WO2016112809A1 - Convertisseur de couple hydraulique à poulie de pompe double composite et transmission à variation continue - Google Patents

Convertisseur de couple hydraulique à poulie de pompe double composite et transmission à variation continue Download PDF

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Publication number
WO2016112809A1
WO2016112809A1 PCT/CN2016/070218 CN2016070218W WO2016112809A1 WO 2016112809 A1 WO2016112809 A1 WO 2016112809A1 CN 2016070218 W CN2016070218 W CN 2016070218W WO 2016112809 A1 WO2016112809 A1 WO 2016112809A1
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Prior art keywords
gear
input
output
carrier
coupled
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PCT/CN2016/070218
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English (en)
Chinese (zh)
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吴志强
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吴志强
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Application filed by 吴志强 filed Critical 吴志强
Priority to CN201680004300.4A priority Critical patent/CN107429810A/zh
Publication of WO2016112809A1 publication Critical patent/WO2016112809A1/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
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric 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
    • 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
    • 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
    • F16H47/085—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 with at least two mechanical connections between the hydraulic device and the mechanical transmissions
    • 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
    • F16H2200/203—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 double-pump hydraulic 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 double-pump hydraulic torque converter and a continuously variable transmission which have the advantages of short life, simple structure, convenient operation, low cost, energy saving and high efficiency.
  • a compound double pump wheel hydraulic torque converter comprising an input shaft (1), an output shaft (3), a double pump wheel hydraulic torque converter (4), an overrunning clutch (5), and a coupling gear pair (6)
  • the input gear pair (7) and the output gear pair (8) are provided with a planetary gear (20), an input pinion (21), and a fixed planet carrier between the input shaft (1) and the output shaft (3).
  • the planetary gear (20) on the output carrier (26) cooperates with the output carrier (26) and the input gear (28), and the output carrier (26) is coupled with the output shaft (3), the input gear (28), and the input.
  • the input gear (71) of the gear pair (7) and the output end (52) of the overrunning clutch (5) are coupled to the output end (42) of the double pump wheel torque converter (4), and the double pump wheel hydraulic torque
  • the input (41) of the input (4) is coupled to the output gear (82) of the output gear pair (8), and the output gear (72) of the input gear pair (7) is coupled to the input carrier (24).
  • a continuously variable transmission of a compound double-pump hydraulic torque converter comprising an input shaft (1), an output shaft (3), an input gear pair (4), an output gear (5), a coupling gear pair (6), An overrunning clutch (7), a double pumping wheel torque converter (8), an output gear pair (9), a planetary gear (20) and an input between the input shaft (1) and the output shaft (3) Ring gear (21), fixed ring gear (22), coupling output carrier (23), coupling gear (24), input carrier (25), output bull gear (26), connecting planet carrier (27), input gear (28), the output ring gear (29), the input pinion (30), the output carrier (31), the input large gear (32), and the input ring gear (21) is coupled to the planetary gear on the output carrier (23) (20) Cooperating with the fixed ring gear (22) and the coupled output planet carrier (23), the fixed ring gear (22) and the input end (71) of the overrunning clutch (7) are coupled with the fixed component, and the output output carrier (23) ) coupled to the coupling gear (24),
  • the gear (42) is coupled, the input gear ring (21), the input gear (41) of the input gear pair (4), and the input gear (91) of the output gear pair (9) are coupled to the input shaft (1), and the output gear pair (
  • the output gear (92) of 9) is coupled to the input end (81) of the double pump wheel torque converter (8), the input gear (61) of the gear pair (6) and the output end of the overrunning clutch (7) ( 72) coupled to the output (82) of the dual pump wheel torque converter (8), the input carrier (25) coupled to the output carrier (27) and the output gear (62) of the coupling gear pair (6).
  • 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 double-pump 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 double pump wheel torque converter includes an input shaft 1 , an output shaft 3 , a double pump wheel torque converter 4 , an overrunning clutch 5 , a coupling gear pair 6 , and an input gear.
  • the auxiliary shaft 7 and the output gear pair 8 are provided with a planetary gear 20, an input pinion 21, a fixed carrier 22, an output large gear 23, an input carrier 24, and an input input gear 25 between the input shaft 1 and the output shaft 3.
  • the output carrier 26, the input ring gear 27, the input gear 28, the input pinion 21 and the input gear 81 of the output gear pair 8 are coupled to the input shaft 1, and the input pinion 21 is fixed by the planetary gear 20 fixed on the carrier 22.
  • the carrier 22 and the output bull gear 23 cooperate, the fixed carrier 22 and the input end 51 of the overrunning clutch 5 are coupled to the fixed component, the output bull gear 23 is coupled to the coupling input gear 25, and the input gear 25 is coupled to the input carrier 24.
  • the planetary gear 20 cooperates with the input carrier 24 and the input gear 61 of the coupling gear pair 6.
  • the output gear 62 of the coupling gear pair 6 is coupled to the input ring gear 27, and the input ring gear 27 passes through the planetary gear 20 on the output carrier 26.
