WO2003074839A1 - Machine a piston oscillant presentant un mecanisme de soupape rotatif - Google Patents

Machine a piston oscillant presentant un mecanisme de soupape rotatif Download PDF

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Publication number
WO2003074839A1
WO2003074839A1 PCT/BG2003/000004 BG0300004W WO03074839A1 WO 2003074839 A1 WO2003074839 A1 WO 2003074839A1 BG 0300004 W BG0300004 W BG 0300004W WO 03074839 A1 WO03074839 A1 WO 03074839A1
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WO
WIPO (PCT)
Prior art keywords
link
oscillation
axis
pistons
links
Prior art date
Application number
PCT/BG2003/000004
Other languages
English (en)
Inventor
Angel Nedev Nedev
Original Assignee
Dinev, Mitko, Todorov
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 Dinev, Mitko, Todorov filed Critical Dinev, Mitko, Todorov
Priority to AU2003201551A priority Critical patent/AU2003201551A1/en
Publication of WO2003074839A1 publication Critical patent/WO2003074839A1/fr

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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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/008—Driving elements, brakes, couplings, transmissions specially adapted for rotary or oscillating-piston machines or engines
    • 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
    • F01C9/00—Oscillating-piston machines or engines
    • F01C9/002—Oscillating-piston machines or engines the piston oscillating around a fixed axis
    • 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
    • F02B53/04—Charge admission or combustion-gas discharge
    • F02B53/06—Valve control therefor
    • 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
    • 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 invention relates to a module for a piston machine with adjustable pressure in the compressor chamber which finds application in general machine engineering and more particularly in internal combustion engines, hydraulic engines, pneumatic engines, compressors, pumps, clutches and brakes, either independently or in a group interconnected in a definite manner.
  • a certain module for a piston machine known comprises pistons, kinematically connected to crankshafts and a gas distribution mechanism.
  • the pistons are fitted rigidly to a link, which is common for the crankshafts and is kinematically connected to them.
  • Bearing seated gas distributors located in seats of equidistant contours and of channels shaped in every gas distributor, connecting openings of the seats with combustion chambers, and inlet and exhaust pipes are connected to the crankshafts. /1/
  • a disadvantage of the known module of a piston machine are the extreme operation regimes resulting in insufficient reliability due to the lack of connection between the compressor chambers and/or mobile iston.
  • the module for a piston machine with adjustable pressure in the compressor chamber comprises of pistons, kinematically connected to crankshafts and a gas distribution mechanism.
  • the pistons are fitted rigidly to a link which is common for the crankshafts and is kinematically connected to them, and bearing seated gas distributors located in seats of equidistant contours and of channels shaped in every gas distributor, connecting openings of the seats with combustion chambers, inlet and exhaust pipes are connected to the crankshafts.
  • the module comprises one or several link mechanisms. Each of these mechanisms comprise a link with a preset amplitude of oscillation. Link pistons with seals are fitted rigidly to the link.
  • the link pistons are defined by rotation surfaces of generating line coincident with the line describing the projection of the section of the front area of each piston over surfaces perpendicular to the plane of oscillation of the link and containing the axis of the oscillating link with an axis of rotation coincident with the axis of the oscillating link.
  • the center line of the guide of the link stone or roller is straight or curved, and its direction is in a plane perpendicular to the axis of the oscillating link, and crosses or intersects the axis of the oscillating link.
  • the link is kinematically connected to a crankshaft which centre line is in parallel to the axis of the oscillating link.
  • the eccentricity of the crank of the crankshaft, distance and its oriented position toward the axis of the oscillating link is selected in accordance with the amplitude of oscillation of the link by a definite plan of position or a function of the angle of rotation of the crankshaft and angle of deviation of the link.
  • the link mechanism, with link pistons fitted rigidly to the link is accommodated in special cavities in the frame which comprises several rigidly interconnected parts.
  • the cavities represent closed volumes of sectors, formed by rotation surfaces, equidistant to the rotation surfaces, forming the link pistons fitted rigidly to the link, with an axis of rotation coinciding with the axis of the oscillating link.
  • link pistons are located or not located other pistons, formed by rotation surfaces identical with those of the link pistons fitted rigidly to the link, or equidistantly to the rotation surfaces of the cavities in the frame. They are only fitted rigidly to the frame, in combination or only bearing seated pistons on an axis which centre line coincides in combination or is in parallel to the axis of the oscillating link.
