US20090297385A1 - Rotary Motor With Intermittent Movements of the Rotors - Google Patents

Rotary Motor With Intermittent Movements of the Rotors Download PDF

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Publication number
US20090297385A1
US20090297385A1 US12/085,524 US8552406A US2009297385A1 US 20090297385 A1 US20090297385 A1 US 20090297385A1 US 8552406 A US8552406 A US 8552406A US 2009297385 A1 US2009297385 A1 US 2009297385A1
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United States
Prior art keywords
rotor member
rotor
rotary motor
motor according
rotors
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.)
Abandoned
Application number
US12/085,524
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English (en)
Inventor
Ben Cornelius
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Individual
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Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of US20090297385A1 publication Critical patent/US20090297385A1/en
Abandoned legal-status Critical Current

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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
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/18—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • 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
    • 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
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • F02B53/02—Methods of operating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C2/00—Rotary-piston engines
    • F03C2/08—Rotary-piston engines of intermeshing-engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • 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
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/082—Details specially related to intermeshing engagement type machines or engines
    • F01C1/084—Toothed wheels
    • 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
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/082—Details specially related to intermeshing engagement type machines or engines
    • F01C1/086—Carter
    • 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

  • THIS invention relates to a novel rotary motor.
  • Rotary motors are well known for use in a wide variety of applications, including internal combustion engines for vehicles, compressors, pumps and the like.
  • Wankel rotary engine A wide variety of rotary type internal combustion engines have been proposed and developed in the past.
  • Wankel rotary engine is well known.
  • This includes a substantially laminar rotor member which revolves about a moving axis.
  • the rotor member is a laminar plate in the shape of a triangle having convex sides.
  • the plate rotates about the moving axis within a chamber, which is configured and dimensioned to be slightly wider than the width of the plate member, and having a inner shape which complements the rotated shape of the plate member.
  • compressors and engines which incorporate rotor members having vane-type shapes.
  • rotary motor herein includes both an internal combustion engine and a compressor, pump or the like.
  • a rotary motor comprising:
  • the angular velocity of the first rotor and of the second rotor differ from one another during a rotational cycle of the motor. Preferably through 360° in respect of each rotor.
  • first rotor member and the second rotor member may be dimensioned and configured to enclose a compression chamber between them as they rotate.
  • first rotor member and the second rotor member may each include vanes extending radially outwardly and having receiving formations between them, with the receiving formations of the first rotor member being dimensioned and configured for receiving vanes from the second rotor member and the receiving formations of the second rotor member being dimensioned and configured for receiving vanes from the first rotor member during rotation of the rotor members.
  • the first rotor member and the second rotor member may be rotationally coupled to each other by means of a transmission system.
  • the transmission system may comprise a plurality of gears, which may be partially of a first radius and partially of a second radius.
  • the gears may be of variable radius.
  • the transmission system may be adapted to drive the first rotor member at a first angular velocity and the second rotor member at a second angular velocity for at least part of a revolution, and then drive the first rotor member at the second angular velocity and the second rotor member at the first angular velocity for the complementary part of the revolution.
  • the first axis may be parallel to the second axis and the first rotor member and the second rotor member may be enclosed on two sides by a housing to form chambers within the housing.
  • each vane terminates at its free end in a radially expansible section adapted to follow the contour of the chambers in the housing.
  • the housing could be extended radially outwardly at opposed zones thereof to form a generally elliptically shaped structure.
