EP0310549A1 - Drehkolben-Brennkraftmaschine - Google Patents

Drehkolben-Brennkraftmaschine Download PDF

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Publication number
EP0310549A1
EP0310549A1 EP88810635A EP88810635A EP0310549A1 EP 0310549 A1 EP0310549 A1 EP 0310549A1 EP 88810635 A EP88810635 A EP 88810635A EP 88810635 A EP88810635 A EP 88810635A EP 0310549 A1 EP0310549 A1 EP 0310549A1
Authority
EP
European Patent Office
Prior art keywords
rotor
gear
gears
apex
maincrankshaft
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.)
Withdrawn
Application number
EP88810635A
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English (en)
French (fr)
Inventor
Sofyan Adiwinata
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.)
Individual
Original Assignee
Individual
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
Priority claimed from EP87201763A external-priority patent/EP0307515A1/de
Application filed by Individual filed Critical Individual
Publication of EP0310549A1 publication Critical patent/EP0310549A1/de
Withdrawn legal-status Critical Current

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    • 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
    • F01C1/22—Rotary-piston machines or engines of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth- equivalents than the outer member
    • 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
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/02—Arrangements for drive of co-operating members, e.g. for rotary piston and casing of toothed-gearing type
    • 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
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • THIS INVENTION relates broadly to the art of ROTARY MECHANISM and more particularly relates to the art of ROTARY INTERNAL COMBUSTION ENGINE, including all types of vehicles and equipments or apparatus provided with Rotary Internal Combustion Engines, and or Rotary Equipments/Machines such as Rotary Compressors, Rotary Pumps, Rotary Cutting Tools, or lathes as well as Rotary System for Aircraft Engines, or any future flying crafts, using any kind of fuels suitable for such Rotary Internal Combustion Engines, either for land, sea or air transportations, and for any other special purposes as broad as possible, which hereinafter for the purpose of simplicity will be referred to as ROTARY ENGINE.
  • Rotary engines of the above mentioned type is comprises of an outer compo­nent having axially spaced end walls and a peripheral curved or parallel to the axis and an inner component having axially spaced end surfaces and a peripheral cur­ved or parallel to the axis, which components hereafter for simplicity will be - referred to as the Housing and the Rotor, in which Housing defines a cavity in the shape of epicyclic for 2 apex Rotor or in the shape of 2 lobed epitrocho­idal cavity Housing for the 3 apex Rotor.
  • an internal ring gear is fixed or secured within one side of the Ro­tor and intermeshed to a Pinion gear having a hollow shaft for free wheeling within the said maincrankshaft.
  • the gearing ratio of the internal ring gear : Pinion gear is fixed 3 : 2 for which thereafter the Pinion has to be fixed or secured to Housing frame.
  • Rotor with flat outer surface or flat Rotor will cause what so called “Corner seal leakage” which is considered as one of the most serious problem to be solved due to its geometrical conditions.
  • the object of the present inventions are to provide new system for eliminat­ing all said above low performances by such using larger Pinion gear, to allow larger diameter size of maincrankshaft, rotating the said Pinion gear to allow direct power transmit to the maincranksfat and therefore avoiding the exces­sive wear along the contact lines between the Rotor and the cavity wall and using the radially curved apex Rotor portions as well as radially arcaded Hou­sing cavity wall, between which will be inserted suitable sealing elements which able to eliminate the corner sealing problems as it may available in the conven­tional models.
  • the arms of the planetary gear system or epi­ cyclic gears train will be constructed integral to the Pinion gear so therefore the planetary gears system is able to control the speed ratio of the said above Rotor and the maincrankshaft to 1 : 2 for 2 apex Rotor with an epicyclic Hous­ing cavity and 1 : 3 for 3 apex Rotor with 2 lobed epitrochoid Housing cavity.
  • the Pinion gear is fixed and secu­red to the Housing frame and therefore the Pinion will always stay at its sta­tionary position
