WO2011083958A2 - Transmission à changement de vitesses continu - Google Patents

Transmission à changement de vitesses continu Download PDF

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Publication number
WO2011083958A2
WO2011083958A2 PCT/KR2011/000044 KR2011000044W WO2011083958A2 WO 2011083958 A2 WO2011083958 A2 WO 2011083958A2 KR 2011000044 W KR2011000044 W KR 2011000044W WO 2011083958 A2 WO2011083958 A2 WO 2011083958A2
Authority
WO
WIPO (PCT)
Prior art keywords
gear
shaft
planetary
coupled
planetary gear
Prior art date
Application number
PCT/KR2011/000044
Other languages
English (en)
Korean (ko)
Other versions
WO2011083958A9 (fr
WO2011083958A3 (fr
Inventor
조광호
Original Assignee
Jo Koang Ho
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 Jo Koang Ho filed Critical Jo Koang Ho
Priority to CN2011800126220A priority Critical patent/CN102906454A/zh
Publication of WO2011083958A2 publication Critical patent/WO2011083958A2/fr
Publication of WO2011083958A9 publication Critical patent/WO2011083958A9/fr
Publication of WO2011083958A3 publication Critical patent/WO2011083958A3/fr

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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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/724—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously using external powered electric machines
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears

Definitions

  • the present invention relates to a continuously variable transmission. More specifically, the continuously variable transmission allows variable speed high, medium and low speeds to be variably performed by a control gear using the principle of the lever under the input and output gears. Relates to a device.
  • the driving force for driving the vehicle comes from an internal combustion engine that produces a large force at a small size, but has a small variation in the maximum torque range and the rotational force of the engine at the medium speed is maximized.
  • the transmission has been developed to use efficiently and maximize the range of change in torque range.
  • the transmission is divided into manual transmission, automatic transmission, continuously variable transmission, etc.
  • the manual transmission is designed to accelerate and decelerate by gear ratio by arranging the main shaft and the sub-axis in parallel and equipped with a plurality of gears. There is a hassle to shift to fit.
  • the automatic transmission which enables the shifting operation to be automatically performed by the action of the fluid clutch and the planetary gear, has a low fuel consumption rate and a complicated structure, so that the gear stage is designated as in the manual transmission, and a shifting shock occurs during shifting.
  • the continuously variable transmission having the function of an ideal transmission has a poly-type structure in which the transmission medium is a belt and a disk-type structure in which the transmission medium is a roller, and does not endure large torque and has a weak durability.
  • the present invention has been made to solve the above problems of the prior art, the input unit and the output unit is composed of a combination of a plurality of gears, by applying the principle of the lever to the controller gear provided at the portion connected to the output unit from the input unit
  • the purpose of the present invention is to provide a continuously variable transmission that can change a high speed, a medium speed, and a low speed by varying the speed.
  • the input shaft to which the rotational force is transmitted from the outside, the first spur gear built on the input shaft, the first bevel gear built on the first spur gear, the shaft is coupled to the input shaft and coupled at right angles
  • Second and third bevel gears which are installed at both sides of the shaft and meshed with the first bevel gear at right angles, are coupled to both ends of the shaft and have a lower portion fixed to an upper surface of the first spur gear, on the shaft.
  • a fourth bevel gear coupled to the second bevel gear and perpendicularly engaged with the second and third bevel gears, an input unit coupled to the shaft and having a first spur gear integrally coupled with the fourth bevel gear;
  • a continuously variable transmission including a variable control unit comprising a coupling gear meshed with the first spur gear, a low speed side control gear meshed with the coupling gear and a high speed side control gear meshing with the first spur gear.
  • the shaft has a through hole through which the input shaft is coupled to the center is formed, the bearing is coupled to the through hole is orthogonal to the input shaft, it characterized in that the rotation is crossed in the rotational direction of the input shaft.
  • the low speed side control gear and the high speed side control gear are connected to The low speed side control gear and the high speed side control gear
