WO2016112807A1 - Convertisseur de couple hydraulique de type à turbine centripète composite et transmission à variation continue - Google Patents

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

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Publication number
WO2016112807A1
WO2016112807A1 PCT/CN2016/070216 CN2016070216W WO2016112807A1 WO 2016112807 A1 WO2016112807 A1 WO 2016112807A1 CN 2016070216 W CN2016070216 W CN 2016070216W WO 2016112807 A1 WO2016112807 A1 WO 2016112807A1
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Prior art keywords
gear
input
output
coupled
carrier
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PCT/CN2016/070216
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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 CN201680004308.0A priority Critical patent/CN107407389A/zh
Publication of WO2016112807A1 publication Critical patent/WO2016112807A1/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
    • 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
    • F16H3/76—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with an orbital gear having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable
    • 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 converter and shifting, and more particularly to a composite radial turbine 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 radial turbine torque converter and a continuously variable transmission which are prolonged in service life, simple in structure, convenient in operation, low in cost, energy-saving and high-efficiency.
  • a compound radial turbine torque converter comprising an input shaft (1), an output shaft (3), a radial turbine torque converter (4), an overrunning clutch (5), and a coupling gear pair ( 6), input gear pair (7), output gear pair (8), between the input shaft (1) and the output shaft (3), a planetary gear (20), a fixed planet carrier (21), and a small input Gear (22), output bull gear (23), input gear (24), output carrier (25), input bull gear (26), input planet carrier (27), input small ring gear (28), output large teeth
  • the ring (29), the input pinion (22) and the input gear (81) of the output gear pair (8) are coupled to the input shaft (1), and the input pinion (22) is passed through the planet gears on the fixed carrier (21) ( 20) Cooperating with the fixed carrier (21) and the output large gear (23), the fixed carrier (21) and the input end (51) of the overrunning clutch (5) are coupled with the fixed component, and the output gear (23) and the input are input.
  • the large gear (26) is coupled, and the input large gear (26) cooperates with the input gear (24) and the output carrier (25) through the planetary gear (20) on the output carrier (25), and outputs the planet carrier (25) and
  • the input gear (61) of the coupling gear pair (6) is coupled, and the coupling teeth
  • the output gear (62) of the sub (6) is coupled to the input carrier (27), and the input planet carrier (27) passes the planetary gear (20) and the input small ring gear (28), and the output large ring gear (29)
  • input the small ring gear (28), the output end (52) of the overrunning clutch (5), and the input gear (71) of the input gear pair (7) and the output of the radial turbine torque converter (4) input the small ring gear (28), the output end (52) of the overrunning clutch (5), and the input gear (71) of the input gear pair (7) and the output of the radial turbine torque converter (4).
  • the end (42) is coupled, the input end (41) of the radial turbine torque converter (4) is coupled to the output gear (82) of the output gear pair (8), and the output gear of the input gear pair (7) (72) ) is coupled to the input gear (24), and the output large ring gear (29) is coupled to the output shaft (3).
  • a continuously variable transmission of a compound radial turbine torque converter comprising an input shaft (1), an output shaft (3), a coupling input gear pair (4), a coupling output gear pair (5), an input gear ( 6), overrunning clutch (7), output gear pair (8), radial turbine torque converter (9), coupling gear pair (10), said input shaft (1) and output shaft (3) Planetary gear (20), fixed planet carrier (21), output ring gear (22), input large gear (23), connecting planet carrier (24), input pinion (25), output large gear (26) ), input small ring gear (27), output planet carrier (28), input large ring gear (29), input planet carrier (30), output large ring gear (31), input gear (32), fixed planet carrier ( 21)
  • the planetary gear (20) thereon cooperates with the output ring gear (22) and the input large gear (23), and the fixed carrier (21) and the input end (71) of the overrunning clutch (7) are coupled with the fixed component.
  • the output ring gear (22) is coupled to the input gear (41) of the input input gear pair (4), and the output gear (42) of the input input gear pair (4) is coupled with the coupled carrier (24) to connect the carrier (24) ) through it
  • the planetary gear (20) cooperates with the input pinion (25) and the output large gear (26), the output large gear (26) is coupled with the input small ring gear (27), and the input small ring gear (27) passes through the output carrier ( 28)
  • the upper planetary gear (20) cooperates with the output carrier (28) and the input large ring gear (29), and the output carrier (28) is coupled with the input gear (51) of the coupled output gear pair (5), and is coupled.
  • the output gear (52) of the output gear pair (5) is coupled to the input carrier (30), and the input planetary gear (20) and the output large ring gear (31) and the input gear (32) are coupled to the carrier (30).
