that this imbalance of weight in the design of the eccentric can serve to counterbalance the eccentricity of the path that is followed by the rotor and eccentric about the stator axis.
  • the eccentric be mounted within the inner surface of the rotor in a manner whereby the eccentric is in rolling contact with the inner surface of the rotor.
  • the eccentric may contact the inner surface of the rotor at one or more points but at each of these points, the eccentric should be in rolling contact with the inner surface of the rotor.
  • Roller bearings mounted on the eccentric can serve to provide such rolling contact.
  • the vanes themselves can be made from simple machined flat pieces of metal, and the operating end or sealing end of the vanes can be notched or cut back to fit over the outer surface of the rotor and yet extend towards the center of the engine past the outer surface of the rotor in the portion of the vanes that is carried in slots in the end walls of the stator.
  • This overhang or extension of the sealing vanes past the outer surface of the rotor within the end walls of the stator enhances the sealing effectiveness of the vanes in sealing adjacent chambers of the engine at the end walls.
  • Valves, spark plugs, cams, and carburetors for the engine may all be selected from a wide variety of such devices that are conventional and readily available.
  • An outstanding feature of the rotary engine of this invention is the large cubic inch displacement that can be obtained with a relatively small engine.
  • a rotary engine having a stator with an internal radius of 2.5 inches, a rotor having an external radius of 1.875 inches, and a width of 2 inches would have a cubic inch displacement of about 28 cubic inches.
  • This very small engine would generate about 30 horsepower at 4000-6000 r.p.m.
  • the engine can be designed so that some of its chambers are used for cooling only.
  • alternating chambers can have a continuous flow of air passing through the chamber. This helps to cool the engine, and at least part of the heated cooling air can then be conveniently used in the combustion mixture.
  • the vanes may be biased against the rotor by spring action, pneumatic force, or any other force.
  • pneumatic pressure is at least partially used to bias the vanes against the rotor. This pneumatic action causes greater pressure on the vanes against the rotor in the power and compression cycles and less pressure on the vanes in the intake and exhaust cycles.
  • the vanes divide sections of the engine into chambers. There must be at least two vanes, but three or more vanes are preferred, and there is no theoretical 6 upper limit to the number of vanes that can be used with the rotary engine of this invention.
  • combustion chambers Although an even number of combustion chambers can be used, the use of an odd number of combustion chambers is preferred, because a full cycle on two revolutions of the rotor is obtained with an odd number of chambers. If an even number of combustion chambers is used, the timing and chamber firing sequence is more complex.
  • the compression ratios of the engine are a function of the spacing between the vanes.
  • the narrower the spacing between the vanes the higher the compression ratios that are possible.
  • higher compression ratios are desired narrower spacings can be used.
  • the chamber directly following this combustion chamber can be a relatively broad chamber with a continuous flow of air for cooling.
  • the relative diameters of the inside of the stator and the outside of the rotor are also important. In the broad concept of the invention any inside diameter of the stator can be used.
  • the outside diameter of the rotor is, however, limited by the inside diameter of the stator, but the outside diameter of the rotor can be almost as large as the inside diameter of the stator.
  • the minimum outside diameter of the rotor is limited to a value slightly larger than the inside radius of the stator.
  • the outside diameter of the rotor is at least about percent and more preferably from about to about of the inside diameter of the stator.
  • the relative diameters of the rotor and the inner surface of the stator have a direct bearing upon the compression ratios that can be obtained.
  • the compression ratio increases as the difference between the diameter of the rotor and the diameter of the inner surface of the stator decreases.
  • the eccentric is mounted on the power shaft (which is concentric with the stator axis); and is contained within the space defined by the inner surface of the rotor.
  • the eccentric must be of such a size and shape that it allows the rotor to roll around or near the circumference of the inner surface of the stator. As the rotor rolls around the inner surface of the stator, the eccentric rolls on the inner surface of the rotor at the points of contact between the inner surface of the rotor and the rollers or low-friction bearings on the eccentric.
  • the eccentric may have a wide variety of designs.
  • the eccentric is depicted as a solid circular disc with a roller bearing around the outside of the entire disc.
  • the eccentric could also be a narrow extended arm having rolling contact with the inner surface of the rotor adjacent the portion of the rotor that is closest to the inner surface of the stator with a counterweight portion on the other side of the stator axis.
  • the counter-weight portion also preferably is in rolling contact with the inner surface of the rotor.
  • Various other shapes could also be devised to provide for counter-balancing the eccentric.
  • the rotary engine of the present invention has many attributes that make it an extremely useful power source.
  • rotary engine One of the important features of the rotary engine is its ease of construction. All major parts of the present engine can easily be made on conventional lathes and boring and milling machines. Moreover, the simplicity of the rotor design makes side sealing of the rotor easy to accomplish. No gears are required to transfer the energy to the power shaft or to ensure that the engine remains in phase, as is required in the well-known Wankel rotary engine. In the present design, the engine power shaft is directly driven by the eccentric.
  • combustion can take place at any portion of the inner surface of the cylindrical cavity of the stator.
  • the heat generated is distributed evenly throughout the engine and thermal distortions can be minimized.
  • Another important advantage of the present rotary engine is that the power shaft rotates once per revolution of the rotor.
  • the engine is capable of operating at very high rotor revolutions per minute. This characteristic is important, because high revolutions per minute of the rotor are required for maximum power output.
  • Engines that have high shaft revolutions per revolution of the rotor, such as the Wankel engine which has three shaft revolutions per rotor revolution, require special and expensive gearing to permit practical power take off from the shaft.
  • the number of firings per rotor revolution isdependent upon the number of combustion chambers.
  • the number of firings per revolution of the rotor are half the number of combustion chambers.
  • all combustion chambers will fire.
  • Most convenient for purposes of firing design are those versions of this invention in which the engine has an odd number of chambersfWith an odd number of chambers, the firing sequence is repeated every two revolutions. Whereas, with an even number of revolutions, it may be necessary to skip or omit certain firings.
  • the engine can operate at very high compression ratios, which can be as high as the diesel range. Many other rotary engines cannot directly obtain such high compression ratios.
  • the compression ratio is mainly dependent upon the relative outside diameter of the rotor in comparison to the internal diameter of the stator, and upon the spacing between vanes.
  • One of the most distinctive advantageous features of the present invention is the manner in which the rotary engine is separated into combustion chambers.
  • Most engines containing vanes rely on a seal that is in sliding engagement with the outer surface of the rotor or the inner surface of the stator.
  • the rotor rolls over the sealing vane at the position of full retraction of the vane into the stator. At this position, there is little or no sliding motion between the vane and the rotor.
  • a rotary engine comprising:
  • stator having spaced end walls and a peripheral wall interconnecting the end walls to form a cylindrical cavity having an axis, the inner surface of the peripheral wall having a substantially circular profile;
  • a hollow cylindrical rotor having an outer and inner surface, eachhaving a substantially circular profile, and supported in the cavity for rolling motion with respect to the inner surface of the stator about an axis spaced from but parallel to the stator axis;
  • the rotor having an internal diameter such that the stator axis is located inside the inner surface of the rotor and an external diameter that is less than the diameter of the inner surface of the stator;
  • an eccentric mounted within the inner surface of the rotor for rotation about the stator axis and having bearing means located on the periphery of the eccentric which are in rolling contact with the inner surface of the rotor, whereby in operation the rotor axis described a substantially circular path around the stator axis;
  • stator a plurality of spaced vanes mounted in the stator in sealing relationship with the end walls for reciprocal movement with respect to the inner surface of the stator;
  • At least two chambers are defined by adjacent vanes, the outer surface of the rotor, the inner surface of the stator, and the end walls of the stator;
  • the stator having an intake port for admitting fuel to the working chamber and an exhaust port for discharging exhaustproducts from such chamber.
  • the rotary engine defined in claim 1 which has ignition means for igniting fuel in each working chamber.
  • the rotary engine defined in claim 1 including means in the end walls for guiding and supporting the vanes.
  • the rotary engine defined in claim 13 including a power shaft mounted to the eccentric along the stator axis.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)
US342940A 1973-03-20 1973-03-20 Rotary engine Expired - Lifetime US3919980A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US342940A US3919980A (en) 1973-03-20 1973-03-20 Rotary engine
BE160137A BE833528A (fr) 1973-03-20 1975-09-17 Moteur rotatif

