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WO2016112810A1 - Convertisseur de couple hydraulique de type rouet composite et transmission à variation continue - Google Patents

Convertisseur de couple hydraulique de type rouet composite et transmission à variation continue Download PDF

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Publication number
WO2016112810A1
WO2016112810A1 PCT/CN2016/070219 CN2016070219W WO2016112810A1 WO 2016112810 A1 WO2016112810 A1 WO 2016112810A1 CN 2016070219 W CN2016070219 W CN 2016070219W WO 2016112810 A1 WO2016112810 A1 WO 2016112810A1
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WO
WIPO (PCT)
Prior art keywords
gear
input
output
coupled
carrier
Prior art date
Application number
PCT/CN2016/070219
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English (en)
Chinese (zh)
Inventor
吴志强
Original Assignee
吴志强
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 吴志强 filed Critical 吴志强
Priority to CN201680004314.6A priority Critical patent/CN107614936A/zh
Publication of WO2016112810A1 publication Critical patent/WO2016112810A1/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
    • 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
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • 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
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
    • 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
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
    • 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2033—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with one engaging means

Definitions

  • the invention belongs to the field of torque converters and shifting, and more particularly to a composite impeller type 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 impeller type 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 impeller type torque converter includes an input shaft (1), an output shaft (3), an input gear pair (4), a coupling output gear (5), a coupling input gear pair (6), an overrunning clutch ( 7) an impeller type torque converter (8) and an output gear pair (9), wherein the input shaft (1) and the output shaft (3) are provided with a planetary gear (20) and an input small ring gear ( 21), output large ring gear (22), fixed planet carrier (23), output planet carrier (24), coupling ring gear (25), input gear (26), input planet carrier (27), input ring gear (28 ), the output ring gear (29), the input small ring gear (21) works together with the output large ring gear (22) and the fixed planet carrier (23) through the planetary gear (20) on the fixed carrier (23) to fix the planet
  • the frame (23) and the input end (71) of the overrunning clutch (7) are coupled to the fixed element, and the output large ring gear (22) is coupled to the input gear (61) of the input input gear pair (6), and the input gear pair is coupled
  • the output gear (62) is coupled to the coupling ring gear (25), and the coupling ring gear (25) is coupled to the output carrier (24) and the input gear (26) through the planetary gears (20) on the output carrier (24).
  • the output ring gear (29) works in cooperation, the input carrier (27) is coupled with the output gear (42) of the input gear pair (4), and the input gear (26) and the input gear (41) of the input gear pair (4) And an output end (72) of the overrunning clutch (7) is coupled to an output end (82) of the impeller type torque converter (8), an input end (81) of the impeller type torque converter (8) and an output gear
  • the output gear (92) of the sub (9) is coupled, the input gear (91) of the output gear pair (9) and the input pinion (21) are coupled to the input shaft (1), and the output ring gear (29) and the output shaft (3) ) Connection.
  • a continuously variable transmission of a compound impeller type torque converter comprising an input shaft (1), an output shaft (3), a coupling gear pair (4), an input coupling gear pair (5), and a coupling input gear pair (6) ), output coupling gear pair (7), coupling output gear pair (8), overrunning clutch (9), impeller type torque converter (10), output gear pair (11), said input shaft (1)
  • a planetary gear (20), an input gear (21), an output carrier (22), a fixed gear (23), a coupling gear (24), an input carrier (25), and an output are provided between the output shaft (3) and the output shaft (3).
  • the gear (21) cooperates with the output carrier (22) and the fixed gear (23) through the planetary gears (20) on the output carrier (22), the fixed gear (23) and the input end of the overrunning clutch (9) (91) ) coupled to the fixed element, the output planet carrier (22) and the coupling gear pair (4)
  • the input gear (41) is coupled, the output gear (42) of the coupling gear pair (4) is coupled to the input carrier (25), and the planetary gear (20) and the coupling gear (24) through which the input carrier (25) passes