  • the rotary motor in the form of an internal combustion engine may further comprise an inlet passage for introducing air into the compression chamber and an outlet passage for exhausting gasses from the compression chamber; means for introducing fuel into the compression chamber at predetermined zones; and ignition means for igniting fuel introduced into the compression chamber.
  • FIG. 1 shows a schematic perspective view of an internal combustion engine according to the invention, without the housing;
  • FIG. 2 shows a schematic front view of a first rotor member and a second rotor member and transmission as shown in FIG. 1 ;
  • FIGS. 3 a to 3 f are schematic plan views of the first rotor member and the second rotor member and their movement relative to each other;
  • FIGS. 4 a to 4 d are schematic plan views of the gears in the transmission system to cause movement of the rotor members
  • FIG. 5 is a graph of the angular position of a first rotor and a second rotor against the angular position of the drive shaft during one revolution of the transmission system;
  • FIG. 6 is a schematic illustration of an inlet port and an outlet port in a side plate which forms part of the housing of the motor of the invention
  • FIG. 7 is a schematic plan view of a first rotor member and a second rotor member wherein radially outwardly directed vanes of the rotors each include an extensible front end section;
  • FIG. 8 is a schematic plan view of opposed chambers within the first rotor member and the second rotor member rotate, such chambers being extended outwardly to modify the compression and expansion characteristics of the motor;
  • FIG. 9 is a schematic perspective view of a timing arrangement which duplicates the movement of the vanes of the first rotor member and the second rotor member.
  • a rotary motor in this instance an internal combustion engine, is generally indicated by reference numeral 10 .
  • the rotary member could also be applied as a compressor, pump or the like.
  • the internal combustion engine 10 comprises a first rotor member 20 rotatable about a first axis embodied by a first rotor shaft 30 ; a second rotor member 40 rotatable about a second axis embodied by a second rotor shaft 50 parallel to the first rotor shaft 30 ; and a gear system 60 for rotating the first rotor member 20 and the second rotor member 40 ; wherein the first rotor 20 member and the second rotor member 40 are adapted to rotate at variable angular velocities, and at different angular velocities.
  • the first rotor member 20 and the second rotor member 40 are dimensioned and configured to enclose a combustion chamber 200 between them as they rotate, as shown in FIGS. 3 a to 3 f .
  • the first rotor member 20 and the second rotor member 40 both have engagement surfaces 21 and 41 respectively on opposing sides of each rotor.
  • the rotors 20 and 40 will be enclosed on either side by a housing shown schematically at 55 to prevent combustion outlet gasses escaping from the sides of the rotors 20 and 40 in operation.
  • the housing can comprise a pair of plate members 56 located on either side of the rotors 20 and 40 .
  • the housing 55 includes a pair of circular chambers 56 which intersect as shown in FIG. 8 and within which the rotor members 20 and 40 rotate.
  • the generally circular chambers 56 can be modified for example by a radially outward extension 57 on the periphery thereof in order to modify the compression and expansion of the combustion chamber 200 as explained in more detail below.
  • the first rotor member 20 and the second rotor 40 member each comprise a plurality of vanes 25 and 45 respectively, extending radially outwardly and having receiving formations 26 and 46 respectively, between them, which receiving formations 26 and 46 are dimensioned and configured for operationally receiving vanes from the other rotor member.
  • the free ends of the vane formations 25 and 45 will be provided with radially extensible end sections 25 a and 45 a which are adapted to follow the curvature in the receiving formations 26 and 46 .
  • Such extensible end sections will also be able to follow the periphery of the internal chambers 56 , FIG. 8 , where these are enlarged radially outwardly as shown by the area 57 .
  • the enlarged area 57 will influence the entrainment of air into the chamber 57 , the compression thereof, and the expansion of combustion gasses.
  • the gear system 60 couples the first rotor member 20 and the second rotor member 40 to each other so that they may only move through a predetermined sequence of movements relative to each other.
  • the gear system 60 comprises a plurality of gears and shafts, including the drive gear set 70 located on a drive shaft 73 , the first timing gear set 80 located on a first timing shaft 100 and the second timing gear set 90 located on a second timing shaft 110 .
  • the drive gear set is comprised of a large size gear 71 and a small size gear 72 located next to each other on a drive shaft 73 .
  • the tooth set of the large gear 71 extends for only 180 degrees around the drive shaft, while the tooth set of the small gear 72 extends around the complementary 180 degrees of the drive shaft 73 .