  • the mobility of the bearing seated pistons is ensured by an elastic connection with the frame or by a kinematic connection with the crankshaft or the link.
  • the pistons are positioned at distances greater or commensurate with the pre-piston compressor chambers, corresponding to the amplitude of oscillation of the link together with the link pistons fitted rigidly to it.
  • the crankshaft is kinematically connected or not with bearing seated fluid distributors, formed by rotation surfaces equidistant to the rotation surfaces of the seats in the frame where the fluid distributors are located, with an axis of rotation which coincides with the centre line of the bearing resting of the fluid distributors.
  • the direction of the centre line of bearing resting of the fluid distributors is in parallel, in combination or coincides with the centre line of the axis of the oscillating link.
  • the openings between the seats of the fluid distributors and the pre-piston compressor chambers are in rotation surfaces in parallel, perpendicular or in combination with/to the rotation surfaces of the pre-piston compressor chambers and form a connection through channels, specially formed in the fluid distributors, only to adjacent pre-piston compressor chambers, in combination or only at inlet and exhaust pipes with pre-piston compressor chambers at a definite order.
  • These connections can be realized in combination or only with throttles, nozzles or valves connected with elastic connection to the frame or kinematic connection to the crankshaft or link. Their arrangement is determined by the direction of the fluid through the openings of the pre-piston compressor chambers in an order determined by the operational function of the module.
  • the links are kinematically connected to crankshafts which centre lines are in parallel to the axes of oscillating links and one to other so that the size of the eccentricity of their cranks, distance and orientated position with relation to the axes of oscillating links is to a definite plan of position or a function of angle of rotation of the crankshafts and angle of deviation of the links of all link mechanisms at a time, provided that the crankshafts are kinematically interconnected either only by belt transmission, chain, tooth gear, or joint connection, or by a combined connection.
  • the crankshafts are kinematically connected only to one link or more than one link.
  • a certain advantage of this invention is that it will technologically improve duty performance and life of the module for a piston machine with adjustable pressure in the compressor chamber, and when designed as an internal combustion engine it will ensure a better ecological performance with an increase of the time of combustion of the fuel mixture at a constant volume of the combustion chamber, with a duration up to one hundred and fifty degrees from the rotation of the crankshaft.
  • Figure 1 is a transverse section of the module for a piston machine with adjustable pressure in the compressor chamber, embodied as an internal combustion engine (ICE) with a fuel discharge pump in surfaces in parallel to the surface of oscillation of the links.
  • Figure 2 is a longitudinal section of the module for a piston machine on the line B-B of Fig. 1.
  • ICE internal combustion engine
  • Figure 3 is an indicator diagram of the module for a piston machine, embodied as an ICE with the respective positions of the bearing seated fluid distributor.
  • Figure 4 is a transverse section of the module for a piston machine with adjustable pressure in the compressor chamber, embodied as a compressor.
  • Figure 5 is a transverse section of the module for a piston machine with adjustable pressure in the compressor chamber, embodied as a hydro and pneumatic engine.
  • Figure 6 is a transverse section of the module for a piston machine with adjustable pressure in the compressor chamber, embodied as a kinematic connection between two shafts as a clutch or brake.
  • Figure 7 is a transverse section of the module for a piston machine with adjustable pressure in the compressor chamber, embodied as a compressor or a pump.
  • the module for a piston machine with adjustable pressure in the compressor chamber embodied as an internal combustion engine (ICE) with a fuel discharge pump comprises two link mechanisms located at one hundred and eighty degrees one from another - Fig. 1. Any one of the said link mechanisms comprises a link 1 with an amplitude of oscillation of thirty degrees. Pistons 2 with seals 3 are fitted rigidly to each link 1.
  • the link pistons 2 are shaped by rotation surfaces of a rectangle generating line and axis of rotation coinciding with the axis of oscillation 4 which is common for the two links 1.
  • the link 1 is with a guide 5 for a link roller 6 which axis is of direction crossing the axis of oscillation 4 of link 1.
  • the link 1 is kinematically connected to a crankshaft 7 of a centre line in parallel to the axis of oscillation 4 of the link 1.
