WO2004029481A1 - Appareil de transmission de puissance - Google Patents

Appareil de transmission de puissance Download PDF

Info

Publication number
WO2004029481A1
WO2004029481A1 PCT/AU2003/001273 AU0301273W WO2004029481A1 WO 2004029481 A1 WO2004029481 A1 WO 2004029481A1 AU 0301273 W AU0301273 W AU 0301273W WO 2004029481 A1 WO2004029481 A1 WO 2004029481A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
arm
planetary gear
base
connecting rod
Prior art date
Application number
PCT/AU2003/001273
Other languages
English (en)
Inventor
Peter Bortolin
Fred C. O. Sticher
Original Assignee
Peter Bortolin
Sticher Fred C O
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 AU2002951742A external-priority patent/AU2002951742A0/en
Priority claimed from AU2002952172A external-priority patent/AU2002952172A0/en
Priority claimed from AU2002953078A external-priority patent/AU2002953078A0/en
Priority claimed from AU2002953076A external-priority patent/AU2002953076A0/en
Priority claimed from AU2003902177A external-priority patent/AU2003902177A0/en
Priority claimed from AU2003902359A external-priority patent/AU2003902359A0/en
Priority claimed from AU2003902583A external-priority patent/AU2003902583A0/en
Priority claimed from AU2003902901A external-priority patent/AU2003902901A0/en
Priority claimed from AU2003903217A external-priority patent/AU2003903217A0/en
Priority claimed from AU2003903804A external-priority patent/AU2003903804A0/en
Priority claimed from AU2003904403A external-priority patent/AU2003904403A0/en
Priority claimed from AU2003904347A external-priority patent/AU2003904347A0/en
Priority to AU2003265726A priority Critical patent/AU2003265726A1/en
Application filed by Peter Bortolin, Sticher Fred C O filed Critical Peter Bortolin
Publication of WO2004029481A1 publication Critical patent/WO2004029481A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/12—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types
    • F16H37/124—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types for interconverting rotary motion and reciprocating motion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M11/00—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels
    • B62M11/04—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio
    • B62M11/14—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M9/00—Transmissions characterised by use of an endless chain, belt, or the like
    • B62M9/02—Transmissions characterised by use of an endless chain, belt, or the like of unchangeable ratio
    • 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
    • F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
    • F02B41/02—Engines with prolonged expansion
    • F02B41/04—Engines with prolonged expansion in main cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H21/00—Gearings comprising primarily only links or levers, with or without slides
    • F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
    • F16H21/16—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for interconverting rotary motion and reciprocating motion
    • F16H21/18—Crank gearings; Eccentric gearings
    • F16H21/22—Crank gearings; Eccentric gearings with one connecting-rod and one guided slide to each crank or eccentric
    • F16H21/30—Crank gearings; Eccentric gearings with one connecting-rod and one guided slide to each crank or eccentric with members having rolling contact
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/042—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the connections comprising gear transmissions
    • F01B2009/045—Planetary gearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/12—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types
    • F16H2037/128—Generating reciprocating motion by a planetary gear (ratio 2:1) using endless flexible members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H21/00—Gearings comprising primarily only links or levers, with or without slides
    • F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
    • F16H21/16—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for interconverting rotary motion and reciprocating motion
    • F16H21/18—Crank gearings; Eccentric gearings
    • F16H21/36—Crank gearings; Eccentric gearings without swinging connecting-rod, e.g. with epicyclic parallel motion, slot-and-crank motion
    • F16H21/365—Crank gearings; Eccentric gearings without swinging connecting-rod, e.g. with epicyclic parallel motion, slot-and-crank motion with planetary gearing having a ratio of 2:1 between sun gear and planet gear