  • the output large gear (26) cooperates, the output large gear (26) is coupled with the input gear (81) of the coupled output gear pair (8), and the output gear (82) of the output gear pair (8) is coupled with the input ring gear ( 28)
  • Coupling the input ring gear (28) cooperates with the coupling planet carrier (27)
  • the input gear (61) of the gear pair (6) is coupled, the output gear (62) of the input input gear pair (6) is coupled to the input pinion (32), and the input pinion (32) is coupled to the input carrier (30).
  • the planetary gear (20) cooperates with the input input planet carrier (30) and the output large ring gear (31), and the output large ring gear (31) is coupled with the output shaft (3), and the input input carrier (30) is coupled with the input.
  • the output gear (52) of the gear pair (5) is coupled, the input gear (21), the input gear (51) of the input coupling gear pair (5), and the input gear (111) of the output gear pair (11) and the input shaft (1) ) connection, output gear pair ( 11)
  • the output gear (112) is coupled to the input end (101) of the impeller-type torque converter (10), the coupling gear (24), the input gear (71) of the output coupling gear pair (7), and the overrunning clutch (
  • the output end (92) of 9) is coupled to the output (102) of the impeller-type torque converter (10), and the output gear (72) of the output coupling gear pair (7) is coupled to the coupling planet carrier (27).
  • 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 selected from 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 impeller type 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 the two elements is indicated by a thick solid line, and the thin solid line indicates that the two elements can be rotated relative to each other.
  • Embodiment 1 is a diagrammatic representation of Embodiment 1:
  • a composite impeller type torque converter includes an input shaft 1, an output shaft 3, an input gear pair 4, a coupling output gear 5, a coupling input gear pair 6, an overrunning clutch 7, and an impeller type.
  • the torque converter 8 and the output gear pair 9 are provided with a planetary gear 20, an input small ring gear 21, an output large ring gear 22, a fixed carrier 23, and an output carrier between the input shaft 1 and the output shaft 3.
  • the coupling ring gear 25 is coupled.
  • the coupling ring gear 25 cooperates with the output planet carrier 24 and the input gear 26 through the planetary gears 20 on the output carrier 24, and the output carrier 24 is coupled with the input gear 51 of the coupled output gear 5, and the output gear 5 is coupled.
  • Output gear 52 is coupled to input ring gear 28
  • the input ring gear 28 cooperates with the input carrier 27 and the output ring gear 29 through the planetary gear 20 on the input carrier 27, and the input carrier 27 is coupled with the output gear 42 of the input gear pair 4, and the input gear 26 and the input gear pair
  • the input gear 41 of the 4 and the output 72 of the overrunning clutch 7 are coupled to the output 82 of the impeller-type torque converter 8, and the input 81 of the impeller-type torque converter 8 is coupled to the output gear 92 of the output gear pair 9.
  • the input gear 91 of the output gear pair 9 and the input pinion 21 are coupled to the input shaft 1, and the output ring gear 29 is coupled to the output shaft 3.
  • the coupling ring gear 25 and the input gear 26 converge the power transmitted thereto through the planetary gears 20 on the output carrier 24 to the output carrier 24, and the output carrier 24 is coupled to the output gear ring 5, and is input to the input ring gear 28, and the input planet
  • the frame 27, the input ring gear 28, and the power transmitted thereto through the planetary gears 20 on the input carrier 27 are converged to the output ring gear 29.
  • the input power is split into two paths through the input shaft 1, and the first path is transmitted to the impeller type torque converter 8 via the output gear pair 9, and the impeller type torque converter 8 is divided into two paths, one way to
  • the input gear 26 is input to the input carrier 27 via the input gear pair 4; the second path is input to the small ring gear 21, and the power is transmitted to the output bull gear 22 through the planetary gear 20 on the fixed carrier 23, and the output is output.
  • the large gear 22 is coupled to the input ring gear 25 by the coupling input gear pair 6, and the coupling ring gear 25 and the input gear 26 converge the power transmitted thereto through the planetary gears 20 on the output carrier 24 to the output carrier 24, and then