  • the link mechanisms are located together with the link pistons 2 fitted rigidly to the links 1 in cavities formed in frame 8.
  • the cavities are closed volumes of sectors, formed by rotation surfaces equidistant to the rotation surfaces forming each one of the link pistons 2 with an axis of rotation coinciding with the axis of oscillation 4 of the links 1.
  • pistons 9 of the internal combustion engine rigidly fitted to the frame 8 and bearing seated pistons 10 of the fuel discharge pump, bearing seated on an axis coinciding with the axis of oscillation 4 of the link 1 , connected by an elastic link 11 , in this case a spring, to the frame 8.
  • an elastic link 11 in this case a spring
  • the crankshaft 7 of the link 1 is kinematically connected with fluid distributor 13 of cylindrical surface, bearing seated at an axis in parallel to the axis of oscillation 4 of the link 1.
  • the fluid distributor 13 is bearing seated in a cylindrical seat 14, formed in the fixed piston 9.
  • the openings 15 between the seats 14 and the pre-piston compressor chambers 12 form connections between adjacent pre-piston compressor chambers 12 in a definite order by means of specially made channels in the fluid distributors 13.
  • the connection between the in feed pipeline 16 to the pre-piston compressor chamber 12 with fixed piston 9 is by means of valve 18 connected to the frame 8 by an elastic connection.
  • the connection to the exhaust pipeline 17 and pre-piston compressor chamber 12 with fixed piston 9 is by means of specially made channels in the bearing seated fluid distributor 13 which direction of the centre line of the axis of bearing support coincides with this of the axis of oscillation 4 of the links 1.
  • the connection of the pre-piston compressor chamber 12 with a bearing seated piston 10 of the fuel injection pump with the discharge pipeline 17 is through nozzle 19.
  • the links 1 of the two link mechanisms are fitted rigidly one to another.
  • the crankshafts 7 kinematically connected to them have centre lines parallel to the axis of oscillation 4 and the size of the eccentricity of their cranks, distance and oriented position with relation to the axis of oscillation 4 of the links 1 are such that an amplitude of oscillation of the links 1 of thirty degrees for the two link mechanisms at a time is ensured.
  • the channel of the fluid distributor 13 in conjunction with the opening of the ignition plug 20 form the combustion chamber 21.
  • Figure 2 is shown a cross section on the line B-B of the module of a piston machine with adjustable pressure in the compressor chamber described on the line A-A of the above Fig. 1.
  • the kinematic connection between the crankshafts 7 of the two link mechanisms, and also between the crankshafts 7 and fluid distributors 13 is by means of gear 22 fitted at output shaft 23.
  • the principle of operation of the module for a piston machine with adjustable pressure in the compressor chamber embodied as an internal combustion engine with fuel injection pump is as follows.
  • the air mixture is supplied through inlet line 16 of the internal combustion engine - Fig. 1 and Fig. 2, valve 18 in the compressor chamber 12 with fixed piston 9 where through opening 15 and special channel of a bearing seated fluid distributor 13 it is mixed in the seat 14 with fuel supplied from the compressor chamber 12 of the fuel injection pump with bearing seated piston 10 through nozzle 19 into combustion chamber 21.
  • the fuel mixture is ignited by means of a spark from the ignition plug 20 and burns.
  • the pressure so produced forms a gas force which acts upon the front area of the link pistons 2 in the adjacent compressor chamber 12 with fixed piston 9 where the position of the fluid distributor 13 is changed by means of link 1 and the crankshaft 7 kinematically connected to it, and through tooth gear 22 so that at the end of the working cycle a connection is achieved with the exhaust pipe 17 through a special channel of bearing seated fluid distributor 13 of centre line coinciding with the axis of oscillation 4 of link 1.
  • the torque is transferred by the link piston 2 to the link mechanism and to the output shaft 23. This cycle is repeated many times.
  • Figure 3 an indicator diagram of the module for a piston machine with adjustable pressure in the compressor chamber, embodied as an ICE with a fuel injection pump, with indicated positions of the bearing seated fluid distributor 13 which forms the connection between the adjacent compressor chambers in a full working cycle.
  • the positions of the fluid distributor 13 are shown in the indicator diagram at the respective moment of the working cycle of an ICE.
  • Figure 4 is a transverse section of the module for a piston machine with adjustable pressure in the compressor chamber, embodied as a compressor. It comprises two links 1 with two link pistons 2 fitted rigidly to each one.
  • the links 1 are independently bearing seated on parallel axes of oscillation 4.
  • Each link is separately, kinematically connected to crankshaft 7 which axis is in parallel to the axes of oscillation 4 of links 1 by means of guide 5 and link roller 6.