Definitions

  • the present invention relates to power transmission apparatus and more particularly but not exclusively to crank mechanisms employed in internal combustion engines, both two stroke and four stroke engines, bicycle chain mechanisms and other applications.
  • a power transmission apparatus including a base: a driven shaft rotatably supported by the base, an internal gear surrounding the shaft and fixed to the base, an arm fixed to the shaft and extending generally radially there from, a planetary gear rotatably attached to the arm and meshingly engaged with the internal gear so that rotation of said planetary gear causes rotation of said shaft and a connecting rod rotatably attached to an extension fixed to the planetary gear so that a piston driving said connecting rod causes rotation of said planetary gear, said connecting rod being attached to said planetary gear at a predetermined location from said planetary gear by the length ofthe extension and wherein said connecting rod angularly oscillates across a transverse axis of said shaft.
  • a power transmission apparatus including a base: a drive shaft rotatably supported by the base; an arm attached to the shaft and extending generally radially from therefrom; a secondary arm pivotally attached to the outer end ofthe radial crank arm, and at the opposite end of the said secondary arm, rotatably attached thereto, a piston driven connecting rod causes rotation ofthe radial crank arm, wherein said connecting rod angularly oscillates across a transverse axis of said shaft.
  • a guide means is used to guide the movement of he connecting rod.
  • a power transmission apparatus including a base: a driven shaft rotatably supported by the base, an internal gear surrounding the shaft and fixed to the base, an arm fixed to the shaft and extending generally radially there from, a planetary gear rotatably attached to the arm and meshingly engaged with the internal gear so that rotation of said planetary gear causes rotation of said shaft and to the planetary gear, so that a piston driving said connecting rod causes rotation ofthe said planetary gear and the driven shaft.
  • a power transmission apparatus including a base: a driven shaft rotatably supported by the base; an arm attached to the shaft and extending generally radially therefrom; a secondary arm pivotally attached to the outer end ofthe radial crank arm; and at the opposite end ofthe secondary arm, rotatably attached, is a further arm which has a pedal attached at the outer end wherein the sprockets restrict the pedals to a chosen path and when force is applied to the pedals, it causes rotation ofthe radial crank arm.
  • Figure 1 is a schematic end elevation of a power transmission apparatus of an internal combustion engine at a first embodiment.
  • Figure 2 is a schematic end elevation of a power transmission apparatus of an internal combustion engine of a further embodiment.
  • Figure 3 is a schematic end elevation of a power transmission apparatus, another embodiment for combustion engine.
  • Figure 4 is a schematic end elevation of a power transmission apparatus of a bicycle (showing one pedal).
  • crank assembly 10 for an internal combustion engine.
  • the crank assembly 10 includes a main driven shaft 11 supported by rotation by means of bearings 12 on a base 13.
  • a radial crank arm 14 Extending from the shaft 11 is a radial crank arm 14 terminating, at its radial extremity with a bearing 15.
  • Bearing 15 supports a planetary gear 16 meshingly engaged to an internal gear 17.
  • Attached to the planetary gear 16 is an extension arm 18, of at least two dimensions, which has a pivotally attached conrod 19 at the outer end. At opposite ends ofthe conrod 19, there is a piston (not shown) pivotally attached. A driving force applied to the piston causes the outer end ofthe extension arm 18 to move along a path shown by arrows 20; causing the radial crank arm 14 to rotate in the direction of arrow 21. The planetary gear 16 is caused to rotate in the direction of arrow 22.
  • the planetary gear is three quarters ofthe internal gear dimension; thus causing one and a half revolution ofthe driven shaft (540 degrees) for each stroke completed.
  • the proportional length ofthe extension arm 18 is crucial in order to obtain such an unexpected path seen by the arrow 20, therefore, obtaining during the stoke a much reduced piston displacement from top dead centre to the 45 degree angle and from 135 degree angle to the bottom dead centre.
  • the bulk of the piston's displacement occurs between 45degree and 135 degree angles.
  • extension arm 24 Another option would be to implement a much shorter extension arm 24. With this arrangement, during the stroke, the piston remains stationery from 135 degree to 225 degree angles. Practically the totality ofthe stroke occurs between 45 degree and 135 degree. The outer end of the extension arm 24 will move along arrows 25 which is ample time for the proper combustion of a slow burning fuel.
  • crank assembly 30 for an internal combustion engine.
  • the crank assembly 30 includes two main driven shafts 31 supported for rotation by means of bearings 32 on a base
  • radial crank arms 34 Extending from the shafts 31 are radial crank arms 34 terminating, at their radial extremity with bearings 35.