  • the output gear 5 is coupled to the input ring gear 28, and the input carrier 27, the input ring gear 28, and the power transmitted thereto through the planetary gears 20 on the input carrier 27 are merged to the output ring gear 29, and then transmitted to the output.
  • the shaft 3, thereby achieving external output of the engine power through the output shaft 3.
  • the output carrier 24, the output ring gear 29, and the output shaft 3 are The torque varies with the change of the rotational speed.
  • the lower the rotational speed the greater the torque transmitted to the output carrier 24, the output ring gear 29 and the output shaft 3, and vice versa, the smaller the impeller type liquid in the process.
  • the torque converter 8 also functions as a torque converter to realize a composite impeller type torque converter in which the present invention can change the torque and speed depending on the running resistance of the vehicle.
  • 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 Passing to the input small ring gear 21, and then transmitting the power to the output bull gear 22 through the planetary gears 20 on the fixed carrier 23, and the output large gear 22 is transmitted to the coupling ring gear 25 through the coupling input gear pair 6, wherein Since no power or relatively little power flows into the input gear 26, the input carrier 27, and the input end 71 of the overrunning clutch 7 is coupled to the fixed member at this time, the steering is restricted, and the steering of the input gear 26 and the input carrier 27 cannot be turned.
  • the rotational speed is zero.
  • the power transmitted to the coupled ring gear 25 is transmitted to the output carrier 24 through the planetary gears 20 on the output carrier 24, and then coupled.
  • the gear 5 is transmitted to the input ring gear 28, and the input ring gear 28 is passed through the planetary gear 20 on the input carrier 27 to transfer the power transmitted thereto to the output ring gear 29, and then to the output shaft 3,
  • the torque transmitted to the output shaft 3 is generated by the transmission system and the traction force generated on the drive wheel is sufficient to overcome the starting resistance of the vehicle, the vehicle starts and starts to accelerate, and the output speed of the output end 82 of the impeller torque converter 8 is also Increasingly, the rotational speed of the input gear 26 and the input carrier 27 associated therewith is gradually increased, so that the torque of the output carrier 24, the output ring gear 29, and the output shaft 3 decreases as the number of revolutions increases.
  • Embodiment 2 is a diagrammatic representation of Embodiment 1:
  • a continuously variable transmission of a compound impeller type torque converter includes an input shaft 1, an output shaft 3, a coupling gear pair 4, an input coupling gear pair 5, a coupling input gear pair 6, and an output.
  • a coupling gear pair 7, a coupling output gear pair 8, an overrunning clutch 9, an impeller type torque converter 10, an output gear pair 11, a planetary gear 20 and an input gear 21 are disposed between the input shaft 1 and the output shaft 3.
  • the input pinion gear 32 is coupled to the output carrier 22 and the fixed gear 23 through the planetary gear 20 on the output carrier 22, and the input end 91 of the fixed gear 23 and the overrunning clutch 9 are coupled with the fixed component to output the planet carrier.
  • 22 is coupled to the input gear 41 of the coupling gear pair 4
  • the output gear 42 of the coupling gear pair 4 is coupled to the input carrier 25, and the input carrier 25 cooperates with the coupling gear 24 and the output bull gear 26 via the planetary gear 20 thereon.
  • Output large teeth 26 is coupled to the input gear 81 of the coupled output gear pair 8
  • the output gear 82 of the coupled output gear pair 8 is coupled to the input ring gear 28
  • the input ring gear 28 is coupled to the planet carrier 27 and the output by the planet gear 20 coupled to the carrier 27.
  • the ring gear 29 cooperates, the output ring gear 29 is coupled to the input gear 61 of the input input gear pair 6, the output gear 62 of the input input gear pair 6 is coupled to the input pinion 32, and the input pinion 32 is coupled to the input carrier 30.
  • the planetary gear 20 cooperates with the input input planet carrier 30 and the output large ring gear 31.
  • the output large ring gear 31 is coupled with the output shaft 3, and the input input carrier 30 is coupled with the output gear 52 of the input coupling gear pair 5, and the input gear 21,
  • the input gear 51 of the input coupling gear pair 5 and the input gear 111 of the output gear pair 11 are coupled to the input shaft 1, and the output gear 112 of the output gear pair 11 is coupled to the input end 101 of the impeller torque converter 10, and the coupling gear 24 is coupled.