  • a casing having gear teeth formed on its outer circumference and a ring groove formed on its inner circumferential surface
  • a bracket which is hinge-coupled to a plurality of control rollers inscribed in an annular groove of the casing at an end of a plurality of branched supports and inserted into the casing;
  • a control lever having an actuator coupled to a horizontal portion coupled to the center of the bracket and a vertical portion bent from the horizontal portion.
  • FIG. 1 is a view showing the overall configuration of a continuously variable transmission according to a first embodiment of the present invention
  • FIG. 2 is a view showing the power flow in the rotation of the 'high speed gear train' in the continuously variable transmission according to the first embodiment of the present invention
  • FIG 3 is a view showing the power flow during the rotation of the 'low gear train' in the continuously variable transmission according to the first embodiment of the present invention.
  • Figure 4 is a view showing a 'variable control unit' in a continuously variable transmission according to a first embodiment of the present invention.
  • 5 to 7 are views showing the operating state of the second control lever according to the variation of the 'variable point' in the continuously variable transmission apparatus according to the first embodiment of the present invention.
  • FIG. 8 is a view showing the overall configuration of a continuously variable transmission according to a second embodiment of the present invention.
  • FIG. 9 is a view showing the power flow in the rotation of the 'high speed gear train' in the continuously variable transmission according to the second embodiment of the present invention.
  • FIG 10 is a view showing the power flow during the rotation of the 'low speed gear train' in the continuously variable transmission according to the second embodiment of the present invention.
  • FIG. 11 is a plan view showing the overall configuration of a continuously variable transmission according to a second embodiment of the present invention.
  • FIG. 12 is a perspective view showing the overall configuration of a continuously variable transmission according to a second embodiment of the present invention.
  • FIG. 13 is a plan view showing the entire configuration of a continuously variable transmission according to a third embodiment of the present invention.
  • FIG. 14 is a plan view showing the overall configuration of a continuously variable transmission according to a fifth embodiment of the present invention.
  • T Variable control unit 2: Input shaft
  • FIG. 1 is a view showing the overall configuration of the continuously variable transmission according to the first embodiment of the present invention
  • Figure 2 shows the power flow during the rotation of the 'high speed gear train' in the continuously variable transmission according to the first embodiment of the present invention
  • Figure 3 is a view showing the power flow during the rotation of the 'low speed gear train' in the continuously variable transmission according to the first embodiment of the present invention.
  • An input unit I receiving external rotational power
  • An output unit (O) for shifting the power of the input unit (I) to output it to the outside;
  • variable control unit (T) for reducing the excessively input rotational force.
  • the input unit I is a first input unit
  • a first planetary gear carrier 220d having an input shaft 2 to which rotational force is transmitted from the outside and having planetary gears 222d respectively mounted on a plurality of branching shafts formed at the outer periphery of the other side;
  • a first shaft 227d coupled to the center of the first ring gear 223d and having a first sun gear 226d engaged with the planetary gear 222d at one end thereof, and having a seventh gear 228d at the other end thereof; It is configured to include.
  • the first planetary gear carrier 220d has a disc shape, and a plurality of branching shafts are formed at one edge thereof, and the planetary gear 222d is coupled to the branching shaft, and the first planetary gear carrier 220d is also rotatable.
  • the planetary gear 222d is also rotatable.
  • the first ring gear 223d has a disk shape having a diameter larger than that of the first planetary gear carrier 220d, and a round jaw is formed at an edge thereof, and a tooth is formed on an inner circumferential surface of the round jaw.
  • the first sun gear 226d is formed on the first shaft 227d coupled to the center of the first planetary gear carrier 220d and the first ring gear 223d, and the planetary gear is formed inside the first ring gear 223d. By engaging with 222d, power can be transmitted to the first shaft 227d.
  • a second ring gear 32d having a second gear 322d to which the first gear 225d is meshed on one side and a tooth formed on an inner circumferential surface of the other side;