  • the output large ring gear (31) is coupled to the output shaft (3), and the input gear (32), the input large gear (23), and the input gear (101) of the coupling gear pair (10) are coupled to the input shaft (1).
  • the output gear (102) of the coupling gear pair (10) is coupled to the input end (91) of the centripetal turbine torque converter (9), the output of the radial turbine torque converter (9) ( 92) coupled to the input gear (81) of the output gear pair (8), the output gear (82) of the output gear pair (8) is coupled to the output end (72) of the overrunning clutch (7) and the input gear (6), input Large ring gear (29) with input pinion (25) and input gear ( 6) Connection.
  • 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 radial turbine 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 radial turbine torque converter includes an input shaft 1 , an output shaft 3 , a radial turbine torque converter 4 , an overrunning clutch 5 , a coupling gear pair 6 ,
  • the input gear pair 7 and the output gear pair 8 are provided with a planetary gear 20, a fixed carrier 21, an input pinion 22, an output large gear 23, an input gear 24, and an output carrier between the input shaft 1 and the output shaft 3. 25.
  • the input large gear 26, the input carrier 27, the input small ring gear 28, the output large ring gear 29, the input pinion 22 and the input gear 81 of the output gear pair 8 are coupled to the input shaft 1, and the input pinion 22 is fixed to the planet.
  • the planetary gear 20 on the frame 21 cooperates with the fixed carrier 21 and the output bull gear 23.
  • the fixed end of the carrier 21 and the overrunning clutch 5 is coupled to the fixed element, and the output large gear 23 is coupled to the input large gear 26, and the input is large.
  • the gear 26 cooperates with the input gear 24 and the output carrier 25 via the planetary gear 20 on the output carrier 25, the output carrier 25 is coupled to the input gear 61 of the coupling gear pair 6, and the output gear 62 of the gear pair 6 is coupled to the input planet.
  • the output 42 of the torque converter 4 is coupled, the input 41 of the radial turbine torque converter 4 is coupled to the output gear 82 of the output gear set 8, and the output gear 72 of the input gear set 7 is coupled to the input gear 24.
  • the output large ring gear 29 is coupled to the output shaft 3.
  • the input gear 24 and the input bull gear 26 converge the power transmitted thereto through the planetary gears 20 on the output carrier 25 to the output carrier 25, and the output carrier 25 is coupled to the input carrier 27 via the coupling gear pair 6, and the input planet
  • the frame 27, the input small ring gear 28, and the power transmitted thereto through the planetary gears 20 on the input carrier 27 are merged to the output large ring gear 29.
  • the input power is split into two paths via the input shaft 1, and the first path is transmitted to the centripetal turbine torque converter 4 via the input gear pair 8, and the centripetal turbine torque converter 4 is split into two paths.
  • the output bull gear 23 is transferred to the input bull gear 26, and the input gear 24 and the input bull gear 26 pass the power transmitted thereto through the planetary gear 20 on the output carrier 25 to the output carrier 25, and output
  • the carrier 25 is coupled to the input carrier 27 via the coupling gear pair 6, and the input carrier 27, the input small ring gear 28, and the power transmitted thereto through the planetary gears 20 on the input carrier 27 are converged to the output large ring gear. 29, the output large ring gear 29 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 carrier 25, the output large ring gear 29, 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 carrier 25 and the output.
  • the torque on the large ring gear 29 and the output shaft 3 is larger, and conversely, the smaller, in the process, the centripetal turbine torque converter 4 also acts as a torque converter, thereby realizing the present invention with the vehicle.
  • Composite radial turbine fluid with varying torque and speed Force torque converter when the rotational speed of the input shaft 1 is constant, the torque on the output carrier 25, the output large ring gear 29, 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 carrier 25 and the output.
  • the torque on the large ring gear 29 and the output shaft 3 is larger, and conversely, the smaller, in the process, the centripetal turbine torque converter 4 also acts as a torque converter, thereby realizing the present invention with 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 pinion 22, and transmitting power to the output bull gear 23 through the planet gears 20 on the fixed planet carrier 21, and then to the input bull gear 26, wherein there is no power or relatively little power inflow input at this time.
  • the gear 24 is input to the small ring gear 28, and the input end 51 of the overrunning clutch 5 is coupled with the fixed component to restrict the steering, so that the steering of the input gear 24 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 transmitted to the output carrier 25 through the planetary gears 20 on the output carrier 25, and the output carrier 25 is transmitted to the input carrier 27 through the coupling gear pair 6.
  • the input carrier 27 transmits power to the output large ring gear 29 through the planetary gears 20 thereon, and then to the output shaft 3, when the torque transmitted to the output shaft 3 passes through the power train.
  • the vehicle starts and starts to accelerate, and the rotational speed of the output end 42 of the radial turbine torque converter 4 is gradually increased, and the input gear 24 associated therewith is gradually increased.