  • the input gear 71 of the output coupling gear pair 7 and the output end 92 of the overrunning clutch 9 are coupled to the output end 102 of the impeller torque converter 10, and the output gear 72 of the output coupling gear pair 7 is coupled to the coupling carrier 27. .
  • the coupling gear 24 and the input carrier 25 pass the power transmitted thereto through the planetary gears 20 on the input carrier 25 to the output bull gear 26, and the output large gear 26 is transmitted to the input ring gear 28 through the coupled output gear pair 8.
  • the connecting planet carrier 27 and the input ring gear 28 converge the power transmitted thereto by the planet gears 20 coupled to the planet carrier 27.
  • the ring gear 29 is output.
  • the input power is divided into three paths through the input shaft 1, the first path is transmitted to the input input planet carrier 30 via the input coupling gear pair 5, and the second path is transmitted to the impeller type torque converter 10 via the output gear pair 11
  • the impeller-type torque converter 10 is divided into two paths, one is transmitted to the coupling gear 24, the other is transmitted to the coupling carrier 27 via the output coupling gear pair 7, and the third passage is through the input gear 21, and through the output planet
  • the planet gears 20 on the frame 22 transfer power to the output carrier 22, through the coupling gear pair 4, to the input carrier 25, the coupling gear 24, and the input carrier 25 are transmitted through the planet gears 20 on the input carrier 25.
  • the power here is converged to the output bull gear 26, and is coupled to the input ring gear 28 by the coupled output gear pair 8, the coupling carrier 27, the input ring gear 28 being transmitted thereto by the planet gears 20 coupled to the planet carrier 27.
  • the power sinks to the output ring gear 29, which is coupled to the input pinion 32 via the coupled input gear pair 6, coupled to the input carrier 30, and the input bull gear 32 is coupled through the planet gears 20 coupled to the input carrier 30. Power sink to this point Output ring gear 31, the ring gear 31 and then output to the output shaft 3, thus achieving the external output power of the engine 3 through the output shaft.
  • the torque on the output bull gear 26, the output ring gear 29, and the output shaft 3 varies with the change of the rotational speed thereof, and the lower the rotational speed, the transmission to the output large gear 26 and the output tooth.
  • the torque on the ring 29 and the output shaft 3 is larger, and conversely, the smaller, in the process, the impeller torque converter 10 also acts as a torque converter, thereby realizing the difference in the driving resistance of the present invention with the vehicle.
  • a continuously variable transmission of a compound impeller type torque converter that changes 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 Passed to
  • the gear 21 is input and transmitted to the output carrier 22 via the planet gears 20 on the output carrier 22, and then to the input carrier 25 via the coupling gear pair 4, wherein there is no or relatively little power inflow input at this time.
  • the large gear 26 is coupled to the ring gear 28, and the input end 91 of the overrunning clutch 9 is coupled to the fixed component to restrict the steering, so that the steering of the input bull gear 26 and the coupling ring gear 28 cannot be opposite to the input steering, and the rotational speed is zero.
  • the power transmitted to the input carrier 25 is transferred to the output bull gear 26 through the planetary gear 20 on the input carrier 25, and then transmitted to the input ring gear through the coupled output gear pair 8.
  • the input ring gear 28 is connected to the output ring gear 29 by the planetary gear 20 coupled to the carrier 27, and the output ring gear 29 is transmitted to the input pinion 32 through the coupling input gear pair 6, and the input is coupled.
  • the planet carrier 30 and the input bull gear 32 converge the power transmitted thereto by the planetary gears 20 coupled to the input carrier 30 to the output large ring gear 31, and the output large ring gear 31 is transmitted to the output shaft 3, when transmitted to the output.
  • the torque on the shaft 3, when the traction force generated by the transmission system to the driving wheel is sufficient to overcome the starting resistance of the vehicle, the vehicle starts and starts to accelerate, and the rotational speed of the output end 102 of the impeller torque converter 10 is gradually increased.
  • the rotational speed of the associated coupling gear 24 and the coupling carrier 27 is also gradually increased, so that the torque of the output bull gear 26, the output ring gear 29, and the output shaft 3 is reduced as the number of revolutions increases.

