WO2016112802A1 - Convertisseur de couple hydraulique réglable composite et transmission variable en continu - Google Patents

Convertisseur de couple hydraulique réglable composite et transmission variable en continu Download PDF

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Publication number
WO2016112802A1
WO2016112802A1 PCT/CN2016/070211 CN2016070211W WO2016112802A1 WO 2016112802 A1 WO2016112802 A1 WO 2016112802A1 CN 2016070211 W CN2016070211 W CN 2016070211W WO 2016112802 A1 WO2016112802 A1 WO 2016112802A1
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WIPO (PCT)
Prior art keywords
input
gear
output
carrier
coupled
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Application number
PCT/CN2016/070211
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English (en)
Chinese (zh)
Inventor
吴志强
Original Assignee
吴志强
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Filing date
Publication date
Application filed by 吴志强 filed Critical 吴志强
Priority to CN201680004313.1A priority Critical patent/CN107250616A/zh
Publication of WO2016112802A1 publication Critical patent/WO2016112802A1/fr

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    • 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
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
    • F16H47/08—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • 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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers
    • 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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H2057/087—Arrangement and support of friction devices in planetary gearings, e.g. support of clutch drums, stacked arrangements of friction devices

Definitions

  • the invention belongs to the field of torque converters and shifting, and more particularly to a composite adjustable torque converter and a continuously variable transmission for various ground vehicles, ships, railway locomotives and machine tools.
  • the torque converter is designed according to the principles of hydrostatics, etc. It can transmit little power and is not efficient; in addition, the cost is high.
  • the invention overcomes the deficiencies of the prior art, and provides a compound adjustable hydraulic torque converter and a continuously variable transmission which have the advantages of shortening the service life of the engine, simple structure, convenient operation, low cost, energy saving and high efficiency.
  • a compound adjustable hydraulic torque converter comprising an input shaft (1), an output shaft (3), a coupling gear (4), an overrunning clutch (5), an adjustable hydraulic torque converter (6), an input gear In the sub (7), a planetary gear (20), an output carrier (21), a fixed ring gear (22), an input gear (23), and an outer portion are disposed between the input shaft (1) and the output shaft (3).
  • the planet carrier (21) is coupled to the input pinion (25), and the outer meshing planet carrier (24) cooperates with the input pinion (25) and the input large gear (26) through the planetary gear (20) thereon, and the external meshing planet
  • the frame (24) is coupled with the input small ring gear (28), and the inner meshing planet carrier (27) cooperates with the input small ring gear (28) and the input large ring gear (29) through the planetary gear (20) thereon.
  • the meshing planet carrier (27) is coupled to the output shaft (3), and the input large ring gear (29) and the input The large gear (26) and the coupling gear (4) are coupled, the coupling gear (4) and the output end (52) of the overrunning clutch (5) are coupled to the output end (62) of the adjustable torque converter (6), The input end (61) of the liquid torque converter (6) is coupled to the output gear (72) of the input gear pair (7), the input pinion (23) and the input gear (71) of the input gear pair (7) are The input shaft (1) is connected.
  • a continuously variable transmission of a compound adjustable torque converter comprising an input shaft (1), an output shaft (3), an adjustable hydraulic torque converter (4), an overrunning clutch (5), and an input gear pair ( 6), the output gear pair (7), between the input shaft (1) and the output shaft (3) is provided with a planetary gear (20), a fixed planet carrier (21), an input pinion (22), and a large output.
  • Gear (23), input carrier (24), coupling gear (25), output ring gear (26), coupling pinion (27), external mesh carrier (28), coupling large gear (29), output carrier (30), input ring gear (31), input gear (32), fixed planet carrier (21) through the planetary gear (20) on it and the input pinion (22), the output gear (23) work together, fixed