  • first and second timing gear sets 80 and 90 are comprised of large gears 81 and 91 , and small gears 82 and 92 located next to each other on the first and second timing shaft 100 and 110 .
  • the tooth sets of each of the large gears 81 and 91 extends around the first and second timing shafts 100 and 110 for 90 degrees, while the tooth sets of each of the small gears 82 and 92 extends for 270 degrees (the complementary angle) around the first and second timing shafts 100 and 110 .
  • the first timing gear set 80 and the second timing gear set 90 communicate with the drive gear set 70 (as shown in FIGS. 4 a and 4 d ) so that at some stages the larger gear 71 of the drive gear set 70 drives the smaller gears 82 and 92 of the first timing gear set 80 and the second timing gear set 90 respectively, and at other stages the smaller gear 72 of the drive gear set 70 drives the larger gear 81 and 91 of the first timing gear set 80 and the second timing gear set 90 respectively.
  • FIG. 5 A graph of the angular velocities of the first and second rotor members 40 and 20 is shown in FIG. 5 .
  • the graph shown in FIG. 5 need not be comprised of linear lines, and could for example have curved zones, in the lower graph prior to exchange of direction, and in the upper graph prior to the end thereof. The effect will be that the compression and expansion chambers of the motor of the invention will be of unequal maximum volumes.
  • the first timing gear set 80 and the second timing gear set 90 drive a first timing shaft 100 and a second timing shaft 110 respectively.
  • the first timing shaft 100 and a second timing shaft 110 in turn drive a first reduction gear set 120 and a second reduction gear set 130 respectively, which drive the rotor members 20 and 40 in opposite directions through a first final drive cog 140 and a second final drive cog 150 .
  • both the small gears and the large gears for each of the drive gear set 70 , the first timing gear set 80 and the second timing gear set 90 can be incorporated on a single gear cog, or a continuously variable transmission may be used. It should be noted that the results achieved by the gears described herein could be achieved by various arrangements of gears, not shown, and the invention is not limited to the gear arrangements illustrated in FIGS. 4 a to 4 d.
  • the second reduction gear 130 set has an extra reversal cog 131 to allow for the reversal of direction of the second rotor member 40 .
  • FIG. 9 shows schematically in FIG. 9 wherein templates 63 which could be secured to the axes 30 and 50 of the rotors 20 and 40 respectively are provided, the templates including cam formations 61 in the form of grooves which equate the movement of the vanes 25 , 45 .
  • cam formations 61 are followed by followers in the form of pins 62 .
  • the template 63 and follows 62 will thus duplicate the movement as the rotors 20 and 40 . Doubtless other variations are also possible.
  • the rotary motor operating as an internal combustion engine 10 further comprises an inlet passage shown schematically at 51 , FIG. 6 , for introducing air 52 into the combustion chamber 200 formed by the rotors 20 and 40 .
  • the internal combustion engine 10 comprises an outlet passage shown schematically at 53 , FIG. 6 , for exhausting combustion gasses 54 from the combustion chamber 200 .
  • the internal combustion engine 10 comprises means, such as fuel injectors (not shown) or a carburetor (not shown) for introducing fuel (not shown) into the combustion chamber 200 at predetermined points, either by injecting it directly into the combustion chamber 200 or letting it flow into the combustion chamber 200 together with air introduced through the inlet passage.
  • the internal combustion engine 10 also includes ignition means (not shown), such as a spark plug, for igniting the fuel and air mixture in the combustion chamber 200 . It is envisaged that high compression within the combustion chamber 200 may allow the use of diesel or other similar fuels for compression-ignition operation.
  • ignition means such as a spark plug
  • drive gear set 70 will drive the first timing gear set 80 and second timing gear set 90 .
  • the drive gear set 70 and the respective timing gear sets 80 and 90 are arranged so that, for each revolution of the drive shaft 73 , the first timing shaft 100 is driven at a different angular velocity relative to the second timing shaft 110 for at least part of each revolution, after which the angular velocities of the first and second timing shafts 10 and 110 are reversed as shown in FIG. 5 .
  • the timing shafts drive the first reduction gear set 120 and the second reduction gear set 130 , which then drive the first rotor member and the second rotor members respectively.
  • the direction of the second rotor member 40 is reversed by the inclusion of the reversal cog 131 in the second reduction gear set 130 , so that the first rotor member 20 and second rotor member 40 turn in opposite directions as shown in FIGS. 3 a to 3 f.
  • FIGS. 3 a to 3 f show how the rotor members 20 and 40 rotate relative to each other.