  • the Pinion will rotate or rotated according to intercorelation speed among the gears, and therefore will be able to prevent any possibilities that a strong dynamic force during any extreme conditions - may cause the Rotor to press the cavity wall in order to transmit the power - to the maincrankshaft of the engine, which of course will cause the wearing.
  • Such ring gear as mentioned above for the 2 apex Rotor will be constructed to a gearing ratio of 3 : 2 with its intermeshing Pinion gear, and for the 3 apex Ro­tor will be constructed to a gearing ratio of 4 : 3 with its intermeshing Pinion gear, which based on said above gearing ratio thereafter it is possible to use a larger size of maincrankshaft diameter for better and stronger performances. Based on the above mentioned constructions, it is therefore made possible to - use when necessary such i.e.
  • a radially curved apex Rotor portion which shape extends continuously from one to adjacent apex and which curve shape become minimum in the middle of said 2 adjacent apex
  • Such radially curved apex Rotor shape is not necessary if such construction is used for compressors, pumps, cutting tools, etc.
  • the invention contemplates the chromeplated inner radially arcaded Housing cavity wall as well as for the sealing rings, for the purpose to obtain the smooth and hard chromed surfaces which has a good affinity for lubricating oil and reduce the sealing ring wearing rate significantly.
  • the present invention has a further object to provide that either curved or flat Rotor instead of construct it to have 3 apex with 3 lobed outer surfaces, it is now constructed to have still 3 apex but with 6 lobed of outer surfaces, which construction will enable the said 3 apex Rotor to fully wipe out completely the remaining volume of compressed fluid or gases into the outlet passage within the Housing cavity which thereafter the same out­er surfaces will receive a new volume of fluid or gases from the inlet passage adjacent to the mentioned above outlet passage, to be brought forward into the suction chamber and compression chamber respectively.
  • the invention contemplates that the same channel as previously described will be constructed between each 2 adjacent apex for the purpose of adjusting the com­pression ratio as it may required by manufacturer, which channel of course will still cause the remaining burned gases brought forward and mixed it further with the new inserted air-fuel through adjacent inlet passage.
  • the said planetary gears system or epicyclic gears train are normally consisted of 3 different gears such as the sun, the planet and the static outer ring gear.
  • the sun gear is the gear in the centre part of the system, while the planet is the intermeshed gear between the static ring gear and the said sun gear, and rotates to the opposite direction with the maincrankshaft and therefore enable the arm of the planet gears to rotate in the same direction with the maincrankshaft.
  • the invention contemplates that the arm of the - ­planet gears will be constructed integral with the Pinion gear which is intermesh­ed to the internal ring gear fixed within one side of the Rotor, while the sun gear will be fixed or secured to the maincrankshaft i.e.
  • the suitable planetary gears system or epicyclic gears train will be constructed so as the sun, the planet and the static outer ring gear will be fixed according to the gearing ratio of 1 : 1 : 8, so therefore the arm of the pla­net gears will be rotated or rotates to 40° per 360° maincrankshaft rotation.
  • gear assembly consisted of 2 integrated smaller and larger gears, which the smaller is intermeshed to the ring gear based on ratio of 1 : 4, and the larger intermeshed to sun gear to the ratio of 1 : 2.
  • the arm of the planet gears will be rotated or rotates to 40° per each 360° revolution of the maincrankshaft.
  • Kinematically only one intermeshing gear is required as the planet gear, but by using three gears, there will be more balance available and the loads can be equally divided among the gears and therefore will make possible the - ­utilization of smaller or thinner gears used for the system.
  • the planetary gears system or epicyclic gears train as mentioned above has more advantages compared to the intermeshing gears, particular­ly such as stable rotations, centering accuracy, simple constructions, etc.
