WO2016112804A1 - Convertisseur de couple hydraulique de type à flux axial composite et transmission variable en continu - Google Patents

Convertisseur de couple hydraulique de type à flux axial composite et transmission variable en continu Download PDF

Info

Publication number
WO2016112804A1
WO2016112804A1 PCT/CN2016/070213 CN2016070213W WO2016112804A1 WO 2016112804 A1 WO2016112804 A1 WO 2016112804A1 CN 2016070213 W CN2016070213 W CN 2016070213W WO 2016112804 A1 WO2016112804 A1 WO 2016112804A1
Authority
WO
WIPO (PCT)
Prior art keywords
input
gear
output
carrier
coupled
Prior art date
Application number
PCT/CN2016/070213
Other languages
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 CN201680004298.0A priority Critical patent/CN108027033A/zh
Publication of WO2016112804A1 publication Critical patent/WO2016112804A1/fr

Links

Images

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
    • 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
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • 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
    • F16H2702/00—Combinations of two or more transmissions

Definitions

  • the invention belongs to the field of torque converters and shifting, and more particularly to a composite axial-flow 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 composite axial-flow 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 composite axial flow torque converter comprising an input shaft (1), an output shaft (3), an input gear pair (4), an overrunning clutch (5), an axial flow hydraulic torque converter (6) And an output gear pair (7), wherein 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 an output planet carrier ( 23), input gear (24), input carrier (25), output gear (26), input carrier (27), input pinion (28), output ring gear (29), input ring gear (21) through
  • the planetary gear (20) on the output carrier (23) cooperates with the fixed ring gear (22) and the output carrier (23), and the fixed ring gear (22) and the input end (51) of the overrunning clutch (5) are fixed.
  • the component is coupled, the output carrier (23) is coupled to the input gear (41) of the input gear pair (4), the output gear (42) of the input gear pair (4) is coupled to the input carrier (25), and the input carrier (25)
  • the planetary gear (20) on it cooperates with the input gear (24) and the output gear (26), the output gear (26) is coupled to the input carrier (27), and the planet on which the planet carrier (27) passes is input.
  • the gear (20) works in conjunction with the input pinion (28) and the output ring gear (29)
  • the output ring gear (29) is coupled to the output shaft (3), the input gear (24), the input pinion (28), and the output end (52) of the overrunning clutch (5) and the axial flow torque converter (6)
  • the output end (62) is coupled
  • the input end (61) of the axial flow torque converter (6) is coupled to the output gear (72) of the output gear pair (7)
  • the input gear of the output gear pair (7) (71) and the input ring gear (21) is coupled to the input shaft (1).
  • a continuously variable transmission of a composite axial flow torque converter comprising an input shaft (1), an output shaft (3), an input gear pair (4), an input gear (5), a coupling gear pair (6), An overrunning clutch (7), an axial flow torque converter (8), an output gear pair (9), a planetary gear (20) and an output between the input shaft (1) and the output shaft (3) Planet carrier (21), fixed ring gear (22), input gear (23), connecting planet carrier (24), input pinion (25), input bull gear (26), coupling output planet carrier (27), input small Ring gear (28), input large ring gear (29), input carrier (30), input ring gear (31), output ring gear (32), input gear (23) and input gear pair (6) input gear (61) and the input shaft (1) is coupled, and the input gear (23) cooperates with the output carrier (21) and the fixed ring gear (22) through the planetary gear (20) on the output carrier (21) to fix the ring gear.
  • the output carrier (21) is coupled to the input bull gear (26), and the input large gear (26) is coupled to the planet carrier (24)
  • the planetary gear (20) cooperates with the coupled planet carrier (24) and the input pinion (25)
  • the input gear (5) is coupled to the coupling carrier (24) and the input large ring gear (29), and the input large ring gear (29) passes through the planetary gear (20) on the output carrier (27) and the output carrier (27) , Input small ring gear (28) connection, input small ring gear (28), input gear pair (4) input gear (41) and overrunning clutch (7) output (72) and axial flow torque converter
  • the output end (82) of (8) is coupled, the input end (81) of the axial flow torque converter (8) is coupled to the output gear (92) of the output gear pair (9), and the output gear pair (9) is
  • the input gear (91) is coupled to the input shaft (1), the output gear (42) of the coupling gear pair (4) is coupled to the input carrier (25), and
  • the ring gear (31) cooperates with the input carrier (30) and the output ring gear (32) through the planetary gear (20) on the input carrier (30), and the output ring gear (32) is coupled with the output shaft (3).
  • the input planet carrier (30) is coupled to 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 axial-flow 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 axial flow torque converter includes an input shaft 1, an output shaft 3, an input gear pair 4, an overrunning clutch 5, an axial flow torque converter 6, and an output gear.
  • the auxiliary shaft 7 is provided with a planetary gear 20, an input ring gear 21, a fixed ring gear 22, an output carrier 23, an input gear 24, an input carrier 25, an output gear 26, and an input between the input shaft 1 and the output shaft 3.