  • a second planetary gear having a plurality of planetary gears 342d engaged with the inner circumferential surface of the second ring gear 32d is formed on one side and a third gear 343d formed with the seventh gear 228d on the other side.
  • a second sun gear 362d is coupled to penetrate through the centers of the second ring gear 32d and the second planetary gear carrier 34d and meshes with the planetary gear 342d of the second planetary gear carrier 34d.
  • Figure 4 is a view showing a 'variable control unit' in the continuously variable transmission apparatus according to the first embodiment of the present invention.
  • variable control unit T The variable control unit T,
  • a first control lever T2 eccentrically coupled to the control gear T1 and vertically moving;
  • Support member (T4) is coupled to the lower side of the second control lever (T3) to control the rotation angle of the seesaw movement
  • variable control part T is for reducing the excessive rotational force of the input part I, and by changing the position of the supporting member T4 (hereinafter referred to as 'variable point'), the second control lever T3 is based on the principle of the lever. It is possible to vary the rotation angle of the seesaw motion of a large or small, and by absorbing the variation of the rotation angle in the resistance generating means (T5) it is possible to reduce the excessive rotational force.
  • the resistance generating means T5 generates elastic resistance or fluid resistance, and examples thereof include a spring, a cylinder, a pump, and the like.
  • 5 to 7 are views showing the operating state of the second control lever according to the variation of the 'variable point' in the continuously variable transmission apparatus according to the first embodiment of the present invention.
  • variable point is located at the right end of the second control lever T3.
  • the strong output generated by the second control lever T3 is decelerated by the resistance generating means T5, thereby reducing the rotational force of the first control lever T2 and the controller gear T1. That is, in this case, the deceleration by the resistance generating means T5 may be abruptly shortened.
  • the positional change of the support member T4 is enabled by the operation of the actuator controlled by the controller, and the resistance setting of the resistance generating means T5 can also be set by the controller.
  • the operation of the actuator is performed by a controller (not shown), and since such a control scheme is well known to those skilled in the art, a detailed description thereof will be omitted.
  • the third gear 343d and the second ring gear 32d engaged with the seventh gear 228d are rotated, and the second shaft 36d and the fourth gear 38d are rotated through the second sun gear 362d. Since it is made, the output shaft 3 is output by the rotation of the fifth gear 382d meshed with the fourth gear 38d, and the generator is driven by this output.
  • the first gear 225d is decelerated by this deceleration operation to decelerate the rotational force of the output unit O driven thereon. You can do it.
  • the first gear 225d engaged with it is decelerated by the deceleration of the controller gear T1
  • the second gear 322d of the second ring gear 32d is rotated
  • the second sun gear 362d is rotated.
  • the rotational force is transmitted to the output shaft 3 through the fourth gear 38d and the fifth gear 382d.
  • FIG 8 is a view showing the overall configuration of the continuously variable transmission according to the second embodiment of the present invention
  • Figure 9 shows the power flow during the rotation of the 'high speed gear train' in the continuously variable transmission according to the second embodiment of the present invention
  • 10 is a view showing the power flow during the rotation of the 'low gear train' in the continuously variable transmission according to the second embodiment of the present invention.
  • An input unit I receiving external rotational power
  • An output unit (O) for shifting the power of the input unit (I) to output it to the outside;
  • variable control unit (T) for reducing the excessively input rotational force.
  • the input unit I is a first input unit
  • a first planetary gear carrier 220e having an input shaft 2 to which rotational force is transmitted from the outside and having planetary gears 222e respectively mounted on a plurality of branching shafts formed at the outer periphery of the other side;
  • a first shaft 227e coupled to the center of the first ring gear 223e and having a first sun gear 226e engaged with the planetary gear 222e at one end thereof, and having a shaft gear 228e at the other end thereof;
  • a second shaft 42e having a fourth gear 424e engaged with the shaft gear 228e and having a fifth gear 425e formed at the other end thereof;
  • a third shaft 43e having a second gear 432e engaged with the first gear 225e and having a third gear 433e at the other end thereof;