  • the first rotor member 20 is rotating faster than the second rotor member 40 .
  • a vane 25 on the first rotor member 20 is received into a receiving formation 46 (disposed between the two vanes 45 on the second rotor member 40 ) on the second rotor member 40 , an enclosed combustion chamber 200 is formed.
  • a combustible mixture of air and fuel shown at 52 , FIG. 6 is introduced into the combustion chamber 200 .
  • this mixture may be introduced by known means, such as by using a carburetor and introducing the mixture through the inlet, or by injecting a fine mist of fuel into the combustion chamber 200 by means of a fuel injector (not shown) to mix in the combustion chamber 200 with air introduced through the inlet passage.
  • a fuel injector not shown
  • small auxiliary combustion chambers 22 , FIG. 2 , in the vanes 25 and 45 as illustrated may be provided to enhance the combustion process. It is envisaged that fuel injection will be directed to the small chambers 22 .
  • the combustion chamber 200 becomes reduced in size, thereby compressing the fuel and air mixture (as shown in FIGS. 3 b and 3 c ).
  • the angular velocities of the first and second rotor members will change so that the slower rotor member (the second rotor member 40 ) will now become the faster moving of the two rotor members 20 and 40 , and vice versa for the first rotor member 20 .
  • the compressed fuel/air mixture 52 in the compressed combustion chamber 200 is now ignited by the ignition means.
  • the ignition of the fuel/air mixture causes expansion of the gasses within the combustion chamber 200 .
  • the combustion chamber 200 expands, driving the second rotor member in an anticlockwise direction as shown in FIG. 3 d .
  • another combustion chamber 200 is being formed by the interaction of the vanes and receiving formations on the first and second rotor members 20 and 40 as shown in FIG. 3 e . It has been found that prior to the formation of the closed combustion chamber 200 in FIG. 3 a , the volume thereof is decreased and excessive air is ducted into the adjacent chamber 201 whereby the pressure in the adjacent chamber 201 is increased to greater than ambient air pressure.
  • the combustion gasses 54 in the combustion chamber 200 are then exhausted through an outlet passage 53 in the housing 55 .
  • the outlet passage 53 may be located to the side of the rotor members 20 and 40 in the housing 55 , FIG. 6 .
  • this basic principle of operation may be used in a wide variety of configurations, and that a wide variety of shapes may be used as rotor members 20 , 40 , in order to maximise the volume of fuel/air mixture 52 compressed, or to maximise the time during which the ignited fuel air mixture acts against the vanes 45 .
  • the gear system 60 may be a planetary type gear system. It is further envisaged, due to the elongated shape of the combustion chamber 200 , that two ignition means, in the form of spark plugs, may be used to ignite the fuel air mixture 52 at either end of the combustion chamber 200 . For the same reason, it is preferable to employ two fuel injectors, not shown, in spaced relationship for the elongate combustion chamber 200 .
  • vanes 25 and 45 and receiving formations 26 and 46 of the rotors 20 and 40 may include combustion enhancing formations to enhance combustion efficiency.
  • a set of rotor members may be arranged in a circular formation around a single inlet passage 51 or outlet passage 53 .
  • rotor members 20 , 40 with less pronounced vanes 25 , 45 , may be used for purposes of strength or reliability, and in a wide variety of shapes.
  • a plurality of rotor members 20 , 40 may be located around a single central rotor member so as to cause the formation of a plurality of combustion chambers with the central rotor member.
  • one of the interacting rotor members 20 , 40 may be held stationary while one or more rotating rotor members may rotate around the stationary rotor member, while still interacting with the stationary rotor member in the same manner as described above. It is further envisaged that in such an embodiment, the plurality of rotor members rotating about the stationary one rotor member may be phased in their timing so that combustion will not occur in all the combustion chambers at the same time, but will occur at regular intervals.
  • a number of rotors may be located on the same shaft, with each rotor interacting with a corresponding rotor as a rotor set.
  • Each of these rotor sets may be in synchronisation with each other, or may be phased so that they are out of synchronisation with each other.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)
  • Rotary Pumps (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Hydraulic Motors (AREA)
US12/085,524 2005-11-28 2006-11-27 Rotary Motor With Intermittent Movements of the Rotors Abandoned US20090297385A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
ZA200509575 2005-11-28
ZA2005/09575 2005-11-28
PCT/IB2006/054448 WO2007060642A1 (en) 2005-11-28 2006-11-27 Rotary motor with intermittent movements of the rotors