  • the carrier 27, the input pinion 28, and the output ring gear 29, the input ring gear 21 cooperates with the fixed ring gear 22 and the output carrier 23 through the planetary gears 20 on the output carrier 23, and fixes the ring gear 22 and the overrunning clutch 5
  • the input end 51 is coupled to a fixed member
  • the output carrier 23 is coupled to the input gear 41 of the input gear pair 4
  • the output gear 42 of the input gear pair 4 is coupled to the input carrier 25
  • the input planet carrier 25 is coupled to the planetary gear 20 thereon.
  • the input gear 24 and the output gear 26 cooperate
  • the output gear 26 is coupled to the input carrier 27, and the input carrier 27 cooperates with the input pinion 28 and the output ring gear 29 through the planetary gear 20 thereon, and outputs the ring gear 29 and the output.
  • Shaft 3 is connected, input gear 24, input small
  • the wheel 28 and the output 52 of the overrunning clutch 5 are coupled to the output 62 of the axial-flow torque converter 6, the input 61 of the axial-flow torque converter 6 being coupled to the output gear 72 of the output gear pair 7
  • the input gear 71 of the output gear pair 7 and the input ring gear 21 are coupled to the input shaft 1.
  • the input 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 gear 26.
  • the output gear 26 is transmitted to the input carrier 27, the input carrier 27, and the input pinion 28.
  • the power delivered thereto is converged to the output ring gear 29 by the planetary gears 20 on the input 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 gear 24 and the input pinion 28 is zero, the input carrier 25 and the input planet are input.
  • the frame 27 is reduced in speed, and when the rotational speeds of the input gear 24 and the input pinion 28 are continuously increased, the rotational speeds of the output gear 26 and the output ring gear 29 are also increased, that is, when the input gear 24 is input.
  • the rotational speed of the pinion gear 28 changes, the rotational speeds of the output gear 26, the output ring gear 29, and the output shaft 3 also change.
  • the input power is split into two paths via the input shaft 1, and the first path is transmitted to the axial-flow torque converter 6 via the output gear pair 7, and then transmitted to the input gear 24 and the input pinion 28; the second path
  • the ring gear 21 is input, and the power is transmitted to the output carrier 23 through the planetary gears 20 on the output carrier 23, the output carrier 23 is transmitted to the input carrier 25 through the input gear pair 4, the input gear 24, and the input carrier
  • the power transmitted thereto is converged to the output gear 26 through the planetary gears 20 on the input carrier 25, and then transmitted to the input carrier 27, the input carrier 27, the input pinion 28, and the planetary gears on the input carrier 27.
  • the power transmitted thereto is converged to the output ring gear 29 and then transmitted to the output shaft 3, thereby realizing the external output of the engine power through the output shaft 3.
  • the axial-flow torque converter 6 when the rotational speed of the input shaft 1 is constant, the torque on the output gear 26, the output ring gear 29, and the output shaft 3 varies with the change in the rotational speed thereof, and the lower the rotational speed, the transmission to the output gear 26 and the output ring gear 29 And the torque on the output shaft 3 is larger, and conversely, the smaller, in the process, the axial-flow torque converter 6 also acts as a torque, thereby realizing the difference in the driving resistance of the vehicle according to the vehicle.
  • a compound axial-flow 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 input ring gear 21, and then transmitted to the output carrier 23 through the planetary gears 20 on the output carrier 23, and the output carrier 23 is transmitted to the input carrier 25 through the input gear pair 4, wherein
  • 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 gear 24 and the input pinion 28 cannot be The input steering is reversed and the rotational speed is zero.
  • the power transmitted to the input carrier 25 is transferred to the output gear 26 through the planetary gear 20 thereon, and then transmitted to the input carrier 27, the input.
  • the planet carrier 27 is again passed through the planet gears 20 on it.
  • the power is converged to the output ring gear 29 and then transmitted to the output shaft 3.
  • the torque transmitted to the output shaft 3 is transmitted through the transmission system to the driving wheel, the traction force generated is sufficient to overcome the starting resistance of the vehicle, and the car starts and starts to accelerate.
  • the rotational speed of the output end 62 of the axial-flow torque converter 6 is also gradually increased, and the rotational speeds of the input input gear 24 and the input pinion 28 are also gradually increased, thereby causing the output gear 26 and the output ring gear. 29 and the torque of 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 composite axial-flow torque converter includes an input shaft 1), an output shaft 3, an input gear pair 4, an input gear 5, a coupling gear pair 6, and an overrunning clutch. 7.
  • the input gear 61 of the coupling gear pair 6 and the input shaft 1 are coupled.
  • the input gear 23 cooperates with the output carrier 21 and the fixed ring gear 22 through the planetary gears 20 on the output carrier 21 to fix the ring gear 22 and the overrunning clutch 7.
  • the input end 71 is coupled to the fixed member
  • the output carrier 21 is coupled to the input bull gear 26, and the input bull gear 26 cooperates with the coupling carrier 24 and the input pinion 25 via the planetary gear 20 coupled to the carrier 24, the input gear 5 and Connecting the planet carrier 24 and inputting the large ring gear 29