  • the size of the eccentricity of the crank, distance and oriented position with relation to the axes of oscillation 4 of links 1 is specially selected dependent the amplitude of oscillation in a definite plan of position or functional relation between the angle of rotation of the crankshaft 7 and angle of deviation of links 1 of the two link mechanisms at a time.
  • the two link mechanisms are located in cavities in frame 8.
  • the cavities are closed volumes of sectors formed by rotation surfaces, equidistant to rotation surfaces, forming link pistons 2 fitted rigidly to links 1 , of axis of rotation coinciding with the axis of oscillation 4 of links 1.
  • the connection between the pre-piston compressor chambers 12 and inlet pipe 16 and discharge pipe 17 is by means of valve 18.
  • the principle of operation of the module for a piston machine with adjustable pressure in a compressor chamber embodied as a compressor is as follows. Upon oscillation in every link mechanism link 1 with one of the link pistons 2 at a time creates subpressure in pre- piston compressor chamber 12. The difference in the pressure between compressor chamber 12 and inlet pipe 16 creates gas force which overcomes the elastic connection of valve 18. The fluid is supplied to the compressor chamber 12 by inlet pipe through valve 18. The second link piston 2 creates overpressure in adjacent compressor chamber 12. The difference in pressure between compressor chamber 12 and discharge pipe 17 creates gas force which overcomes the elastic connection of valve 18. The fluid from the compressor chamber 12 enters the discharge pipe 17 through valve 18. Positions of valves 18 will change upon deviation of link 1 to back end position. This cycle is repeated many times.
  • FIG. 5 a module for a piston machine with adjustable pressure in the compressor chamber, embodied as a hydro and pneumatic engine.
  • the differences between the module shown in Fig. 1 and Fig. 2, and the module shown in Fig. 5 are as follows.
  • the links 1 of the two link mechanisms are with bearing resting independent from each other and common axis of oscillation 4. In this case the use of a fixed piston 9 or bearing seated piston 10 is not necessary.
  • the compressor chamber 12 is formed between the link pistons 2 of the two link mechanisms.
  • a certain advantage of the said construction is that it allows the kinematically connected crankshafts 7 to rotate in one direction upon change of direction of the fluid toward the compressor chamber 12 which is performed by the fluid distributor 13.
  • Figure 6 is a module for a piston machine with adjustable pressure in the compressor chamber, embodied as a kinematic connection between two shafts as a clutch or brake.
  • This module comprises three link mechanisms spaced at 120° one from other.
  • the links 1 are interconnected rigidly and with link pistons 2, and have a common axis of oscillation 4.
  • the crankshafts 3 kinematically connected to them are of axes parallel to the axis of oscillation 4.
  • the crankshafts 7 are kinematically interconnected by an epicydic tooth gear 22.
  • the mobile pistons 10 between the link pistons 2 are bearing seated on a shaft of a centre line coinciding with the axis of oscillation 4 of the links 1.
  • the connection between two adjacent compressor chambers 12 is by a throttle 24.
  • the kinematic connection is between the shaft of the mobile pistons 10 and the shaft of the central gear wheel of the epicydic tooth gear 22.
  • the mobility of the shaft of the bearing seated piston 10 with relation to the shaft of the central tooth wheel of the epicydic tooth gear 22 is ensured by transfer of the fluid between two adjacent compressor chambers 12 through throttle 24.
  • the modules plays the role of a clutch. In the case when no fluid is transferred and when the central gear wheel of the epicydic tooth gear 22 is fitted rigidly, the module runs as a brake.
  • FIG. 7 a module for a piston machine with adjustable pressure in the compressor chamber, embodied as a compressor or a pump.
  • This module comprises a link mechanism of which the link 1 with link piston 2 is kinematically connected with a bearing rested piston 10 with a bearing axis parallel to the axis of oscillation 4 of the link 1 through tooth gear 22.
  • the differences as compared to the module shown in Fig. 4 are in the increased volume of the compressor chamber 12, commensurate with the amplitude of oscillation greater than 90 degrees.
  • the principle of operation is as follows.
  • the amplitude of oscillation of the link 1 through the link piston 2 is increased by a high tooth gear 22.
  • pressure at the one end of the piston 10 and downpressure at the other in a cycle which ensures a constant direction of the fluid through the valves 18.
  • the amplitude of oscillation of the link mechanism is performed in a certain plan of position or as a function of the angle of rotation of the crankshaft and angle of deviation of the link 1 , known from the theory of mechanisms and machines. This is obtained by means of the type of the guide 5 of the link roller 6, the size of the eccentricity of the crank of the crankshaft 7, its distance and oriented position with relation to the axis of the oscillating links 1 at one or more link mechanisms in a construction.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