  • the carrier (21) and the input end (51) of the overrunning clutch (5) are coupled to the fixed element, the output large gear (23) is coupled to the coupling gear (25), and the coupling gear (25) is passed through the input carrier (24)
  • the planetary gear (20) cooperates with the input carrier (24) and the output ring gear (26), the output ring gear (26) is coupled with the coupling pinion (27), and the coupling pinion (27) is passed through the external mesh carrier (28).
  • the input gear (32) cooperates, the output carrier (30) is coupled with the output shaft (3), the input gear (32), the input pinion (22), and the input gear of the output gear pair (7) (71) ) is coupled to the input shaft (1), the output gear (72) of the output gear pair (7) is coupled to the input end (41) of the adjustable torque converter (4), and the adjustable torque converter (4)
  • the output end (42) is coupled to the output end (52) of the overrunning clutch (5) and the input gear (61) of the input gear pair (6), and the input gear (62) of the input gear pair (6) is coupled to the input carrier ( 24) Coupling, the input planet carrier (24) is coupled to the coupling bull gear (29).
  • the components that need to be coupled may be directly connected.
  • the method of coupling a shaft, a hollow or a coupling frame may be adopted, and may be connected through or across several other components; when the coupled component is When the gears or ring gears are engaged or coupled with each other, the components that do not need to be coupled can be rotated relative to each other.
  • the gear ratios of the gear pairs and the shifting mechanism are designed according to actual needs.
  • the torque converter can be replaced by a fluid coupling, a pressure motor and a hydraulic pump, and an electromagnetic clutch.
  • the present invention When the present invention is applied to a vehicle, it is possible to automatically change the output torque and the speed change depending on the magnitude of the resistance that the vehicle is subjected to while traveling.
  • the invention makes the engine and the starter operate in the economic speed region, that is, the engine works in the range of the very small pollution discharge speed, and avoids the engine discharging a large amount of exhaust gas during the idle speed and high speed operation, thereby reducing the exhaust gas. Emissions are conducive to protecting the environment;
  • the invention can utilize the effect of internal speed difference to buffer and overload protection, which is beneficial to prolonging the service life of the engine and the transmission system and the starter.
  • speed up which is beneficial to improve the driving performance of the vehicle;
  • the invention makes the input power uninterrupted, can ensure the vehicle has good acceleration and high average speed, reduces the wear of the engine, prolongs the overhaul interval mileage, and is beneficial to improving productivity.
  • the present invention is a composite adjustable hydraulic torque converter and a continuously variable transmission for various ground vehicles, ships, railway locomotives, and machine tools.
  • FIG. 1 is a structural view of a first embodiment of the present invention
  • FIG. 2 is a structural view of a second embodiment of the present invention
  • the connection between two components in the drawing uses a thick solid line to indicate a fixed connection, and a thin solid line indicates The two elements can be rotated relative to each other.
  • Embodiment 1 is a diagrammatic representation of Embodiment 1:
  • a composite adjustable torque converter includes an input shaft 1, an output shaft 3, a coupling gear 4, and a transcendental a clutch 5, an adjustable torque converter 6, an input gear pair 7, between the input shaft 1 and the output shaft 3, a planetary gear 20, an output carrier 21, a fixed ring gear 22, an input gear 23, and an outer
  • the input gear 23 cooperates
  • the fixed ring gear 22 and the input end 51 of the overrunning clutch 5 are coupled to the fixed element
  • the output carrier 21 is coupled to the input pinion 25, and the outer gear carrier 24 passes the planetary gear 20 and the input pinion 25,
  • the input large gear 26 cooperates
  • the outer meshing planet carrier 24 is coupled with the input small ring gear 28, and the inner meshing planet carrier 27 cooperates with the input small ring gear 28 and the input large ring gear 29 through the planetary