  • Output planet carrier 26, lose The input gear 28 cooperates, the output carrier 26 is coupled to the output shaft 3, the input gear 28, the input gear 71 of the input gear pair 7, and the output 52 of the overrunning clutch 5 and the output 42 of the dual pump turbine torque converter 4
  • the input 41 of the twin-pump torque converter 4 is coupled to the output gear 82 of the output gear set 8
  • the output gear 72 of the input gear set 7 is coupled to the input carrier 24.
  • the input carrier 24 and the coupling input gear 25 converge the power transmitted thereto through the planetary gears 20 on the input carrier 24 to the input gear 61 of the coupling gear pair 6, and the input gear 61 of the coupling gear pair 6 is coupled to the gear pair 6
  • the output gear 62 is transmitted to the input ring gear 27, the input ring gear 27, the input gear 28 and the power output planet carrier 26 that is transmitted thereto via the planet gears 20 on the output carrier 26.
  • the two power flows will change according to the change of the rotational speed distribution between the two.
  • the rotational speeds of the input carrier 24 and the input gear 28 are zero, the input gear 25 and the input teeth are coupled.
  • the ring 27 is decelerated and increased in torque.
  • the rotational speeds of the output gear 62 and the output carrier 26 of the coupling gear pair 6 also increase, that is, when When the rotational speeds of the input carrier 24 and the input gear 28 change, the rotational speeds of the output gear 62, the output carrier 26, and the output shaft 3 of the coupling gear pair 6 also change.
  • the input power is divided into two paths through the input shaft 1, the first path is output to the double pump wheel torque converter 4 via the output gear pair 8, and the double pump wheel torque converter 4 is divided into two paths, one way It is transmitted to the input gear 28, and the other is input to the input gear 71 of the input gear pair 7, to the output gear 72 of the input gear pair 7, and then to the input carrier 24; the second path is input to the pinion 21, and then through the fixed planet.
  • the planet gears 20 on the frame 22 transfer power to the output bull gear 23, the output bull gear 23 is transferred to the coupling input gear 25, the input planet carrier 24, and the coupling input gear 25 are transmitted through the planet gears 20 on the input carrier 24 to This power sinks to the input gear 61 of the coupling gear pair 6, and is transmitted to the input ring gear 27 via the output gear 62 of the coupling gear pair 6, the input ring gear 27, the input gear 28 and the planetary gears on the output carrier 26.
  • the power transmitted thereto is converged to the output carrier 26 and then transmitted to the output shaft 3, thereby realizing the external output of the engine power through the output shaft 3.
  • the torque on the output gear 62, the output carrier 26, and the output shaft 3 of the coupling gear pair 6 changes with the change of the rotational speed thereof, and the lower the rotational speed, the transmission to the coupling gear pair
  • the torque on the output gear 62, the output carrier 26, and the output shaft 3 of 6 is larger, and conversely, the smaller, in the process, the double-pump hydraulic torque converter 4 also acts as a torque converter, thereby realizing
  • the invention relates to a composite double-pump hydraulic torque converter capable of changing torque and speed according to different running resistance of the vehicle.
  • the input power, the input rotational speed and the load of the engine are unchanged, that is, the rotational speed of the input shaft 1
  • the torque is constant.
  • the output shaft 3 has zero speed.
  • the input power of the engine is transmitted to the input pinion 21 via the input shaft 1, and the power is transmitted to the output through the planetary gear 20 on the fixed carrier 22.
  • the gear 23, the output bull gear 23 is transferred to the coupling input gear 25, wherein since no power or relatively little power flows into the input carrier 24, the input gear 28 at this time, and the input end 51 of the overrunning clutch 5 is coupled to the fixed element,
  • the function of limiting the steering is such that the steering of the input carrier 24 and the input gear 28 cannot be opposite to the input steering, and the rotational speed is zero.
  • the power transmitted to the input input gear 25 passes through the planetary gear input to the carrier 24.
  • the power transmitted thereto is merged into the input gear 61 of the coupling gear pair 6, and then transmitted to the input ring gear 27 via the output gear 62 of the coupling gear pair 6, and the input ring gear 27 passes through the planetary gears on the output carrier 26.
  • the power transmitted thereto is converged to the output carrier 26 and then transmitted to the output shaft 3, and the torque transmitted to the output shaft 3 is transmitted to the drive wheel through the transmission system.
  • Embodiment 2 When it is enough to overcome the starting resistance of the car, the car starts and starts to accelerate, and the rotational speed of the output end 42 of the double-pump torque converter 4 is gradually increased, and the rotational speeds of the input planet carrier 24 and the input gear 28 associated with it are also This gradually increases, so that the torque of the output gear 62 of the coupling gear pair 6, the output carrier 26, and the output shaft 3 decreases as the number of revolutions increases.
  • a continuously variable transmission of a composite double-pump hydraulic torque converter includes an input shaft 1, an output shaft 3, an input gear pair 4, an output gear 5, a coupling gear pair 6, and an overrunning clutch 7 a double pump wheel torque converter 8 and an output gear pair 9.
  • the input shaft 1 and the output shaft 3 are provided with a planetary gear 20, an input ring gear 21, a fixed ring gear 22, and a coupling output carrier 23, Coupling gear 24, input planet carrier 25, output bull gear 26, coupling planet carrier 27, input gear 28, output ring gear 29, input pinion 30, output planet carrier 31, input bull gear 32, input ring gear 21 through coupling output