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US342940A US3919980A (en) 1973-03-20 1973-03-20 Rotary engine

Publications (1)

Publication Number Publication Date
US3919980A true US3919980A (en) 1975-11-18

Family

ID=23343951

Family Applications (1)

Application Number Title Priority Date Filing Date
US342940A Expired - Lifetime US3919980A (en) 1973-03-20 1973-03-20 Rotary engine

Country Status (2)

Country Link
US (1) US3919980A (fr)
BE (1) BE833528A (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4021160A (en) * 1975-06-09 1977-05-03 Vukasin Todorovic Orbital motor
US4079083A (en) * 1975-02-03 1978-03-14 Ciba-Geigy Corporation Vane type orbital engine
US4219315A (en) * 1977-05-26 1980-08-26 Sarich Tony R Sealing member for orbital or rotary motors
WO1998022696A1 (fr) * 1996-11-22 1998-05-28 Sanchez, Santiago Un type de machines a pistons rotatifs
CN1091834C (zh) * 1998-09-10 2002-10-02 陈骏 一种滚动转子式动力机
US6481988B2 (en) * 2000-03-31 2002-11-19 Otice Establishment Internal combustion engine
US20070215094A1 (en) * 2006-03-06 2007-09-20 Sumiyuki Nagata Nagata cycle rotary engine
US20110083637A1 (en) * 2009-10-08 2011-04-14 Blount David H Rotary double engine
CN107587936A (zh) * 2017-10-19 2018-01-16 狄庆会 偏心转子发动机及其燃烧做功方法