  • the rotational speed of the input small ring gear 28 is also gradually increased, so that the torque of the output carrier 25, the output large ring gear 29, and the output shaft 3 is reduced as the number of revolutions increases.
  • Embodiment 2 is a diagrammatic representation of Embodiment 1:
  • a continuously variable transmission of a compound radial turbine torque converter includes an input shaft 1, an output shaft 3, a coupling input gear pair 4, a coupling output gear pair 5, an input gear 6,
  • the overrunning clutch 7, the output gear pair 8, the radial turbine torque converter 9, the coupling gear pair 10, the planetary gear 20, the fixed carrier 21, and the output gear are disposed between the input shaft 1 and the output shaft 3.
  • the input gear 32, the fixed planet carrier 21 cooperates with the output ring gear 22 and the input large gear 23 through the planetary gear 20 thereon, and the fixed end of the fixed carrier 21 and the overrunning clutch 7 is coupled with the fixed component, and the output ring gear 22 is output.
  • Coupling with the input gear 41 of the input input gear pair 4, the output gear 42 of the input input gear pair 4 is coupled to the coupling carrier 24, and the planetary carrier 20 of the coupling carrier 24 is coupled with the input pinion 25 and the output bull gear 26 via the planetary gear 20 thereon.
  • the input gear 32, the input bull gear 23, and the input gear 101 of the coupling gear pair 10 are coupled to the input shaft 1, and the output gear 102 of the coupling gear pair 10 is coupled to the input end 91 of the centripetal turbine torque converter 9,
  • the output end 92 of the heart turbine type torque converter 9 is coupled to the input gear 81 of the output gear pair 8, and the output gear 82 of the output gear pair 8 is coupled to the output end 72 of the overrunning clutch 7 and the input gear 6 to input a large ring gear.
  • 29 is coupled to the input pinion 25 and the input gear 6.
  • the connecting planet carrier 24 and the input pinion 25 converge the power transmitted thereto through the planetary gears 20 coupled to the carrier 24 to the output bull gear 26, and the output bull gear 26 is transmitted to the input small ring gear 27, and the input small ring gear 27
  • the input large ring gear 29 converges the power transmitted thereto through the planetary gears 20 on the output carrier 28 to the output carrier 28.
  • the input power is split into three paths via the input shaft 1, and the first path is coupled to the input gear pair 10, the radial turbine torque converter 9, the output gear pair 8 and the input gear pair 6, and is transmitted to the input large ring gear 29
  • the input large ring gear 29 is transmitted to the input pinion 25;
  • the second path is transmitted to the input bull gear 23, and the input large gear 23 transmits power to the output ring gear 22 through the planetary gears 20 on the fixed carrier 21, and the output teeth are output.
  • the ring 22 is again transmitted to the coupling carrier 24 by the coupling input gear pair 4, and the coupling carrier 24 and the input pinion 25 converge the power transmitted thereto to the output bull gear 26 through the planetary gear 20 coupled to the carrier 24, and the output is large.
  • the gear 26 is again transmitted to the input small ring gear 27, the input small ring gear 27, the input large ring gear 29 is passed through the planetary gears 20 on the output carrier 28 to transfer the power transmitted thereto to the output carrier 28, and the output carrier 28 is By coupling the output gear pair 5, it is transmitted to the input carrier 30; the third path is transmitted to the input gear 32, the input carrier 30, the input gear 32 and the power transmitted thereto through the planetary gear 20 on the input carrier 30 Output large ring gear 31 Output ring gear 31 and then transmitted 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 carrier 28, 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 bull gear 26 and the output planet.
  • the torque on the frame 28 and the output shaft 3 is larger, and conversely, the smaller, in the process, the centripetal turbine torque converter 9 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 radial turbine 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 Passing to the input bull gear 23, and transmitting power to the output ring gear 22 through the planetary gears 20 on the fixed planet carrier 21, and the output ring gear 22 is transmitted to the coupled planet carrier 24 through the coupled input gear pair 4, wherein
  • the input large ring gear 29 and the input end 71 of the overrunning clutch 7 is coupled with the fixed element to limit the steering, so that the input pinion 25 and the input large ring gear 29 are The steering cannot be reversed from the input steering, and the rotational speed is zero.
  • the power transmitted to the coupled carrier 24 is transferred to the output bull gear 26 through the planetary gear 20 thereon, and the output large gear 26 is output. It is transmitted to the input small ring gear 27, and the input small ring gear 27 is connected to the output carrier 28 through the planetary gears 20 on the output carrier 28, and the output carrier 28 is connected through the output.
  • the gear pair 5 is transmitted to the input carrier 30, and the input carrier 30, the input gear 32, and the power transmitted thereto through the planetary gear 20 of the input carrier 30 are merged to the output large ring gear 31, and the output ring gear 31 is retransmitted.