  • the meshing carrier 27 is coupled to the output shaft 3, the input large ring gear 29 is coupled to the input bull gear 26 and the coupling gear 4, the coupling gear 4 and the output 52 of the overrunning clutch 5 and the output 62 of the adjustable torque converter 6 Coupling, input 61 of the adjustable torque converter 6
  • the output gear 72 of the gear pair 7 is coupled, the input pinion 23 and the input gear 71 of the input gear pair 7 is coupled with the input shaft 1.
  • the input pinion 25 and the input bull gear 26 fuse the power transmitted thereto through the planetary gears 20 on the external meshing carrier 24 to the external meshing carrier 24, and the external meshing carrier 24 is transmitted to the input small ring gear 28, and the input is small.
  • the ring gear 28, the input large ring gear 29, and the power transmitted thereto by the planetary gears 20 on the internal meshing carrier 27 are merged with the internal meshing planet carrier 27.
  • the two power flows will vary according to the change of the rotational speed distribution between the two.
  • the input large gear 26 and the input large ring gear 29 have a rotational speed of zero
  • the external meshing carrier 24 The internal meshing carrier 27 is reduced in speed, and when the input large gear 26 and the input large ring gear 29 are continuously increased in speed, the rotational speeds of the external meshing carrier 24 and the internal meshing carrier 27 also increase. That is, when the rotational speed of the input large gear 26 and the input large ring gear 29 changes, the rotational speeds of the external meshing carrier 24, the internal meshing carrier 27, and the output shaft 3 also change.
  • the input power is divided into two paths through the input shaft 1, one through the input gear pair 7, the torque converter 6 and the coupling gear 4, and then transmitted to the input large ring gear 29, the input large gear 26; the other is transmitted to the input
  • the pinion gear 23, the input pinion gear 23 transmits power to the output carrier 21 through the planetary gears 20 on the output carrier 21, the output carrier 21 is transmitted to the input pinion 25, the input pinion 25, and the input bull gear 26 pass.
  • the planetary gears 20 on the outer meshing planet carrier 24 converge the power transmitted thereto to the outer meshing planet carrier 24, and the outer meshing planet carrier 24 is transferred to the input small ring gear 28, the small ring gear 28 is input, and the large ring gear 29 is input.
  • the power transmitted thereto is converged to the internal meshing carrier 27 by the planetary gears 20 on the internal meshing carrier 27, and the internal meshing carrier 27 is transmitted to the output shaft 3, thereby realizing the external output of the engine power through the output shaft 3. .
  • the torque on the external meshing carrier 24, the internal meshing carrier 27, and the output shaft 3 varies with the change of the rotational speed thereof, and the lower the rotational speed, the transmission to the external meshing carrier 24
  • the torque on the inner meshing carrier 27 and the output shaft 3 is larger, and conversely, the smaller, in the process, the adjustable torque converter 6 also acts as a torque converter, thereby realizing the invention with the vehicle.
  • a compound adjustable torque converter that changes torque and speed with different running resistance.
  • the input power, the input rotational speed and the load of the engine are constant, that is, the rotational speed and torque of the input shaft 1 are constant, and before the vehicle starts, the rotational speed of the output shaft 3 is zero, and the input power of the engine passes through the input shaft 1 And transmitted to the input pinion 23, and then the power is transmitted to the output carrier 21 through the planetary gears 20 on the output carrier 21, and then transmitted to the input pinion 25, wherein there is no or relatively little power inflow input at this time.
  • the gear 26 is input to the large ring gear 29, and the input end 51 of the overrunning clutch 5 is coupled with the fixed element to restrict the steering, so that the steering of the input large gear 26 and the input large ring gear 29 cannot be opposite to the input steering, and the rotation speed is Zero, at this time, the power delivered to the input pinion 25,
  • the power is transmitted to the outer meshing planet carrier 24 via the planet gears 20 on the outer meshing planet carrier 24, the outer meshing planet carrier 24 is transferred to the input small ring gear 28, and the input small ring gear 28 is passed through the inner mesh planet carrier 27.