  • the planetary gears 20 on the planet carrier 23 cooperate with the fixed ring gear 22 and the coupled output planet carrier 23.
  • the fixed ring gear 22 and the input end 71 of the overrunning clutch 7 are coupled to the fixed element, and the coupled output carrier 23 is coupled to the coupling gear 24,
  • the coupling gear 24 cooperates with the input carrier 25 and the output bull gear 26 via the planetary gears 20 on the input carrier 25, the output bull gear 26 is coupled to the input gear 28, and the input gear 28 is coupled to the planetary gear 20 on the carrier 27 Connecting the planet carrier 27, output
  • the ring gear 29 cooperates
  • the output gear 5 is coupled with the output ring gear 29 and the input pinion 30, and the input pinion 30 cooperates with the output carrier 31 and the input large gear 32 through the planetary gear 20 on the output carrier 31 to output the planet.
  • the frame 31 is coupled to the output shaft 3, the input large gear 32 is coupled to the output gear 42 of the input gear pair 4, and the input ring gear 21, the input gear 41 of the input gear pair 4, and the input gear 91 of the output gear pair 9 are coupled to the input shaft 1.
  • the output gear 92 of the output gear pair 9 is coupled to the input end 81 of the dual pump wheel torque converter 8, the input gear 61 of the gear pair 6 and the output 72 of the overrunning clutch 7 and the double pump wheel torque converter
  • the output 82 of the 8 is coupled and the input carrier 25 is coupled to the output carrier 27 and the output gear 62 of the coupling gear pair 6.
  • the coupling gear 24 and the input carrier 25 converge the power transmitted thereto through the planetary gears 20 on the input carrier 25 to the output bull gear 26, and the output bull gear 26 is transmitted to the input gear 28, and the carrier 27 and the input gear 28 are coupled.
  • the power delivered thereto is converged to the output ring gear 29 by the planet gears 20 coupled to the planet carrier 27.
  • 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 25 and the coupled carrier 27 is zero, the coupling gear 24 and the input gear 28, the speed is increased, and when the rotational speed of the input carrier 25 and the coupled carrier 27 is continuously increased, the rotational speeds of the output large gear 26 and the output ring gear 29 are also increased, that is, when the input carrier 25 is input.
  • the rotational speed of the coupled carrier 27 changes, the rotational speeds of the output bull gear 26, the output ring gear 29, and the output shaft 3 also change.
  • the input power is divided into three paths via the input shaft 1, and the first path is transmitted to the input bull gear 32 via the input gear pair 4; the second path is transmitted to the double pump wheel torque converter 8 via the output gear pair 9, and then Passed to the gear pair 6, passed to the loser
  • the planetary carrier 25 is transferred to the coupled carrier 27; the third passage is input to the ring gear 21, and the power is transmitted to the coupled output carrier 23 through the planetary gear 20 coupled to the output carrier 23, and then transmitted to the coupling gear 24
  • 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 then to the input gear 28, and the planetary carrier 27 and the input gear 28 are coupled to the planet.
  • the planetary gear 20 on the frame 27 merges the power transmitted thereto to the output ring gear 29, and the output ring gear 29 passes through the output gear 5, and is transmitted to the input pinion 30, the input pinion 30, and the input large gear 32 through the output carrier.
  • the planetary gear 20 on 31 converges the power transmitted thereto to the output carrier 31, and the output carrier 31 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 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 double pump wheel torque converter 8 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 double-pump hydraulic 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
  • the power is transmitted to the input ring gear 21, and then the power transmission is coupled to the output carrier 23 through the planetary gears 20 coupled to the output carrier 23, and then transmitted to the coupling gear 24, wherein no or less power flows into the input planet at this time.
  • the frame 25 is coupled to the carrier 27, and the input end 71 of the overrunning clutch 7 is coupled to the fixed component to restrict the steering, so that the steering of the input carrier 25 and the coupled carrier 27 cannot be reversed from the input steering, and the rotational speed is zero.
  • the power transmitted to the coupling gear 24 is transferred to the output bull gear 26 through the planetary gear 20 on the input carrier 25, and then transmitted to the input gear 28, which passes through the coupling carrier 27.
  • the upper planetary gear 20 converges the power transmitted thereto to the output ring gear 29, and the output ring gear 29 passes through the output gear 5, and is transmitted to the input pinion 30, the input pinion 30, and the input.
  • the gear 32 converges the power transmitted thereto through the planetary gears 20 on the output carrier 31 to the output carrier 31, and the output carrier 31 is transmitted to the output shaft 3, and the torque transmitted to the output shaft 3 is transmitted through the transmission system.
  • the traction force generated on the driving wheel is enough to overcome the starting resistance of the vehicle, the car starts and starts to accelerate, and the rotational speed of the output end 82 of the double pump wheel torque converter 8 is gradually increased, and the input planet carrier 25 and the connection are connected thereto.
  • the rotational speed of the carrier 27 also gradually increases, so that the torque of the output bull gear 26, the output ring gear 29, 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)
  • Structure Of Transmissions (AREA)
  • Retarders (AREA)
  • Transmission Devices (AREA)