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

Abstract

Convertisseur de couple hydraulique de type à turbine centripète composite et transmission à variation continue. Un pignon d'entrée (22) 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 grand engrenage d'entrée (26), un porte-satellites de sortie (25) est relié à une paire d'engrenages de liaison, la paire d'engrenages de liaison (6) est reliée à un porte-satellites d'entrée (27), une petite couronne dentée d'entrée (28), un embrayage à roue libre (5) et une paire d'engrenages d'entrée (7) sont reliés à un convertisseur de couple hydraulique de type à turbine centripète (4), le convertisseur de couple hydraulique de type à turbine centripète (4) est relié à la paire d'engrenages de sortie (8), la paire d'engrenages d'entrée (7) est reliée à un engrenage d'entrée (24), et une grande couronne dentée de sortie (29) est reliée à un arbre de sortie (3).
PCT/CN2016/070216 2015-01-16 2016-01-06 Convertisseur de couple hydraulique de type à turbine centripète composite et transmission à variation continue WO2016112807A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201680004308.0A CN107407389A (zh) 2015-01-16 2016-01-06 一种复合型向心涡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
CN201510021352.XA CN104653745B (zh) 2015-01-16 2015-01-16 一种复合型向心涡轮式液力变矩器
CN201510021352.X 2015-01-16

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Publication Number Publication Date
WO2016112807A1 true WO2016112807A1 (fr) 2016-07-21

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CN (5) CN104653745B (fr)
HK (1) HK1211656A1 (fr)
WO (1) WO2016112807A1 (fr)

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CN104653745B (zh) * 2015-01-16 2017-06-23 广州市无级制动科技有限责任公司 一种复合型向心涡轮式液力变矩器

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KR20060009190A (ko) * 2004-07-21 2006-01-31 이종완 범위가 확장된 무단변속장치
CN102022506A (zh) * 2009-09-09 2011-04-20 吴志强 一种复合型向心涡轮式液力变矩器
WO2011093425A1 (fr) * 2010-01-28 2011-08-04 株式会社ユニバンス Dispositif de transmission de puissance
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CN103939558A (zh) * 2014-05-07 2014-07-23 吴志强 一种复合型向心涡轮式液力变矩器以及无级变速器
CN104653745A (zh) * 2015-01-16 2015-05-27 吴志强 一种复合型向心涡轮式液力变矩器以及无级变速器

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NL284069A (fr) * 1961-10-10
CN2596112Y (zh) * 2002-08-14 2003-12-31 天津鼎盛工程机械有限公司 一种降轴式单级向心涡轮液力变矩器
CN202955198U (zh) * 2012-11-23 2013-05-29 天津工程机械研究院 一种低速高效节能型单级向心涡轮液力变矩器
CN203717833U (zh) * 2013-12-19 2014-07-16 天津工程机械研究院 取力口前置的单级向心涡轮液力变矩器

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* 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
CN102022506A (zh) * 2009-09-09 2011-04-20 吴志强 一种复合型向心涡轮式液力变矩器
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
CN103939558A (zh) * 2014-05-07 2014-07-23 吴志强 一种复合型向心涡轮式液力变矩器以及无级变速器
CN104653745A (zh) * 2015-01-16 2015-05-27 吴志强 一种复合型向心涡轮式液力变矩器以及无级变速器

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CN107339396A (zh) 2017-11-10
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CN107339395A (zh) 2017-11-10
CN104653745B (zh) 2017-06-23

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