  • the planetary gear 20 transmits power to the internal meshing carrier 27 and then to the output shaft 3.
  • Embodiment 2 is a diagrammatic representation of Embodiment 1:
  • a continuously variable transmission of a composite adjustable torque converter includes an input shaft 1, an output shaft 3, an adjustable hydraulic torque converter 4, an overrunning clutch 5, an input gear pair 6, An output gear pair 7, between the input shaft 1 and the output shaft 3, a planetary gear 20, a fixed carrier 21, an input pinion 22, an output bull gear 23, an input carrier 24, a coupling gear 25, and an output ring gear are disposed.
  • the coupling pinion 27 the outer meshing carrier 28, the coupling large gear 29, the output carrier 30, the input ring gear 31, the input gear 32, the planetary carrier 20 and the input pinion 22 through which the carrier 21 is fixed, and the output
  • the large gear 23 cooperates, the fixed carrier 21 and the input end 51 of the overrunning clutch 5 are coupled to the fixed element, the output large gear 23 is coupled to the coupling gear 25, and the coupling gear 25 is passed through the planetary gear 20 and the input carrier on the input carrier 24.
  • the output ring gear 26 cooperates, the output ring gear 26 is coupled with the coupling pinion 27, and the coupling pinion 27 cooperates with the external meshing carrier 28 and the coupling large gear 29 through the planetary gear 20 on the external meshing carrier 28, Engage the planet carrier 28 with input teeth
  • the ring 31 is coupled, the input ring gear 31 cooperates with the output carrier 30 and the input gear 32 through the planetary gear 20 on the output carrier 30, the output carrier 30 is coupled with the output shaft 3, the input gear 32, the input pinion 22 and the output
  • the input gear 71 of the gear pair 7 is coupled to the input shaft 1, and the output gear 72 of the output gear pair 7 is coupled to the input end 41 of the adjustable torque converter 4, and the output end 42 of the adjustable torque converter 4 is transposed
  • the output end 52 of the clutch 5 and the input gear 61 of the input gear pair 6 are coupled, the output gear 62 of the input gear pair 6 is coupled to the input carrier 24, and the input carrier 24 is coupled to the coupling large gear 29.
  • the input carrier 24 and the coupling gear 25 pass the power transmitted thereto through the planetary gear 20 on the input carrier 24 to the output ring gear 26, and the output ring gear 26 is transmitted to the coupling pinion 27, the coupling pinion 27, and the coupling is large.
  • the gear 29 then converges the power transmitted thereto through the planet gears 20 on the outer meshing planet carrier 28 to the outer mesh planet carrier 28.
  • the two power flows will change according to the change of the rotational speed distribution between the two.
  • the rotational speed of the input carrier 24 and the coupling large gear 29 is zero, the coupling gear 25 and the connection are small.
  • the gear 27 is reduced in speed, and when the rotational speed of the input carrier 24 and the coupling large gear 29 is continuously increased, the rotational speed of the coupling gear 25 and the coupling pinion 27 also increases, that is, when the input carrier 24 is input.
  • the rotational speed of the coupling large gear 29 changes, the rotational speeds of the output ring gear 26, the external meshing carrier 28, and the output shaft 3 also change.
  • the input power is split into three paths via the input shaft 1, and the first path is output to the input carrier 24 via the output gear pair 7, the torque converter 4, and the input gear pair 6, and then transmitted to the coupled gear 29;
  • the two paths are transmitted to the input pinion 22, and the input pinion 22 transmits power to the output bull gear 23 through the planetary gears 20 on the fixed carrier 21, and the output large gear 23 is transmitted to the coupling gear 25, the coupling gear 25, and the input planet.
  • the frame 24 merges the power transmitted thereto through the planetary gears 20 on the input carrier 24 to the output ring gear 26, and the output ring gear 26 is transmitted to the coupling pinion 27, the coupling pinion 27, the coupling gear 29 and the external meshing.
  • the planetary gears 20 on the planet carrier 28 converge the power transmitted thereto to the external meshing carrier 28, and the external meshing carrier 28 is transmitted to the input ring gear 31; the third path is transmitted to the input gear 32, the input gear 32, and the input teeth.