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US822700A (en) * 1905-06-21 1906-06-05 Watson Birdsall Rulon Rotary engine.
US1575860A (en) * 1922-04-05 1926-03-09 Travis B Monk Internal-combustion engine
US1996620A (en) * 1931-10-19 1935-04-02 Herman Reis Tightening means for the compression and suction chambers of rotary piston engines
US2005141A (en) * 1933-01-16 1935-06-18 Ivan J Amo Internal combustion engine
US2015027A (en) * 1933-07-26 1935-09-17 Roy T Quick Jr Rotary engine
US3220388A (en) * 1963-06-21 1965-11-30 Dwight M Brown Rotary internal combustion engine
US3316887A (en) * 1965-05-24 1967-05-02 William M Melvin Rotary engine
US3539280A (en) * 1968-02-07 1970-11-10 Alfredo Ravera Endothermic rotary engine with shiftable blades
US3809024A (en) * 1972-08-14 1974-05-07 H Abbey Four-stroke and two-stroke rotary internal combustion engine

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US822700A (en) * 1905-06-21 1906-06-05 Watson Birdsall Rulon Rotary engine.
US1575860A (en) * 1922-04-05 1926-03-09 Travis B Monk Internal-combustion engine
US1996620A (en) * 1931-10-19 1935-04-02 Herman Reis Tightening means for the compression and suction chambers of rotary piston engines
US2005141A (en) * 1933-01-16 1935-06-18 Ivan J Amo Internal combustion engine
US2015027A (en) * 1933-07-26 1935-09-17 Roy T Quick Jr Rotary engine
US3220388A (en) * 1963-06-21 1965-11-30 Dwight M Brown Rotary internal combustion engine
US3316887A (en) * 1965-05-24 1967-05-02 William M Melvin Rotary engine
US3539280A (en) * 1968-02-07 1970-11-10 Alfredo Ravera Endothermic rotary engine with shiftable blades
US3809024A (en) * 1972-08-14 1974-05-07 H Abbey Four-stroke and two-stroke rotary internal combustion engine

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4079083A (en) * 1975-02-03 1978-03-14 Ciba-Geigy Corporation Vane type orbital engine
US4021160A (en) * 1975-06-09 1977-05-03 Vukasin Todorovic Orbital motor
US4219315A (en) * 1977-05-26 1980-08-26 Sarich Tony R Sealing member for orbital or rotary motors
WO1998022696A1 (fr) * 1996-11-22 1998-05-28 Sanchez, Santiago Un type de machines a pistons rotatifs
CN1091834C (zh) * 1998-09-10 2002-10-02 陈骏 一种滚动转子式动力机
US6481988B2 (en) * 2000-03-31 2002-11-19 Otice Establishment Internal combustion engine
US20070215094A1 (en) * 2006-03-06 2007-09-20 Sumiyuki Nagata Nagata cycle rotary engine
US7757658B2 (en) * 2006-03-06 2010-07-20 Sumiyuki Nagata Nagata cycle rotary engine
US20110083637A1 (en) * 2009-10-08 2011-04-14 Blount David H Rotary double engine
CN107587936A (zh) * 2017-10-19 2018-01-16 狄庆会 偏心转子发动机及其燃烧做功方法
WO2019076148A1 (fr) * 2017-10-19 2019-04-25 狄庆会 Moteur à rotor excentré et son procédé de combustion et de fonctionnement
CN107587936B (zh) * 2017-10-19 2024-04-26 狄庆会 偏心转子发动机及其燃烧做功方法

Also Published As

Publication number Publication date
BE833528A (fr) 1976-01-16

Similar Documents

Publication Publication Date Title
US4004556A (en) Rotary internal combustion engine of axially sliding vane type
US4334506A (en) Reciprocating rotary engine
US4072132A (en) Rotary internal combustion engine
US4203410A (en) Method for operating a rotary engine
US2158532A (en) Complementary rotary engine
US4033299A (en) Rotary engine
US3919980A (en) Rotary engine
US4170213A (en) Rotary engine
US3968776A (en) Rotary crankless machine
US3807368A (en) Rotary piston machine
US3902465A (en) Rotary engine
US4316439A (en) Rotary engine with internal or external pressure cycle
US3132632A (en) Rotary engine
US4422419A (en) Rotary internal combustion engine
GB1565669A (en) Reciprocating rotary combustion engines
EP0734486B1 (fr) Moteur rotatif
US3299867A (en) Vane type internal combustion engines
JPS5914612B2 (ja) ロ−タリ−エンジン
US7673595B2 (en) Rotor-piston internal combustion engine
US3801237A (en) Rotary engine or pump
US3765379A (en) Rotary type power plant
US4009690A (en) Rotary internal combustion engine
US3818886A (en) Rotary internal combustion engine
US3529909A (en) Rotary engine
US3858559A (en) Coupled vane rotary fluid device