Publications (1)

Publication Number Publication Date
US20090297385A1 true US20090297385A1 (en) 2009-12-03

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US12/085,524 Abandoned US20090297385A1 (en) 2005-11-28 2006-11-27 Rotary Motor With Intermittent Movements of the Rotors

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Country Link
US (1) US20090297385A1 (ru)
EP (1) EP1957753A1 (ru)
JP (1) JP2009517600A (ru)
KR (1) KR20080078809A (ru)
CN (1) CN101360886A (ru)
AU (1) AU2006318065A1 (ru)
BR (1) BRPI0619064A2 (ru)
CA (1) CA2631319A1 (ru)
RU (1) RU2008126308A (ru)
WO (1) WO2007060642A1 (ru)
ZA (1) ZA200804480B (ru)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120160209A1 (en) * 2010-12-22 2012-06-28 Boucher Bobby Turbine having cooperating and counter-rotating rotors in a same plane

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009095895A2 (en) * 2008-02-01 2009-08-06 Ben Cornelius Transmission arrangement for a rotary machine
GB2473341B (en) * 2009-03-25 2011-06-29 Environmental Mfg Llp A gear set for a rotary mechanism
CN109555683B (zh) * 2019-01-18 2024-03-29 宁波领智机械科技有限公司 一种输送固液双相的转子泵

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4057035A (en) * 1976-03-11 1977-11-08 Cherng Yi Su Internal combustion engines
US4312629A (en) * 1980-08-22 1982-01-26 General Supply (Constructions) Co. Ltd. Universal rotating machine for expanding or compressing a compressible fluid
US5485725A (en) * 1992-02-18 1996-01-23 Tochigi Fugi Sangyo Kabushiki Kaisha Continuously variable transmission

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE634333A (ru) *
GB190710556A (en) * 1906-05-05 1908-04-30 Stephen Hopkins Draper Improvements in Rotary Engines.
GB203779A (en) * 1922-06-13 1923-09-13 Frederick Vincent Improvements in and relating to rotary engines
FR790174A (fr) * 1935-05-17 1935-11-15 Engrenage progressif
BE899318A (nl) * 1984-04-02 1984-07-31 Haesevoets Lambert Dubbelkamwiel ontploffinsmotor.
SE442760B (sv) * 1985-02-05 1986-01-27 Karl Zetterlund Rotationskolvmotor
JPH0492144A (ja) * 1990-08-01 1992-03-25 Sharp Corp 間欠駆動装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4057035A (en) * 1976-03-11 1977-11-08 Cherng Yi Su Internal combustion engines
US4312629A (en) * 1980-08-22 1982-01-26 General Supply (Constructions) Co. Ltd. Universal rotating machine for expanding or compressing a compressible fluid
US5485725A (en) * 1992-02-18 1996-01-23 Tochigi Fugi Sangyo Kabushiki Kaisha Continuously variable transmission

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120160209A1 (en) * 2010-12-22 2012-06-28 Boucher Bobby Turbine having cooperating and counter-rotating rotors in a same plane

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WO2007060642A1 (en) 2007-05-31
ZA200804480B (en) 2009-08-26
CA2631319A1 (en) 2007-05-31
CN101360886A (zh) 2009-02-04
JP2009517600A (ja) 2009-04-30
RU2008126308A (ru) 2010-01-10
AU2006318065A1 (en) 2007-05-31
EP1957753A1 (en) 2008-08-20
KR20080078809A (ko) 2008-08-28
BRPI0619064A2 (pt) 2011-09-20
WO2007060642B1 (en) 2007-09-20

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