  • the ring 31 is again passed through the planetary gear 20 on the output carrier 30 to transfer the power sink thereto. Flowing on the output carrier 30, the output carrier 30 is transferred to the output shaft 3, thereby achieving external output of the engine power through the output shaft 3.
  • the torque on the output ring gear 26, the external meshing planet carrier 28, and the output shaft 3 varies with the change of the rotational speed thereof, and the lower the rotational speed is transmitted to the output ring gear 26,
  • the torque on the meshing planet carrier 28 and the output shaft 3 is larger, and conversely, the smaller, in the process, the adjustable torque converter 4 also acts as a torque converter, thereby realizing the driving resistance of the present invention with the vehicle.
  • a continuously variable transmission of a composite adjustable torque converter that varies torque and speed.
  • the input power, the input rotational speed and the load of the engine are constant, that is, the rotational speed and torque of the input shaft 1 are constant, and before the vehicle starts, the rotational speed of the output shaft 3 is zero, and the input power of the engine passes through the input shaft 1 And transmitted to the input pinion 22, and then the power is transmitted to the output bull gear 23 through the planetary gear 20 on the fixed carrier 21, and then transmitted to the coupling gear 25, wherein no power or less is flowed into the input carrier at this time. 24.
  • the large gear 29 is coupled, and the input end 51 of the overrunning clutch 5 is coupled to the fixed component to restrict the steering, so that the steering of the input carrier 24 and the coupling large gear 29 cannot be opposite to the input steering, and the rotational speed is zero.
  • the power transmitted to the coupling gear 25 is transmitted to the output ring gear 26 through the planetary gears 20 on the input carrier 24, the output ring gear 26 is transmitted to the coupling pinion 27, and the coupling pinion 27 is again meshed.
  • the planetary gears 20 on the planet carrier 28 transmit power to the outer meshing planet carrier 28, the outer meshing planet carrier 28 is transferred to the input ring gear 31, the input ring gear 31, the input gear 32 and the input gear 32
  • the planetary gears 20 of the carrier 30 converge the power transmitted thereto to the output carrier 30, and the output carrier 30 is transmitted to the output shaft 3, and the torque transmitted to the output shaft 3 is transmitted to the drive wheels via the transmission system.
  • the traction force is sufficient to overcome the starting resistance of the automobile, the automobile starts and starts to accelerate, and the rotational speed of the output terminal 42 of the adjustable torque converter 4 is gradually increased, and the rotational speed of the input planetary carrier 24 and the coupled large gear 29 is also connected. This is gradually increased, so that the torque of the output ring gear 26, the outer mesh carrier 28, and the output shaft 3 decreases as the number of revolutions increases.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Structure Of Transmissions (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention concerne un convertisseur de couple hydraulique réglable composite. Un porte-satellites de sortie (21) est relié à un pignon d'entrée (25), un porte-satellites à engrènement externe (24) est relié à une petite couronne dentée d'entrée (28), un porte-satellites à engrènement interne (27) est relié à un arbre de sortie (3), une grande couronne dentée d'entrée (29) est reliée à un grand engrenage d'entrée (26) et un engrenage de liaison (4), l'engrenage de liaison (4) et un embrayage de dépassement (5) sont reliés à un convertisseur de couple hydraulique réglable (6), le convertisseur de couple hydraulique réglable (6) est relié à une paire d'engrenages d'entrée (7), et un pignon d'entrée (23) et la paire d'engrenages d'entrée (7) sont reliés à un arbre d'entrée (1). En outre, l'invention concerne également une transmission variable en continu d'un convertisseur de couple hydraulique réglable composite.
PCT/CN2016/070211 2015-01-16 2016-01-06 Convertisseur de couple hydraulique réglable composite et transmission variable en continu WO2016112802A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201680004313.1A CN107250616A (zh) 2015-01-16 2016-01-06 一种复合型可调液力变矩器以及无级变速器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201510021358.7A CN104728384B (zh) 2015-01-16 2015-01-16 一种复合型可调液力变矩器以及无级变速器
CN2015100213587 2015-01-16