  • the input large ring gear 29 is coupled to the output carrier 27 and the input small ring gear 28 via the planetary gears 20 on the output carrier 27, and is input to the small ring gear 28, the input gear 41 of the input gear pair 4, and the output end of the overrunning clutch 7.
  • the 72 is coupled to the output end 82 of the axial flow torque converter 8, the input end 81 of the axial flow torque converter 8 is coupled to the output gear 92 of the output gear pair 9, and the input gear 91 of the output gear pair 9 is
  • the input shaft 1 is coupled, the output gear 42 of the coupling gear pair 4 is coupled to the input carrier 25, the output carrier 27 is coupled to the input ring gear 31, and the input ring gear 31 is passed through the planetary gear 20 on the input carrier 30 and the input carrier 30.
  • the output ring gear 32 cooperates, the output ring gear 32 is coupled to the output shaft 3, and the input carrier 30 is coupled to the output gear 62 of the coupling gear pair 6.
  • the input pinion 25 and the input bull gear 26 converge the power transmitted thereto through the planetary gears 20 coupled to the carrier 24 to the coupled carrier 24, and the coupled carrier 24 is transmitted through the input gear 5 to the input large ring gear 29,
  • the input small ring gear 28, the input large ring gear 29, converges the power transmitted thereto to the coupled output carrier 27 by the planetary gears 20 coupled to the output carrier 27.
  • the two power flows will change according to the change of the rotational speed distribution between the two.
  • the input pinion 25 and the input small ring gear 28 have a rotational speed of zero
  • the input large gear 26 When the input large ring gear 29 is used to reduce the speed and increase the torque, when the input pinion 25 and the input small ring gear 28 are continuously increased in speed, the rotational speed of the coupled carrier 24 and the coupled output carrier 27 also increases.
  • the rotational speed of the input pinion 25 and the input small ring gear 28 changes, the rotational speeds of the coupled carrier 24, the coupled output carrier 27, and the output shaft 3 also change.
  • the input power is split into three paths via the input shaft 1, the first path is transmitted to the input planet carrier 30 via the input gear 23 and the coupling gear pair 6, and the second path is transmitted to the axial flow hydraulic force via the output gear pair 9.
  • the torque device 8 and the axial flow torque converter 8 are further divided into two paths, one path is transmitted to the input small ring gear 28, the other path is transmitted to the input pinion gear 25 via the input gear pair 4, and the third path is input to the input gear 23 And transmitting power to the output carrier 21 through the planetary gears 20 on the output carrier 21, and then to the input bull gear 26, the input pinion 25, and the input bull gear 26 are transmitted through the planetary gears 20 coupled to the carrier 24.
  • the power here is converged to the coupled planet carrier 24, passed through the input gear 5, to the input large ring gear 29, the input small ring gear 28, and the input large ring gear 29 is transmitted through the planet gears 20 coupled to the output planet carrier 27
  • the power of this is converged to the output output carrier 27, coupled to the output carrier 27 and then transmitted to the input ring gear 31,
  • the input carrier 30 and the input ring gear 31 pass the power transmitted thereto through the planetary gear 20 on the input carrier 30 to the output ring gear 32, and the output ring gear 32 is transmitted to the output shaft 3, thereby realizing the power of the engine. It is output to the outside through the output shaft 3.
  • the torque on the coupled carrier 24, the coupled output carrier 27, and the output shaft 3 varies with the change in the rotational speed thereof, and the lower the rotational speed, the transmission to the coupled carrier 24, the coupling
  • a continuously variable transmission of a composite axial-flow torque converter that changes torque and speed with different 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 Passing to the input gear 23 and transmitting power to the output carrier 21 through the planetary gears 20 on the output carrier 21, and then to the input bull gear 26, wherein no or less power flows into the input pinion at this time. 25.
  • the small ring gear 28 is input, and the input end 71 of the overrunning clutch 7 is coupled to the fixed component to limit the steering, so that the steering of the input pinion 25 and the input small ring gear 28 cannot be opposite to the input steering, and the rotational speed is zero.
  • the power transmitted to the input bull gear 26 is transferred to the coupled carrier 24 through the planetary gear 20 coupled to the carrier 24, and then transmitted to the input large ring gear 29 through the input gear 5.
  • the input large ring gear 29 converges the power transmitted thereto by the planetary gears 20 coupled to the output carrier 27 to the coupled output carrier 27, and the coupled output carrier 27 is transferred to the input ring gear 31, the input The carrier 30, the input ring gear 31, through the planetary gears 20 on the input carrier 30, converge the power transmitted thereto to the output ring gear 32, and the output ring gear 32 is transmitted to the output shaft 3, when it is transmitted to the output shaft 3.
  • Torque when the traction force generated by the transmission system to the driving wheel is sufficient 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 axial torque converter 8 is gradually increased.
  • the rotational speed of the input pinion 25 and the input small ring gear 28 is also gradually increased, so that the torque of the coupled carrier 24, the coupled output carrier 27, and the output shaft 3 decreases as the rotational speed increases.