  • the Housing cavity construction will be made in 2 or more parts either crossing or paral­lel to the axis shaft dependent to the variation as it may necessary provided with proper gasket or rubber or any other suitable sealing as to prevent any possibilities of compression leakage, cooling water leakage as well as any lub­ricating oil leakage from one into another working chambers.
  • the invention contemplates that - ­in order to obtain the correct and precision shape as to the same of the out­er envelope of the Rotor based on speed ration of 1 : 3 to the maincrankshaft for the 3 apex Rotor, or speed ratio 1 : 2 to the maincrankshaft for the 2 -­apex Rotor, including the permissible or allowed clearance as will be deter­mined by the manufacturer, therefore, a special cutting tool which is construc­ted based on the same principles of the engine but provided with accurate -­size of cutting blade fixed or secured to the said above tools, will be used to cut and form the inner Housing cavity precisely. Such cutting tools should be constructed also based on the same eccentricity of the engine.
  • the invention has further particular objects to provide the engines with the same gearing principles such as the gears for internal ring gear, the pinion, the intermeshing gears train as well as the planetary gears system or epicyclic gears train, but to be based on different gearing ratio, which will be determined or as resulted from the computation of the formula described in our previously submitted applications (European Patent applications No. 87.201780.1 and U.S. Patent application Serial No. 098 189) as follows: in which: I.I.G.P. refers to the pitch diameter of the internal involute gear pinion. I.I.G. refers to the pitch diameter of the internal involute gear.
  • a/b designates the additional rotation of the internal involute gear on each rotation of the maincrankshaft
  • p designates the basic ratio of the specific type of rotary engine, being 1/2 for the rotary engine using 2 apex Rotor and epicyclic Housing ca­vity, and 2/3 for the rotary engine using 3 apex Rotor and 2 lobed - ­epitrochoid Housing cavity.
  • a rotary internal combustion engine is provided with 2 units Rotor of the radially curved 2 apex 21 having curved Housing cavity 20 which rotors will be mounted to each of the eccentric hubshaft 23 made and constructed integral with the maincrank­shaft 24, to have free wheeling by means of metal bearings between the ro­tor and the eccentric hubshaft 22 and between the maincrankshaft and the Housing frame 25.
  • the Rotor will be provided with side seal elements 27 which is connected with the apex seal elements 28 and lubricating oil scraper rings 26 & 29.
  • the curved Housing cavity is provided with inlet and outlet passages 30 which is controlled by means of valves 31 supported by coil springs 32 and which valves will be driven by means of camshaft 36 and rocker arms 33 and con­necting rods 34.
  • the engine is also provided with ignitions by means of spark plugs 35 which is fixed or secured to the Hosuing frame 20 and which Housing frame has a supporting main body which is also to function as the lub-oil tank 39.
  • the Housing frame will also be provided with cooling water passages 40 as conventionally constructed.
  • Rotor 21 Within one side of the Rotor 21 will be fixed or secured an internal ring gear 37 which will be intermeshed to a pinion gear 38 to be based on gearing ratio of 3 : 2, and made or constructed in an integral cluster gears assembly with gear 47 having a hollow shaft for free wheeling around the maincrankshaft 24 by means of roller bearings 41.
  • the gear 47 is intermeshed with a gear 51 which is made or constructed in another cluster gears assembly with the gear 52 having a separate shaft 42.
  • the gearing ratio between gear 47 and 51 is fixed at 2 : 1.
  • the gear 52 is intermeshed to a final pinion gear 48 which is fixed or secured to the maincrankshaft 24 by means of involute spline and strengthen by means of special locknut 49, and the gears 52 and 48 is fixed on gearing ratio 2 : 1.
  • the cluster gears assembly shaft 42 will be provided with bearing 43 which end of the shaft will be mounted to the Housing frame 20 and gear cover 50. Both ends of the maincrankshaft 24 will be mounted with ball bearings 44 and lub-oil seal 46 and seal cover 45 to prevent any lub oil leakage out of engine.
  • the Housing cavity of an epicyclic form 20, and the permanent or cons­tant clearance between the Rotor apex 21 and the Housing cavity 20 is therefore made possible by such constructions.