L'invention concerne un module de machine à piston oscillant utilisé dans des moteurs à combustion interne, des moteurs hydrauliques, des moteurs pneumatiques, des compresseurs et des pompes. Ledit module comprend deux mécanismes de liaison espacés de 180° l'un par rapport à l'autre dans une structure (8). Des pistons (10) à appui de la pompe d'injection de combustible et des pistons fixes (9) d'un moteur à combustion interne, formant les chambres (12) de compression, sont situés entre les pistons (2) de liaison. Les distributeurs (13) de fluide à appui forment une connexion par l'intermédiaire d'ouvertures (15) entre les chambres de compression adjacentes (12) d'un moteur à combustion interne. L'air injecté à travers la soupape (18), la chambre (12) de compression et l'ouverture (15) dans le distributeur (13) de fluide est mélangé à du combustible injecté par la pompe d'injection de combustible à travers une buse (19) dans la chambre (21) de combustion.
PCT/BG2003/000004 2002-03-04 2003-01-21 Machine a piston oscillant presentant un mecanisme de soupape rotatif WO2003074839A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2003201551A AU2003201551A1 (en) 2002-03-04 2003-01-21 Oscillating piston machine with rotary valve mechanism

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
BG106475A BG64852B1 (bg) 2002-03-04 2002-03-04 Модул за бутална машина с регулируемо налягане в компресорната камера
BG106475 2002-03-04