  • a second ring gear 32e having a seventh gear 327e engaged with the third gear 433e on one side and a gear formed on an inner circumferential surface of the other side;
  • a plurality of planetary gears 342e meshed with the inner circumferential surface of the second ring gear 32e is formed at one side, and a sixth gear 366e meshed with the fifth gear 425e of the input unit I is formed at the other side.
  • An output shaft 3 which is coupled through a center of the second ring gear 32e and the second planetary gear carrier 34e and has a second sun gear 362e engaged with the planetary gear 342e on one side; It is configured to include.
  • variable controller T is the same as the variable controller of the first embodiment described above, repeated description thereof will be omitted.
  • FIG 11 is a plan view showing the entire configuration of a continuously variable transmission according to a second embodiment of the present invention
  • Figure 12 is a perspective view showing the overall configuration of a continuously variable transmission according to a second embodiment of the present invention.
  • An input unit (I) installed in the housing 500 and receiving external rotational power
  • An output unit (O) installed in the housing (500) to shift the power of the input unit (I) and output it to the outside;
  • Power transmission means for connecting the input unit (I) and output unit (O)
  • the input unit I is a first input unit
  • the low gear train (L) is
  • the planetary gear carrier 220a having the input shaft 2 formed on one side and having a plurality of branched shafts 221a on the other side,
  • a ring gear 223a coupled to the outer side of the planetary gear carrier 220a and having a gear 224a on the inner circumferential surface to which the planetary gear 222a is engaged, and having a first gear 225a formed at the outer center thereof;
  • An input planetary gear part 22a configured to be coupled through a center of the ring gear 223a and having a shaft 227a coupled to a sun gear 226a engaged with the planetary gear 222a at one end thereof;
  • a fluid pump 42a having a first connecting gear 41a meshed with the first gear 225a, a fluid supply part 44a for supplying and recovering a fluid to the fluid pump 42a, and the fluid supply part
  • a load generation device 4a constituted by a control unit for controlling driving of the 44a;
  • the input shaft (2a) is coupled to the wind power propeller (not shown) exposed to the outside.
  • the rotational force of the propeller becomes excessive, and when the rotational force flows into the input side planetary gear 222a through the input shaft 2a, the high speed gear train H may be damaged by excessive rotational speed.
  • the load generating device 4 is driven to decelerate the overspeed state at an appropriate rotational speed.
  • the load generating device 4 generates a load on the first connecting gear 41a by supplying a fluid to the fluid pump 42 according to a signal from the controller, thereby reducing the rotational force by half.
  • a high speed gear train (H) connected to the input unit (I) and receiving a high speed rotational force
  • It includes an output shaft (3a) for receiving the rotational force of the high-speed gear train (H) to supply to the generator.
  • the high speed gear train (H) is
  • a third gear 5a coupled to the other end of the shaft 227a;
  • a second connecting gear 6a meshed with the third gear 5a;
  • a fourth gear 75a meshed with the second connecting gear 6a is formed outside, and a ring gear 71a having a gear portion formed on an inner circumferential surface thereof;
  • a plurality of planetary gears 72a meshed with the gears of the inner circumferential surface of the ring gear 71a;
  • the sixth gear 76a meshed with 41a);
  • the planetary gear part 7a of the output side composed of a planetary gear carrier 77a having an output shaft 3a connected to a generator and connected to a generator at one end of the planetary gear 72a.
  • the planetary gear 72a, the sun gear 73a, and the planetary gear carrier 77a are output to the output shaft 3a, and the generator is driven by this output.
  • the rotational force input at an excessive speed is transmitted to the sixth gear 76a through the first connecting gear 41a and then to the sixth gear 76a through the shaft 74a after decelerating to the appropriate rotational force in the load generating device 4 as described above.
  • the engaged fifth connection gear 75a is rotated, and the output is doubled by the force of rotating the planetary gear carrier 71a and the planetary gear 72a connected thereto.
  • FIG. 13 is a plan view showing the overall configuration of a continuously variable transmission according to a third embodiment of the present invention.
  • the continuously variable transmission A4 according to the fourth embodiment of the present invention is a continuously variable transmission A4 according to the fourth embodiment of the present invention.
  • An input unit (I) installed in the housing 500 and receiving external rotational power