  • Figure 4 is showing the exact position of each Rotor as drawn in the Figure 1 & 2, at the same time and at the eccentric hubshaft distance of 180° bet­ween each other.
  • the Housing cavity of the rear part will be constructed higher than the front part due to the given eccentricity.
  • Figure 5 & 6 are showing the planetary gears system or epicyclic gears train used for the same radially curved 2 apex Rotor 21 with radially arcaded Hous­ing cavity 20.
  • the sun gear 348 which is fixed or secured to the maincrank­shaft 324, is intermeshed to 3 units of planet gears 362 which are mounted to the armshaft 361 for free wheeling, based on gearing ratio of 1 : 1.
  • the 3 units of planet gears 362 are also intermeshed to the outer ring gear of 359 based on gearing ratio of 1 : 3.
  • Figure 7 is a rotary compressor based on the invention principles and de­signed for car air conditioning system to the actual size of 1 : 1 to show how small and effective is the invention for such particular purpose.
  • Such compressor is constructed to have 2 apex Rotor 421 with flat outer surfaces provided with proper sealing elements 427, within which the same material will be constructed an integral internal ring gear 437 and inter­meshed to the pinion gear 438, based on gearing ratio of 2 : 3.
  • Rotor 421 will be mounted to the eccentric hubshaft made in one integrated with the maincrankshaft 424, for free wheeling through roller bearing installed in between, 422.
  • the pinion gear 438 is made integral with the arm of the planet gears 460 which is constructed to hold the armshaft 461 where the planet gears 462 will free wheeling around.
  • the sun gear is fixed or secured to the maincrankshaft by means of involute spline and intermeshed to the 3 unit of planet gears based on gearing ratio of 1 : 1.
  • the 3 units of planet gears are also intermeshed to the outer ring gear 459 which is fixed and secured to the Housing frame.
  • the arm will be rotated or rotates to 90° per each revolution of the maincrankshaft 424 which means will rotate the Rotor to 60° as it may required for additional rotation per each revolution of the maincrankshaft in order to obtain speed ratio of 1 : 2.
  • the maincrnakshaft 424 is also provided with lubricating oil holes through the centre 453 for sufficient lubrication of the roller bearing 441 which is installed within the hollow shaft of the pinion gear 438, and also to lubricate the rotating seal assembly consisted of a coil spring 457 and carbon seal 446/C and stationary seal seat and rubber gasket 458, and retaining ring 459. Both sides of the maincrankshaft 424 will be firmly mounted to the front -­ball bearing 444/F and rear ball bearing 444/R to have a snap ring 459 and closed by end cover 445 after given with sufficient special lub-oil. In front part, the balance counterweight 464 is fixed and secured to the main­crankshaft 424 by means of locknut 449.
  • the cylindrical roller bearing is fixed and secured to the Housing frame by means of special locknut 460, while the clutch assembly is fixed and secured to the maincrankshaft 424 by means fof front hexagonal nut 465.
  • the compressor will also be provided with schrader 454 and within the inside part is installed a cylindrical plate valve 463.
  • Figure 8 is showing a special cutting tool made for the purpose to cut or to shape precisely the radially arcade Housing cavity or flat inner surface either for 2 apex Rotor or 3 apex Rotor.
  • Such equipment will consist of the same shape of the Rotor 221 provided with cutting blade 254 which is fixed or secured by means of bolt and nut 255, which Rotor 221 is mounted to the eccentric hub­shaft 223 made in one and integrated with the maincrankshaft 224, and rotated to the speed ratio of 1 : 2 for the 2 apex Rotor or speed ratio of 1 : 3 for the 3 apex Rotor, by means of intermeshing gears as previously described 237 & 238, 247 & 251, 252 & 248, in such a way in accordance to each gear­ing ratio as it may required for each type of engine.
  • maincrankshaft 224 will be hold by 2 ball bearings 244 which in the front part will be connected to the pinion locknut 249 and at the rear will be closed by any hex nut.
  • a pulley 253 will be installed in between the both bearings and fixed to the maincrankshaft 224 by means of inserted key 256