Landscapes

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

Abstract

L'invention concerne un convertisseur de couple hydraulique de type à flux axial composite. Un porte-satellites de sortie (23) est relié à une paire d'engrenages d'entrée (4), la paire d'engrenages d'entrée (4) est reliée à un porte-satellites d'entrée (25), un engrenage de sortie (26) est relié à un porte-satellites d'entrée (27), une couronne dentée de sortie (29) est reliée à un arbre de sortie (3), un engrenage d'entrée (24), un pignon d'entrée (28), et un embrayage de dépassement (5) sont reliés à un convertisseur de couple hydraulique de type à flux axial (6), le convertisseur de couple hydraulique de type à flux axial (6) est relié à une paire d'engrenages de sortie (7), et la paire d'engrenages de sortie (7) et une couronne dentée d'entrée (21) 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 de type à flux axial composite.
PCT/CN2016/070213 2015-01-16 2016-01-06 Convertisseur de couple hydraulique de type à flux axial composite et transmission variable en continu WO2016112804A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201680004298.0A CN108027033A (zh) 2015-01-16 2016-01-06 一种复合型轴流式液力变矩器以及无级变速器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN2015100213534 2015-01-16
CN201510021353.4A CN104696472B (zh) 2015-01-16 2015-01-16 一种复合型轴流式液力变矩器以及无级变速器

Publications (1)

Publication Number Publication Date
WO2016112804A1 true WO2016112804A1 (fr) 2016-07-21

Family

ID=53343890

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2016/070213 WO2016112804A1 (fr) 2015-01-16 2016-01-06 Convertisseur de couple hydraulique de type à flux axial composite et transmission variable en continu

Country Status (3)

Country Link
CN (4) CN105422783A (fr)
HK (3) HK1211667A1 (fr)
WO (1) WO2016112804A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105422783A (zh) * 2015-01-16 2016-03-23 吴志强 一种复合型轴流式液力变矩器的无级变速器
CN107448574A (zh) * 2015-07-07 2017-12-08 广州市志变制能科技有限责任公司 一种复合型双泵轮液力变矩器以及起动器