  • An output unit (O) installed in the housing (500) to shift the power of the input unit (I) and output it to the outside;
  • the input unit I is a first input unit
  • the low gear train (L) is
  • the planetary gear carrier 220b having the planetary gear 222b coupled to one side and having an eleventh gear 225b formed at the other side thereof,
  • An input planetary gear part 22b formed at one end of the shaft 227b penetratingly coupled to the center of the planetary gear carrier 220b and composed of a sun gear 226b engaged with the planetary gear 222b;
  • a high speed gear train (H) connected to the input unit (I) and receiving a high speed rotational force
  • It includes an output shaft (3b) for receiving the rotational force of the high-speed gear train (H) to supply to the generator.
  • the high speed gear train (H) is
  • a twelfth gear 5b coupled to the other end of the shaft 227b;
  • a planetary gear carrier 77b having a thirteenth gear 75b meshed with the second connection gear 6b on one side and a plurality of planetary gears 72b coupled to the other side;
  • a ring gear 71b having a gear portion formed on an inner circumferential surface thereof to be engaged with the planetary gear 72b and having an output shaft 3b formed on the other side thereof;
  • the output side planetary gear part 7b which consists of the 14th gear 76b meshed with 41b is comprised.
  • the first connecting gear 41b meshed with the eleventh gear 225b is rotated, which is decelerated to an appropriate rotational force by the operation of the load generating device 4b.
  • the sun gear 73b is rotated by the rotation of the fourteenth gear 76b connected to the first connecting gear 41b to rotate the planetary gear 72b, thereby doubling the output.
  • FIG. 14 is a plan view showing the entire configuration of a continuously variable transmission according to a fifth embodiment of the present invention.
  • the continuously variable transmission A5 according to the fifth embodiment of the present invention is a continuously variable transmission A5 according to the fifth embodiment of the present invention.
  • An input unit (I) installed in the housing 500 and receiving external rotational power
  • An output unit O installed in the housing 500 to shift the power of the input unit I and output the output to the outside.
  • the input unit I is a first input unit
  • the low gear train (L) is
  • a planetary gear carrier 220c having a plurality of branching shafts 221c coupled to a plurality of planetary gears 222c engaged with the sun gear 226c and having a shaft 227c formed at the center of the other side.
  • a gear 224c is formed on an inner circumferential surface of the planetary gear 222c so that the planetary gear 222c is engaged with the ring gear 223c coupled to the outer side of the planetary gear carrier 220c.
  • An input planetary gear part 22c including a twenty-first gear 225c formed at the center of the other side of the ring gear 223c;
  • a high speed gear train (H) connected to the input unit (I) and receiving a high speed rotational force
  • It includes an output shaft (3c) for receiving the rotational force of the high-speed gear train (H) to supply to the generator.
  • the high speed gear train (H) is
  • a second connecting gear 6c meshed with the 22nd gear 5c;
  • a planetary gear carrier 77c having a twenty-third gear 75c meshed with the second connection gear 6c and having a plurality of planetary gears 72c coupled to the other side;
  • a ring gear 71c having a gear portion formed on an inner circumferential surface thereof so as to be engaged with the planetary gear 72c;
  • a shaft 74c having one end connected to the planetary gear carrier 77c and coupled through a ring gear 71c and having a twenty-fourth gear 76c engaged with the first connection gear 41c at the other end thereof; And an output side planetary gear portion 7c composed of a sun gear 73c meshed with the planetary gear 72c and connected to the output shaft 3c.
  • the first connecting gear 41c meshed with the twenty-first gear 225c is rotated, which is decelerated to an appropriate rotational force by the operation of the load generating device 4c.
  • the twenty-fourth gear 76c engaged with the first connection gear 41c is rotated, the shaft 74c connected thereto is rotated, and the planetary gear carrier 77c connected to the other side of the shaft 74c is rotated to form a planet.
  • the rotational force is transmitted to the gear 72c, and the rotational force of the planetary gear 72c is transmitted to the sun gear 73c and transmitted to the output shaft 3c, so the output can be doubled.
  • the input side and the output side are composed of a plurality of gears, and by applying the principle of the lever to the controller gear installed at the portion connected from the input side to the output side, it is possible to produce a large force with a small force, high, medium and low speed. There is an effect that can easily change the speed change of.