  • the ball bearing is positioned to the both side of the main frame 257 which is also constructed to accomodate the separate hubshaft of the cluster gears as­sembly 242 of the one side while for the other side will be supported by a spe­cial separate stand 258 which is fixed or secured to the mainframe by means of bolt and nuts.
  • Figure 9 & 10 are the drawings of the planetary gears system applied to the rotary engine having curved 3 apex Rotor 21 and 2 lobed curved epitrochoid Housing cavity 20, which planet gears according to this invention will be cons­tructed in a cluster gears assembly consisted of a smaller gear 362/I and lar­ger gear 362/II, which will be intermeshed to the sun gear 348 as well as to the outer ring gear 359 to be based on gearing ratio between gear 348 & 362/II fixed at 1 : 2 and between gear 362/I & ring gear 359 fixed at 1 : 4.
  • the said sun gear is fixed to the maincrankshaft by means of involute spline and strengthen by means of special locknut 349.
  • Figure 11 & 12 are the drawing of the typical rotary engine having 3 apex Rotor with 6 lobed outer surfaces and 2 lobed epitrochoid Housing cavity, and the Rotor is fixed at speed ratio of 1 : 3 with the maincrankshaft which motion can be seen from the Figure 11.
  • Figure 13 & 14 are perspective drawing of the Rotor provided with intermesh­ing gears in accordance to the invention and the exact position of the apex Ro­tor at a speed ratio of 1 : 3.
  • this typical design has a shorter eccentricity as well as shorter horizontal lenth of line c4 - b2 as shown in the Figure 13.
  • Figure 15 is a perspective drawing of the whole concept of the invention based on silhouetted broken away view to show the Rotor, 121 radial apex seal 128 curved Housing 120, side seal elements 127, internal ring gear 137, pinion gear 138, the intermeshing gears 147, 148, 151 & 152, the maincrankshaft 124 and eccentric hubshaft 123, flywheel 164, inlet passage 166, outlet passage 165 and lub oil tank 195, oil filter 190, cooling fan 180, electric generator 170, etc.
  • Figure 16 a,b,c & d are showing the kinematic of the preferred embodiment of the invention, in which rotary engine, an I.I.G./Internal Involute Gear (400) is fixed to the Rotor (200) and intermeshed to an I.I.G.P./Internal Involute Gear Pinion (500) having a hollow shaft, through which a M.C.S./Maincrankshaft (100) including its integral E.H./Eccentric Hub Shaft (150) will rotates freely.
  • I.I.G./Internal Involute Gear (400) is fixed to the Rotor (200) and intermeshed to an I.I.G.P./Internal Involute Gear Pinion (500) having a hollow shaft, through which a M.C.S./Maincrankshaft (100) including its integral E.H./Eccentric Hub Shaft (150) will rotates freely.
  • the I.I.G.P. (500) is fixed or secured to its Housing frame as con­ventionally constructed.
  • the contact points of the both pitch circles are consisted of point C which be­long the the pitch circle of I.I.G. (400) and point P which belong to the pitch cir­cle of I.I.G.P. (500).
  • the invention is also applicable to any other rotary type such as 2 apex Rotor or 4 apex Rotor, which for the purpose of simplicity the basic ratio for the specific type of rotary (such as 1/2 for 2 apex Rotor, 2/3 for 3 apex Rotor and 3/4 for 4 apex Rotor), hereinafter will be designated or referred to as p respectively, as can be seen from the formula of this invention.
  • the intermeshing gears which are installed between the Rotor (200)/I.I.G.(400) and the M.C.S. (100) will cause the I.I.G.P. (100) to rotate in the same direction in order to be able the point of C ⁇ to reach the position of the point C ⁇ based on speed ratio of 1 : 2 for 2 apex Rotor, or 1 : 3 for 3 apex Rotor or 3 : 4 for 4 apex Rotor.
  • the I.I.G.P. (500) is constructed in one hollow shaft with one of the intermeshing gear through which it will be rotated or rotates according to its proper speed ratio.
  • Such fractional figure of 1/9 can be easily splitted into 1/3 x 1/3 which means that the further intermeshing gears between the I.I.G.P.(500) and M.C.S.(100) is fixed to gearing ratio of 1 : 3 and 1 : 3 respectively. (minimum gears for space efficiency).
  • the diameter of the M.C.S. (100) can be constructed larger than the conventional model.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Retarders (AREA)
EP88810635A 1987-09-17 1988-09-16 Drehkolben-Brennkraftmaschine Withdrawn EP0310549A1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
EP87201763 1987-09-17
EP87201763A EP0307515A1 (de) 1987-09-17 1987-09-17 Drehkolben-Brennkraftmaschine
US23968888A 1988-09-02 1988-09-02
US239688 1988-09-02