  • the bearings 35 have support arms 36, rotatably engaged with the arms 34.
  • Two connecting rods 38 are rotatably attached to the arms 36 by bearings 37.
  • the two connecting rods 38 are pivotally attached to one piston (not shown).
  • a driving force to the piston causes connecting pins 39 supporting the bearings 37 to slide along a horizontal path in opposite direction 40 controlled by a guide 41.
  • the radial crank arms 34 will rotate in the direction of arrows 42.
  • 2000cc engine performing at least like a 4000cc conventional engine. If the engines are of similar displacement, 4000cc and 4000cc, this arrangement will only need to rotate at half the speed to achieve similar performance, ie 1500 rpm versus 3000 rpm for the conventional engine.
  • the piston's displacement is very fast in this arrangement.
  • the piston's displacement is 40 to 50mm. Conventional is only 1 mm. A clear indication ofthe huge mechanical efficiency of this arrangement. Consequently, the embodiment exploits the combustion energy where or when it is most efficient. Therefore, the torque generated is greatly enhanced.
  • this engine can have half the number of pistons of a conventional one without compromising performance.
  • crank assembly 50 for an internal combustion engine.
  • the crank assembly 50 includes a main driven shaft 51 supported for rotation by means of bearings 52 on a base 53.
  • a radial crank arm 54 Extending from the shaft 51 is a radial crank arm 54 terminating, at its radial extremity with a bearing 55.
  • the bearing 55 supports a planetary gear 56, meshingly engaged to an internal gear 57 which is fixed to the base 53.
  • a conrod 58 Pivotally attached to the planetary gear 56, is a conrod 58 shown at the T.D.C. position and having a piston 64 pivotally attached at the outer end.
  • a driving force applied to the piston causes the planetary gear 56 to rotate in the direction of arrow 59 and the radial crank arm 54 to rotate in the direction of arrow 60.
  • the inner end ofthe conrod 58 at T.D.C. position 61 is caused to move along the path arrows 62 while completing the power stroke and the exhaust stroke in reaching 63.
  • the piston's displacement is much greater.
  • the driven shaft has a CN. joint.
  • the internal gear is synchronised to slide vertically in this case in order to increase the length ofthe power stroke.
  • a constant displacement ofthe piston for the duration of the power stroke is achieved while not having to increase the dimension ofthe engine.
  • the embodiment in a one piston engine with four strokes, the embodiment has compression and firing once fo ⁇ each completed cycle while the driven shaft rotates three revolutions (1080 degrees), since the planetary gear is three quarters the dimension ofthe internal gear.
  • the power and exhaust strokes are therefore much reduced in length for convenience.
  • an engine can perform six or eight firings while the conventional engine of similar displacement has completed one revolution (360 degree) of the driven shaft, ie similar to a firing frequency of a conventional engine having twelve or sixteen pistons.
  • the power and exhaust strokes are much reduced in length for convenience.
  • an engine can perform six or eight firings while the conventional engine of similar displacement has completed one revolution (360 degrees) ofthe driven shaft.
  • a firing frequency similar to a conventional engine having twelve or sixteen pistons.
  • the speed ofthe engine can be four times slower for similar rpm.
  • crank assembly 20 for pedal powered apparatus.
  • the crank assembly 20 includes a main driven shaft 21 supported for rotation by means of bearings 22 on a base 23.
  • a radial crank arm 24 Extending from the shafts 21 is a radial crank arm 24 terminating, at its radial extremity with a bearing 25.
  • Bearing 25 supports a planetary gear 26, engaged by chain 27 to sprocket 28 attached to base 23.
  • a driving force connected to the pedal arm 29 causes rotation ofthe planetary sprocket in the direction of arrow 30.
  • Due to engagement by chain 27 to the sprocket 28 which is fixed to the base 23.
  • the radial arm 24 will rotate in the direction of arrows 31.
  • the pedal arm 29 moves along elliptical path 32.
  • gear ratio is two to one.
  • Other gear ratio are possible for faster or slower pedal displacement.
  • Either sprocket 26 or sprocket 28 can be of shapes other than circular in order to obtain a preferred torque output-configuration and to maximise the efficiency at the top and bottom D.C. in particular.
  • the related dimensions of he two sprockets 26 and 28 can be chosen in order to obtain a preferred pedal's path together with related lengths ofthe pedal arm 29 and radial crank arm 24.
  • the sprocket 28 can have freedom of rotation of movement synchronised to rotate at a convenient slower rate, for a chosen pedal path. Therefore, the torsional force created to rotate the sprocket 28 can be also exploited.
  • chains and sprockets to operate the pedal's arm can be implemented if necessary or preferred.
  • the length ofthe pedal path therefore is 1040mm overall.
  • a conventional bicycle mechanism normally has a stoke of 340mm.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Transmission Devices (AREA)
  • Retarders (AREA)