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

Abstract

La présente invention concerne un convertisseur de couple hydraulique de type rouet composite. Une grande couronne dentée (22) de sortie est reliée à une paire d'engrenages (6) d'entrée de liaison. La paire d'engrenages (6) d'entrée de liaison est reliée à une couronne dentée (25) de liaison. Un porte-satellites (24) de sortie est relié à un engrenage (5) de sortie de liaison. L'engrenage (5) de sortie de liaison est relié à une couronne dentée (28) d'entrée. Un porte-satellites (27) d'entrée est relié à une paire d'engrenages (4) d'entrée. Un engrenage (26) d'entrée, une paire engrenages (4) d'entrée et un embrayage à inertie (7) sont reliés à un convertisseur de couple hydraulique de type rouet (8). Le convertisseur de couple hydraulique de type rouet (8) est relié à une paire d'engrenages (9) de sortie. La paire d'engrenages (9) de sortie et un pignon (21) d'entrée sont reliés à un arbre d'entrée (1). Une couronne dentée (29) de sortie est reliée à un arbre de sortie (3). Par ailleurs, l'invention concerne en outre une transmission à variation continue d'un convertisseur de couple hydraulique de type rouet.
PCT/CN2016/070219 2015-01-16 2016-01-06 Convertisseur de couple hydraulique de type rouet composite et transmission à variation continue WO2016112810A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201680004314.6A CN107614936A (zh) 2015-01-16 2016-01-06 一种复合型叶轮式液力变矩器以及无级变速器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN2015100213943 2015-01-16
CN201510021394.3A CN104696476B (zh) 2015-01-16 2015-01-16 一种复合型叶轮式液力变矩器

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WO2016112810A1 true WO2016112810A1 (fr) 2016-07-21

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CN (5) CN107816529A (fr)
HK (1) HK1211662A1 (fr)
WO (1) WO2016112810A1 (fr)

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Publication number Priority date Publication date Assignee Title
CN107816529A (zh) * 2015-01-16 2018-03-20 广州市志变制能科技有限责任公司 一种复合式液力异型偶合器
WO2020182163A1 (fr) * 2019-03-12 2020-09-17 熊建文 Roue libre bidirectionnelle et transmission à deux vitesses

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CN102022513A (zh) * 2009-09-09 2011-04-20 吴志强 一种复合型叶轮式液力变矩器
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
CN103953709A (zh) * 2014-05-07 2014-07-30 吴志强 一种复合型叶轮式液力变矩器以及无级变速器
CN104696476A (zh) * 2015-01-16 2015-06-10 吴志强 一种复合型叶轮式液力变矩器以及无级变速器

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DE10115987A1 (de) * 2001-03-30 2002-10-02 Zahnradfabrik Friedrichshafen Mehrstufengetriebe
CN103953710B (zh) * 2014-05-07 2016-04-13 吴志强 一种复合型双泵轮液力变矩器以及无级变速器
CN103939567B (zh) * 2014-05-07 2016-04-13 吴志强 一种具有综合式液力变矩器的无级变速器

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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
CN102022513A (zh) * 2009-09-09 2011-04-20 吴志强 一种复合型叶轮式液力变矩器
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
CN103953709A (zh) * 2014-05-07 2014-07-30 吴志强 一种复合型叶轮式液力变矩器以及无级变速器
CN104696476A (zh) * 2015-01-16 2015-06-10 吴志强 一种复合型叶轮式液力变矩器以及无级变速器

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CN104696476B (zh) 2018-01-23
CN107614936A (zh) 2018-01-19

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