Abstract

La présente invention a trait à une transmission à changement de vitesses continu qui effectue de façon variable des opérations de changement de vitesses entre une vitesse faible, une vitesse moyenne et une vitesse élevée au moyen d'un dispositif de commande de la boîte de vitesses utilisant le principe du levier dans une condition dans laquelle un rapport de vitesse en entrée et un rapport de vitesse en sortie sont mis en prise en continu l'un avec l'autre. La transmission à changement de vitesses continu selon la présente invention comprend : un logement (500) ; un périphérique d'entrée (I) agencé à l'intérieur du logement (500) de manière à recevoir une puissance de rotation provenant d'une source extérieure ; un périphérique de sortie (O) agencé à l'intérieur du logement (500) de manière à transmettre la puissance provenant du périphérique d'entrée (I) et à fournir en sortie la puissance transmise vers l'extérieur ; et une unité de commande variable intercalée entre le périphérique d'entrée (I) et le périphérique de sortie (O) de manière à commander l'accélération/la décélération. Selon la présente invention, l'entrée et la sortie sont constituées par des combinaisons d'une pluralité de rapports de vitesse et le principe du levier est appliqué au dispositif de commande de la boîte de vitesses disposé dans la partie connectée à partir de l'entrée jusqu'à la sortie de sorte que le dispositif de commande de la boîte de vitesses peut tourner rapidement grâce à une faible quantité de force et les opérations de changement de vitesses entre une vitesse faible, une vitesse moyenne et une vitesse élevée peuvent être facilement effectuées.
PCT/KR2011/000044 2010-01-05 2011-01-05 Transmission à changement de vitesses continu WO2011083958A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN2011800126220A CN102906454A (zh) 2010-01-05 2011-01-05 无级变速装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1020100000311A KR101134032B1 (ko) 2010-01-05 2010-01-05 무단 변속장치
KR10-2010-0000311 2010-01-05

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WO2011083958A2 true WO2011083958A2 (fr) 2011-07-14
WO2011083958A9 WO2011083958A9 (fr) 2011-12-01
WO2011083958A3 WO2011083958A3 (fr) 2012-01-19

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KR (1) KR101134032B1 (fr)
CN (1) CN102906454A (fr)
WO (1) WO2011083958A2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101499936B1 (ko) 2013-07-30 2015-03-18 이춘우 무단변속기
CN105003632B (zh) * 2015-07-10 2017-07-18 席昊 一种机械直接无级变速器
CN108266499A (zh) * 2016-12-31 2018-07-10 吴方平 一种车辆变速器

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002039289A (ja) * 2000-07-24 2002-02-06 Hideo Sato 無段変速機
KR100469839B1 (ko) * 2002-07-16 2005-02-02 조광호 기어식 무단 변속 장치
KR100899635B1 (ko) * 2008-03-18 2009-05-27 최태수 무단 변속장치

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Publication number Priority date Publication date Assignee Title
CN2177130Y (zh) * 1993-04-01 1994-09-14 石玉山 行星齿轮无级变速器
JPH0874966A (ja) * 1994-06-30 1996-03-19 Kenji Shionoya 無段変速装置
CN2738039Y (zh) * 2004-10-29 2005-11-02 北京市无极通汽车系统技术有限公司 机械式无极自动变速的传动装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002039289A (ja) * 2000-07-24 2002-02-06 Hideo Sato 無段変速機
KR100469839B1 (ko) * 2002-07-16 2005-02-02 조광호 기어식 무단 변속 장치
KR100899635B1 (ko) * 2008-03-18 2009-05-27 최태수 무단 변속장치

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Publication number Publication date
KR20110080203A (ko) 2011-07-13
CN102906454A (zh) 2013-01-30
WO2011083958A9 (fr) 2011-12-01
KR101134032B1 (ko) 2012-04-13
WO2011083958A3 (fr) 2012-01-19

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