Abstract

L'invention concerne un appareil de transmission de puissance (10) comprenant une base (13), et un arbre rotatif entraîné (11) supporté par la base (13). L'appareil (10) comporte un engrenage interne (17) entourant l'arbre (11) et fixé à la base (13), un bras (14) fixé à l'arbre (11) orienté généralement radialement à partir de l'arbre, un engrenage planétaire (13) rotatif fixé au bras (14) en prise avec l'engrenage interne (17) de façon que la rotation de l'engrenage planétaire (16) provoque la rotation de l'arbre (11) et une tige de connexion (19) fixée rotative à une extension (18) fixée à l'engrenage planétaire (16) de façon qu'un piston (non montré) entraînant la tige de connexion (19) provoque la rotation de cet engrenage planétaire (16). La tige de connexion (19) est fixée à l'engrenage planétaire (16) à un emplacement déterminé, à partir de l'engrenage planétaire (16), par la longueur de l'extension (18), et la tige de connexion (19) oscille de façon angulaire en travers d'un axe transversal de l'arbre (11).
PCT/AU2003/001273 2002-09-30 2003-09-26 Appareil de transmission de puissance WO2004029481A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2003265726A AU2003265726A1 (en) 2002-09-30 2003-09-26 Power transmission apparatus

Applications Claiming Priority (24)

Application Number Priority Date Filing Date Title
AU2002951742A AU2002951742A0 (en) 2002-09-30 2002-09-30 Cosmos
AU2002951742 2002-09-30
AU2002952172 2002-10-21
AU2002952172A AU2002952172A0 (en) 2002-10-21 2002-10-21 Cosmos
AU2002953076A AU2002953076A0 (en) 2002-12-03 2002-12-03 Cosmos
AU2002953078 2002-12-03
AU2002953076 2002-12-03
AU2002953078A AU2002953078A0 (en) 2002-12-03 2002-12-03 Cosmos
AU2003902177 2003-05-07
AU2003902177A AU2003902177A0 (en) 2003-05-07 2003-05-07 Cosmos
AU2003902359A AU2003902359A0 (en) 2003-05-15 2003-05-15 Cosmos
AU2003902359 2003-05-15
AU2003902583 2003-05-22
AU2003902583A AU2003902583A0 (en) 2003-05-22 2003-05-22 Cosmos
AU2003902901A AU2003902901A0 (en) 2003-06-11 2003-06-11 Cosmos
AU2003902901 2003-06-11
AU2003903217 2003-06-25
AU2003903217A AU2003903217A0 (en) 2003-06-25 2003-06-25 Cosmos
AU2003903804A AU2003903804A0 (en) 2003-07-23 2003-07-23 Cosmos
AU2003903804 2003-07-23
AU2003904403A AU2003904403A0 (en) 2003-08-15 2003-08-15 Cosmos
AU2003904403 2003-08-15
AU2003904347 2003-08-15
AU2003904347A AU2003904347A0 (en) 2003-08-15 2003-08-15 Cosmos

Publications (1)

Publication Number Publication Date
WO2004029481A1 true WO2004029481A1 (fr) 2004-04-08

Family

ID=32046235

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/AU2003/001273 WO2004029481A1 (fr) 2002-09-30 2003-09-26 Appareil de transmission de puissance

Country Status (2)

Country Link
TW (1) TW200506242A (fr)
WO (1) WO2004029481A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005085596A1 (fr) * 2004-03-08 2005-09-15 Norman Leslie Matthews Mecanisme a mouvement alternatif destine a un moteur a pistons
WO2007025779A2 (fr) * 2005-09-03 2007-03-08 Christoph Schuhwerk Mecanisme a manivelle comprenant un dispositif pour realiser une modification periodique de la longueur de son levier actif
CN104948698A (zh) * 2015-07-01 2015-09-30 李云峰 一种往复-旋转运动转换机构
WO2020053642A1 (fr) * 2019-06-14 2020-03-19 Mellasse Nabil Moteur a combustion interne a train epicycloïdale et a pistons alternatifs