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
CN102022514A (zh) * 2009-09-09 2011-04-20 吴志强 一种复合型轴流式液力变矩器
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
CN103939569A (zh) * 2014-05-07 2014-07-23 吴志强 一种复合型轴流式液力变矩器以及无级变速器
CN104696472A (zh) * 2015-01-16 2015-06-10 吴志强 一种复合型轴流式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
GB1156049A (en) * 1965-11-01 1969-06-25 Inpower Works Ltd Improvements in or relating to Fluid Torque Transmitters.
DE19859458B4 (de) * 1997-12-23 2007-11-22 Luk Gs Verwaltungs Kg Getriebe
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
CN102022514A (zh) * 2009-09-09 2011-04-20 吴志强 一种复合型轴流式液力变矩器
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
CN103939569A (zh) * 2014-05-07 2014-07-23 吴志强 一种复合型轴流式液力变矩器以及无级变速器
CN104696472A (zh) * 2015-01-16 2015-06-10 吴志强 一种复合型轴流式液力变矩器以及无级变速器
CN105333095A (zh) * 2015-01-16 2016-02-17 吴志强 一种复合型轴流式液力变矩器

Also Published As

Publication number Publication date
HK1216335A1 (zh) 2016-11-04
HK1211667A1 (zh) 2016-05-27
CN104696472A (zh) 2015-06-10
CN105422783A (zh) 2016-03-23
CN104696472B (zh) 2016-03-16
HK1222437A1 (zh) 2017-06-30
CN105333095A (zh) 2016-02-17
CN108027033A (zh) 2018-05-11

Similar Documents

Publication Publication Date Title
WO2017005177A1 (fr) Coupleur hydraulique de type boîtier composite, et démarreur
CN106015475A (zh) 一种复合型多元件工作轮液力变矩器以及起动器
WO2017005184A1 (fr) Accouplement hydraulique combiné à limitation de couple à milieu aqueux, et démarreur
WO2017005181A1 (fr) Coupleur hydraulique de transmission à engrenages harmonique composite, et démarreur
WO2016112804A1 (fr) Convertisseur de couple hydraulique de type à flux axial composite et transmission variable en continu
WO2016112810A1 (fr) Convertisseur de couple hydraulique de type rouet composite et transmission à variation continue
WO2016112800A1 (fr) Convertisseur de couple hydraulique composite et intégré et transmission variable en continu
WO2016112805A1 (fr) Convertisseur de couple hydraulique à double turbine composite et transmission variable en continu
WO2016112803A1 (fr) Convertisseur composite de couple hydraulique réglable par aube directrice et transmission à variation continue
WO2016112809A1 (fr) Convertisseur de couple hydraulique à poulie de pompe double composite et transmission à variation continue
WO2016112811A1 (fr) Convertisseur de couple hydraulique de type à double roue de guidage composite et transmission à variation continue
WO2016112801A1 (fr) Convertisseur de couple hydraulique de roue de travail à éléments multiples composite et transmission à variation continue
WO2016112808A1 (fr) Convertisseur de couple hydraulique centripète composite et transmission à variation continue
WO2016112806A1 (fr) Convertisseur de couple hydraulique composite ayant une soupape de débordement externe et transmission variable en continu
WO2016112802A1 (fr) Convertisseur de couple hydraulique réglable composite et transmission variable en continu
WO2016112807A1 (fr) Convertisseur de couple hydraulique de type à turbine centripète composite et transmission à variation continue
CN104482162B (zh) 一种复合型箱体式液力偶合器以及起动器
WO2017005187A1 (fr) Coupleur hydraulique à vitesse variable et démarreur composite
WO2017005186A1 (fr) Coupleur hydraulique composite rempli de liquide commandé par vanne et démarreur
WO2017005182A1 (fr) Coupleur façonné hydraulique composite, et démarreur
WO2017005180A1 (fr) Coupleur hydraulique combiné de type boîte de vitesses montée à l'arrière, et démarreur
WO2017004782A1 (fr) Transmission hydraulique combinée
WO2017005176A1 (fr) Coupleur hydraulique combiné de broyeur à carter, et démarreur
WO2017005183A1 (fr) Coupleur hydraulique de limitation de couple étendu à chambre auxiliaire arrière composé et démarreur
WO2017005179A1 (fr) Coupleur hydraulique à deux chambres composite, et démarreur

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 16737030

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

32PN Ep: public notification in the ep bulletin as address of the adressee cannot be established

Free format text: NOTING OF LOSS OF RIGHTS PURSUANT TO RULE 112(1) EPC (EPO FORM 1205A DATED 11/12/2017)

122 Ep: pct application non-entry in european phase

Ref document number: 16737030

Country of ref document: EP

Kind code of ref document: A1