Publications (1)

Publication Number Publication Date
WO2016112802A1 true WO2016112802A1 (fr) 2016-07-21

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PCT/CN2016/070211 WO2016112802A1 (fr) 2015-01-16 2016-01-06 Convertisseur de couple hydraulique réglable composite et transmission variable en continu

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CN (4) CN105333090A (fr)
HK (3) HK1211658A1 (fr)
WO (1) WO2016112802A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105333090A (zh) * 2015-01-16 2016-02-17 吴志强 一种复合型可调液力变矩器

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05263906A (ja) * 1990-12-13 1993-10-12 Fuji Heavy Ind Ltd 車両用無段変速機の圧力制御装置
KR20060009190A (ko) * 2004-07-21 2006-01-31 이종완 범위가 확장된 무단변속장치
CN102022503A (zh) * 2009-09-09 2011-04-20 吴志强 一种复合型可调液力变矩器
WO2011093425A1 (fr) * 2010-01-28 2011-08-04 株式会社ユニバンス Dispositif de transmission de puissance
CN102287498A (zh) * 2011-08-05 2011-12-21 南京工程学院 一种行星齿轮无级变速器
CN102297255A (zh) * 2011-08-04 2011-12-28 湖南江麓容大车辆传动股份有限公司 自动变速器总成及自动变速型汽车
CN103953707A (zh) * 2014-05-07 2014-07-30 吴志强 一种复合型可调液力变矩器以及无级变速器
CN104728384A (zh) * 2015-01-16 2015-06-24 吴志强 一种复合型可调液力变矩器以及无级变速器

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Publication number Priority date Publication date Assignee Title
GB1156049A (en) * 1965-11-01 1969-06-25 Inpower Works Ltd Improvements in or relating to Fluid Torque Transmitters.
CN1109615C (zh) * 1997-12-23 2003-05-28 卢克摩擦片和离合器有限公司 变速箱
CN101598198B (zh) * 2008-06-06 2013-06-26 吴志强 一种复合型内锥输出行星锥式无级变速器
CN202091463U (zh) * 2011-05-16 2011-12-28 山推工程机械股份有限公司 一种新型液力变矩器

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05263906A (ja) * 1990-12-13 1993-10-12 Fuji Heavy Ind Ltd 車両用無段変速機の圧力制御装置
KR20060009190A (ko) * 2004-07-21 2006-01-31 이종완 범위가 확장된 무단변속장치
CN102022503A (zh) * 2009-09-09 2011-04-20 吴志强 一种复合型可调液力变矩器
WO2011093425A1 (fr) * 2010-01-28 2011-08-04 株式会社ユニバンス Dispositif de transmission de puissance
CN102297255A (zh) * 2011-08-04 2011-12-28 湖南江麓容大车辆传动股份有限公司 自动变速器总成及自动变速型汽车
CN102287498A (zh) * 2011-08-05 2011-12-21 南京工程学院 一种行星齿轮无级变速器
CN103953707A (zh) * 2014-05-07 2014-07-30 吴志强 一种复合型可调液力变矩器以及无级变速器
CN104728384A (zh) * 2015-01-16 2015-06-24 吴志强 一种复合型可调液力变矩器以及无级变速器
CN105333090A (zh) * 2015-01-16 2016-02-17 吴志强 一种复合型可调液力变矩器

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Publication number Publication date
CN104728384A (zh) 2015-06-24
CN104728384B (zh) 2016-03-16
HK1222438A1 (zh) 2017-06-30
CN105333090A (zh) 2016-02-17
HK1211658A1 (zh) 2016-05-27
HK1216339A1 (zh) 2016-11-04
CN107250616A (zh) 2017-10-13
CN105402352A (zh) 2016-03-16

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