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103234016A (zh) * 2013-05-06 2013-08-07 扬州大学 长幅内摆线机构

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2432197A1 (de) * 1974-07-05 1976-01-22 Herbert Peters Doppelkurbeltriebwerk fuer nicht rotierende kraftmaschinen und kompressoren mit epicykloider geradefuehrung des hubkurbelzapfens vermittels zahnraedereingriff, mit einer doppelt wirkenden durchgehenden schubstange mit 2 in entgegengesetzter richtung wirkenden kolben in gleicher zylinderachse
NL7907922A (nl) * 1979-10-29 1981-06-01 Michel Josef Willem Coenen Rijwiel.
WO1990001647A1 (fr) * 1988-08-02 1990-02-22 Cosimo Sarno Double transmission inversee a bielle et manivelle
EP0386847A2 (fr) * 1989-03-08 1990-09-12 Osamu Nishiyama Mécanisme de manivelle
WO1995030847A1 (fr) * 1994-05-10 1995-11-16 Longwell Japan Co., Ltd. Dispositif a manivelle et dispositif de machine
WO1997026452A1 (fr) * 1996-01-19 1997-07-24 Peter Robert Raffaele Moteur a trois temps
CA2213044A1 (fr) * 1997-10-01 1999-04-01 Dean Christian Josephson Vilebrequin orbital
WO2002029280A1 (fr) * 2000-10-06 2002-04-11 Peter Bortolin Dispositif de transmission d'energie

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2432197A1 (de) * 1974-07-05 1976-01-22 Herbert Peters Doppelkurbeltriebwerk fuer nicht rotierende kraftmaschinen und kompressoren mit epicykloider geradefuehrung des hubkurbelzapfens vermittels zahnraedereingriff, mit einer doppelt wirkenden durchgehenden schubstange mit 2 in entgegengesetzter richtung wirkenden kolben in gleicher zylinderachse
NL7907922A (nl) * 1979-10-29 1981-06-01 Michel Josef Willem Coenen Rijwiel.
WO1990001647A1 (fr) * 1988-08-02 1990-02-22 Cosimo Sarno Double transmission inversee a bielle et manivelle
EP0386847A2 (fr) * 1989-03-08 1990-09-12 Osamu Nishiyama Mécanisme de manivelle
WO1995030847A1 (fr) * 1994-05-10 1995-11-16 Longwell Japan Co., Ltd. Dispositif a manivelle et dispositif de machine
WO1997026452A1 (fr) * 1996-01-19 1997-07-24 Peter Robert Raffaele Moteur a trois temps
CA2213044A1 (fr) * 1997-10-01 1999-04-01 Dean Christian Josephson Vilebrequin orbital
WO2002029280A1 (fr) * 2000-10-06 2002-04-11 Peter Bortolin Dispositif de transmission d'energie

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
DATABASE WPI Week 198125, Derwent World Patents Index; Class Q23, AN 1981-F7414D *

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005085596A1 (fr) * 2004-03-08 2005-09-15 Norman Leslie Matthews Mecanisme a mouvement alternatif destine a un moteur a pistons
WO2007025779A2 (fr) * 2005-09-03 2007-03-08 Christoph Schuhwerk Mecanisme a manivelle comprenant un dispositif pour realiser une modification periodique de la longueur de son levier actif
WO2007025779A3 (fr) * 2005-09-03 2007-05-03 Christoph Schuhwerk Mecanisme a manivelle comprenant un dispositif pour realiser une modification periodique de la longueur de son levier actif
CN104948698A (zh) * 2015-07-01 2015-09-30 李云峰 一种往复-旋转运动转换机构
CN104948698B (zh) * 2015-07-01 2017-06-09 李云峰 一种往复‑旋转运动转换机构
WO2020053642A1 (fr) * 2019-06-14 2020-03-19 Mellasse Nabil Moteur a combustion interne a train epicycloïdale et a pistons alternatifs
US11732641B2 (en) 2019-06-14 2023-08-22 Nabil Mellasse Internal combustion engine with an epicyclic gear train and reciprocating pistons

Also Published As

Publication number Publication date
TW200506242A (en) 2005-02-16

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