Abstract

Convertisseur de couple hydraulique à poulie de pompe double composite. Un pignon d'entrée (21) et une paire d'engrenages de sortie (8) sont reliés à un arbre d'entrée (1), un grand engrenage de sortie (23) est relié à un engrenage d'entrée de liaison (25), une paire d'engrenages de liaison (6) est reliée à une couronne dentée d'entrée (27), un porte-satellites de sortie (26) est relié à un arbre de sortie (3), un engrenage d'entrée (28), une paire d'engrenages d'entrée (7) et un embrayage à roue libre (5) sont reliés à un convertisseur de couple hydraulique à poulie de pompe double (4), le convertisseur de couple hydraulique à poulie de pompe double (4) est relié à une paire d'engrenages de sortie (8), et la paire d'engrenages d'entrée (7) est reliée à un porte-satellites d'entrée (24). En outre, l'invention concerne également une transmission à variation continue d'un convertisseur de couple hydraulique à poulie de pompe double composite.
PCT/CN2016/070218 2015-01-16 2016-01-06 Convertisseur de couple hydraulique à poulie de pompe double composite et transmission à variation continue WO2016112809A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201680004300.4A CN107429810A (zh) 2015-01-16 2016-01-06 一种复合型双泵轮液力变矩器以及无级变速器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201510021379.9A CN104696475B (zh) 2015-01-16 2015-01-16 一种复合型双泵轮液力变矩器
CN201510021379.9 2015-01-16

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WO2016112809A1 true WO2016112809A1 (fr) 2016-07-21

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CN (5) CN107339397A (fr)
HK (1) HK1211661A1 (fr)
WO (1) WO2016112809A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107339397A (zh) * 2015-01-16 2017-11-10 广州市志变制能科技有限责任公司 一种复合型双腔液力偶合器的无级变速器

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
CN102022511A (zh) * 2009-09-09 2011-04-20 吴志强 一种复合型双泵轮液力变矩器
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
CN103953710A (zh) * 2014-05-07 2014-07-30 吴志强 一种复合型双泵轮液力变矩器以及无级变速器
CN104696475A (zh) * 2015-01-16 2015-06-10 吴志强 一种复合型双泵轮液力变矩器以及无级变速器

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60101355A (ja) * 1983-11-08 1985-06-05 Daikin Mfg Co Ltd 流体伝動装置
US6569048B1 (en) * 2002-01-28 2003-05-27 Visteon Global Technologies, Inc. Tandem torque converter
CN102312977B (zh) * 2010-07-07 2015-05-13 吴志强 一种复合型箱体式液力偶合器
CN103591248B (zh) * 2013-11-12 2016-01-20 北京科技大学 一种行星式自动变速器

Patent 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
CN102022511A (zh) * 2009-09-09 2011-04-20 吴志强 一种复合型双泵轮液力变矩器
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
CN103953710A (zh) * 2014-05-07 2014-07-30 吴志强 一种复合型双泵轮液力变矩器以及无级变速器
CN104696475A (zh) * 2015-01-16 2015-06-10 吴志强 一种复合型双泵轮液力变矩器以及无级变速器

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CN107429810A (zh) 2017-12-01
HK1211661A1 (en) 2016-05-27

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