Publications (1)

Publication Number Publication Date
EP0310549A1 true EP0310549A1 (de) 1989-04-05

Family

ID=26109319

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88810635A Withdrawn EP0310549A1 (de) 1987-09-17 1988-09-16 Drehkolben-Brennkraftmaschine

Country Status (3)

Country Link
EP (1) EP0310549A1 (de)
JP (1) JPH01163402A (de)
AU (1) AU2234188A (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2404960A (en) * 2003-08-12 2005-02-16 Raytheon Co Wire-wound leadscrew assembly
US10001123B2 (en) 2015-05-29 2018-06-19 Sten Kreuger Fluid pressure changing device
GB2557946A (en) * 2016-12-19 2018-07-04 Pattakos Manousos Rotary engine
CN108757166A (zh) * 2018-06-12 2018-11-06 杜三平 一种四冲程转子发动机
DE102018005332A1 (de) 2018-06-27 2020-01-02 Bernd Süss Rotationskolbenmotor
US11035364B2 (en) 2015-05-29 2021-06-15 Sten Kreuger Pressure changing device

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1194636B (de) * 1962-03-24 1965-06-10 Beteiligungs & Patentverw Gmbh Kreiskolbenmaschine
US3244155A (en) * 1965-05-28 1966-04-05 Laudet Pierre Rotary engine with two concentric rotors
DE2853930A1 (de) * 1978-12-14 1980-06-19 Karl Dipl Ing Otto Rotationskolbenmaschine in kreisbogenausfuehrung mit kreisbogenfuehrung des rotors
US4308002A (en) * 1979-10-25 1981-12-29 Alfonso Di Stefano Wankel-type engine with semi-circular sectional configuration for chamber end surface
GB2095334A (en) * 1981-03-20 1982-09-29 Trochoid Power Corp Rotary positive-displacement fluidmachines
EP0262721A1 (de) * 1986-09-18 1988-04-06 Sofyan Adiwinata Drehkolbenmaschine mit durch Umlaufräder angetriebenem Rotor und gleichmässig drehender Welle

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1194636B (de) * 1962-03-24 1965-06-10 Beteiligungs & Patentverw Gmbh Kreiskolbenmaschine
US3244155A (en) * 1965-05-28 1966-04-05 Laudet Pierre Rotary engine with two concentric rotors
DE2853930A1 (de) * 1978-12-14 1980-06-19 Karl Dipl Ing Otto Rotationskolbenmaschine in kreisbogenausfuehrung mit kreisbogenfuehrung des rotors
US4308002A (en) * 1979-10-25 1981-12-29 Alfonso Di Stefano Wankel-type engine with semi-circular sectional configuration for chamber end surface
GB2095334A (en) * 1981-03-20 1982-09-29 Trochoid Power Corp Rotary positive-displacement fluidmachines
EP0262721A1 (de) * 1986-09-18 1988-04-06 Sofyan Adiwinata Drehkolbenmaschine mit durch Umlaufräder angetriebenem Rotor und gleichmässig drehender Welle

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2404960A (en) * 2003-08-12 2005-02-16 Raytheon Co Wire-wound leadscrew assembly
US10001123B2 (en) 2015-05-29 2018-06-19 Sten Kreuger Fluid pressure changing device
US10408214B2 (en) 2015-05-29 2019-09-10 Sten Kreuger Fluid pressure changing device
US11035364B2 (en) 2015-05-29 2021-06-15 Sten Kreuger Pressure changing device
GB2557946A (en) * 2016-12-19 2018-07-04 Pattakos Manousos Rotary engine
CN108757166A (zh) * 2018-06-12 2018-11-06 杜三平 一种四冲程转子发动机
DE102018005332A1 (de) 2018-06-27 2020-01-02 Bernd Süss Rotationskolbenmotor

Also Published As

Publication number Publication date
AU2234188A (en) 1989-03-23
JPH01163402A (ja) 1989-06-27

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