Publications (1)

Publication Number Publication Date
WO2003074839A1 true WO2003074839A1 (fr) 2003-09-12

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ID=27768056

Family Applications (1)

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PCT/BG2003/000004 WO2003074839A1 (fr) 2002-03-04 2003-01-21 Machine a piston oscillant presentant un mecanisme de soupape rotatif

Country Status (3)

Country Link
AU (1) AU2003201551A1 (fr)
BG (1) BG64852B1 (fr)
WO (1) WO2003074839A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2925571A1 (fr) * 2007-12-19 2009-06-26 Sycomoreen Sarl Machine a pistons rotatifs a battement controle
WO2010010094A3 (fr) * 2008-07-21 2010-09-10 Manfred Max Rapp Moteur à piston
AT510278B1 (de) * 2011-05-13 2012-03-15 Freller Walter Schwingkolbenmotor
RU2485336C2 (ru) * 2010-02-17 2013-06-20 Валерий Моисеевич Арутюнов Двухроторная машина с наддувом
RU2486343C2 (ru) * 2009-07-31 2013-06-27 Валерий Моисеевич Арутюнов Машина с маятниковым рычагом (варианты)

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DE5998C (de) * R. JOHNSON in Bradford Kapselpumpe bezw. Kraftmaschine
DE3998C (de) * C. bartelt' in Stargard i. Pommern, Jägerstrafse 34 Direkt und doppeltwirkende schwingende Expansionsdampfpumpe
DE24205C (de) * P. J. CARMIEN in Issy bei Paris Pumpe mit oscillirendem Kolben, auch als Wassermesser und Motor anzuwenden
US710212A (en) * 1901-12-02 1902-09-30 Michael j doherty Fluid-meter.
US1473199A (en) * 1921-03-25 1923-11-06 Peraza Jose Castillo Oscillating internal-combustion engine
FR615243A (fr) * 1925-05-11 1926-12-31 Moteur à combustion interne à simple et double effet et à cylindrée variable
GB402818A (en) * 1932-06-09 1933-12-11 Albert Williams Daw Improvements in or relating to rotary engines, pumps and the like
FR1367633A (fr) * 1963-06-04 1964-07-24 Moteur à explosion à mouvement oscillant
DE2607586A1 (de) * 1976-02-25 1977-09-08 Friedrich Dorgathen Brennkraftmaschine zur erzeugung einer drehbewegung
US4099448A (en) * 1976-01-19 1978-07-11 Young Gerald H Oscillating engine
JPS57200619A (en) * 1981-06-03 1982-12-08 Ryohei Akai Rolling type internal combustion engine
US5086732A (en) * 1990-09-07 1992-02-11 Seno Cornelio L Four stroke concentric oscillating rotary vane internal combustion engine
CA2183306A1 (fr) * 1996-08-14 1998-02-15 Clarence Lavern Sunley Moteur a combustion interne
DE10025939A1 (de) * 2000-05-26 2001-11-29 Helmut Obieglo Quantum Delay Rotational Motor

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Publication number Priority date Publication date Assignee Title
BG61777B1 (bg) * 1994-11-28 1998-05-29 Ангел НЕДЕВ Бутална машина

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Publication number Priority date Publication date Assignee Title
DE5998C (de) * R. JOHNSON in Bradford Kapselpumpe bezw. Kraftmaschine
DE3998C (de) * C. bartelt' in Stargard i. Pommern, Jägerstrafse 34 Direkt und doppeltwirkende schwingende Expansionsdampfpumpe
DE24205C (de) * P. J. CARMIEN in Issy bei Paris Pumpe mit oscillirendem Kolben, auch als Wassermesser und Motor anzuwenden
US710212A (en) * 1901-12-02 1902-09-30 Michael j doherty Fluid-meter.
US1473199A (en) * 1921-03-25 1923-11-06 Peraza Jose Castillo Oscillating internal-combustion engine
FR615243A (fr) * 1925-05-11 1926-12-31 Moteur à combustion interne à simple et double effet et à cylindrée variable
GB402818A (en) * 1932-06-09 1933-12-11 Albert Williams Daw Improvements in or relating to rotary engines, pumps and the like
FR1367633A (fr) * 1963-06-04 1964-07-24 Moteur à explosion à mouvement oscillant
US4099448A (en) * 1976-01-19 1978-07-11 Young Gerald H Oscillating engine
DE2607586A1 (de) * 1976-02-25 1977-09-08 Friedrich Dorgathen Brennkraftmaschine zur erzeugung einer drehbewegung
JPS57200619A (en) * 1981-06-03 1982-12-08 Ryohei Akai Rolling type internal combustion engine
US5086732A (en) * 1990-09-07 1992-02-11 Seno Cornelio L Four stroke concentric oscillating rotary vane internal combustion engine
CA2183306A1 (fr) * 1996-08-14 1998-02-15 Clarence Lavern Sunley Moteur a combustion interne
DE10025939A1 (de) * 2000-05-26 2001-11-29 Helmut Obieglo Quantum Delay Rotational Motor

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Title
PATENT ABSTRACTS OF JAPAN vol. 007, no. 050 (M - 197) 26 February 1983 (1983-02-26) *

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2925571A1 (fr) * 2007-12-19 2009-06-26 Sycomoreen Sarl Machine a pistons rotatifs a battement controle
WO2010010094A3 (fr) * 2008-07-21 2010-09-10 Manfred Max Rapp Moteur à piston
DE102008040574B4 (de) * 2008-07-21 2013-08-14 Manfred Max Rapp Kolbenmaschine
RU2486343C2 (ru) * 2009-07-31 2013-06-27 Валерий Моисеевич Арутюнов Машина с маятниковым рычагом (варианты)
RU2485336C2 (ru) * 2010-02-17 2013-06-20 Валерий Моисеевич Арутюнов Двухроторная машина с наддувом
AT510278B1 (de) * 2011-05-13 2012-03-15 Freller Walter Schwingkolbenmotor

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Publication number Publication date
AU2003201551A1 (en) 2003-09-16
BG106475A (en) 2003-09-30
BG64852B1 (bg) 2006-06-30

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