WO2017005186A1 - Coupleur hydraulique composite rempli de liquide commandé par vanne et démarreur - Google Patents

Coupleur hydraulique composite rempli de liquide commandé par vanne et démarreur Download PDF

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Publication number
WO2017005186A1
WO2017005186A1 PCT/CN2016/088750 CN2016088750W WO2017005186A1 WO 2017005186 A1 WO2017005186 A1 WO 2017005186A1 CN 2016088750 W CN2016088750 W CN 2016088750W WO 2017005186 A1 WO2017005186 A1 WO 2017005186A1
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WIPO (PCT)
Prior art keywords
gear
input
output
carrier
coupled
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Application number
PCT/CN2016/088750
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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 CN201680039176.5A priority Critical patent/CN108603578A/zh
Publication of WO2017005186A1 publication Critical patent/WO2017005186A1/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
    • 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
    • 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

Definitions

  • the invention belongs to the field of fluid coupling and starting, and more particularly to a composite valve-controlled liquid-filled fluid coupling and starter for various ground vehicles, ships, railway locomotives and machine tools.
  • the fluid coupling 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 valve-regulated liquid-filled fluid coupling and a starter which prolong the service life of the engine, has a simple structure, is convenient to operate, has low cost, and is energy-saving and high-efficiency.
  • a composite valve-regulated liquid-filled fluid coupling and starter comprising an input shaft (1), a valve-controlled liquid-filled fluid coupling (3), a first one-way clutch (4), and an output shaft (5) ), empty gear mechanism (6), coupling gear pair (7), input gear pair (8), output gear (9), output gear pair (10), second one-way clutch (11), electromagnetic clutch (12 ), a starter gear pair (13), a start gear pair (14), an overrunning clutch (15), a planetary gear (20), an input carrier, between the input shaft (1) and the output shaft (5) (21), output ring gear (22), input pinion (23), output gear (24), fixed planet carrier (25), input gear (26), output small ring gear (27), coupled to the input planet carrier ( 28) fixed ring gear (29), the input shaft (1) is coupled with the output gear (142) of the start gear pair (14) and the input end (151) of the overrunning clutch (15), and the output end of the overrunning clutch (152) coupled to the input pinion (23), the input end (111) of
  • the output of the empty gear mechanism (6) ( 62) coupled to the output shaft (5), the output gear (72) of the coupling gear pair (7) is coupled to the coupling input carrier (28), and coupled to the planetary gear (20) and output through the input carrier (28)
  • the small ring gear (27) and the fixed ring gear (29) cooperate with each other, and the output small ring gear (27) is coupled with the input end (41) of the first one-way clutch (4) to fix the carrier (25) and the fixed tooth.
  • the ring (29) is coupled to the stationary element.
  • Composite valve-regulated liquid-filled fluid coupling including input shaft (1), valve-controlled liquid-filled fluid coupling (3) a one-way clutch (4), an output shaft (5), an input gear pair (6), a coupling shaft (7), a coupling frame (8), a coupling gear (9), an overrunning clutch (10), Between the input shaft (1) and the output shaft (5), a planetary gear (20), an input carrier (21), an input gear (22), an output ring gear (23), an output small ring gear (24), Fixed planet carrier (25), input large ring gear (26), input bull gear (27), output carrier (28), input pinion (29), input shaft (1) and coupling shaft (7) and overrunning clutch
  • the input end (101) of (10) is coupled, the input end (101) of the overrunning clutch (10) is coupled to the input gear (22), the coupling shaft (7) is coupled to the input bull gear (27), and the input gear (22) is passed
  • the planetary gear (20) on the input carrier (21) cooperates with the input carrier (21) and the output ring gear
  • the elements that need to be coupled, and the elements that are separated by several other elements, can be connected to or through several other elements by means of a hollow or a coupling frame; when the coupled elements are gears or ring gears, Then, meshing or coupling; the gear ratio of each gear pair and the shifting mechanism is designed according to actual needs.
  • valve-controlled fluid-filled fluid coupling can be replaced by an axial-flow hydraulic torque converter.
  • the air-locking mechanism can select a clutch instead.
  • 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 enables the engine and the starter to operate in the region of the tempering speed, that is, the engine operates in a range of very small pollution discharge speeds, thereby avoiding the engine discharging a large amount of exhaust gas during idle speed and high speed operation, thereby reducing the number of exhaust gases.
  • the emission of exhaust gas is 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 drive train 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 vehicle speed, reduces the wear of the engine, prolongs the overhaul interval mileage, and is beneficial to improving productivity;
  • the invention reduces the transmission mechanism of the current starter machine and reduces the manufacturing cost. After the engine is started, only the braking and separating measures of the starting motor are required to stop the transmission.
  • the present invention is a composite valve-controlled fluid-filled fluid coupling and starter 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 diagram of a second embodiment of the present invention.
  • 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 valve-controlled fluid-filled fluid coupling and starter includes an input shaft 1 , a valve-controlled fluid-filled fluid coupling 3 , a first one-way clutch 4 , and an output shaft 5 .
  • empty gear mechanism 6 coupling gear pair 7, input gear pair 8, output gear 9, output gear pair 10, second one-way clutch 11, electromagnetic clutch 12, starter gear pair 13, starting gear pair 14, overrunning clutch 15.
  • the planetary gear 20, the input carrier 21, the output ring gear 22, the input pinion 23, the output gear 24, the fixed carrier 25, the input gear 26, and the output are disposed between the input shaft 1 and the output shaft 5.
  • the input shaft 1 is coupled with the output gear 142 of the start gear pair 14 and the input end 151 of the overrunning clutch 15, the output end 152 of the overrunning clutch 15 and the input pinion 23,
  • the input end 111 of the second one-way clutch 11 and the output gear 132 of the starter gear pair 13 are coupled, and the output gear 132 of the starter gear pair 13 and the input gear 131 of the starter gear pair 13 cooperate with each other, and the second one-way clutch Output 112 of the 11 and the output gear
  • the input gear 101 of the output gear pair 10 is coupled to the input gear 81 of the input gear pair 8, the input end 31 of the valve-filled fluid coupling 3 and the output gear 82 of the input gear pair 8 and
  • the output end 42 of the first one-way clutch 4 is coupled, and the output end 32 of the valve-controlled fluid-filled fluid coupling 3 is coupled to the input gear 26, and the input gear 26 passes through the planetary gear 20 and the output gear 24 on the fixed carrier 25.
  • the fixed planet carrier 25 cooperates with each other, the output gear 24 is coupled to the input carrier 21, and the input planet carrier 21 cooperates with the output ring gear 22 and the input pinion 23 through the planetary gear 20 thereon, and outputs the ring gear 22 and the output gear.
  • the input end 61 of the neutral gear mechanism 6 is coupled to the input end 71 of the coupling gear pair 7, the output gear 9 and the input end 121 of the electromagnetic clutch 12, the output gear 122 of the electromagnetic clutch 12 and the input gear of the start gear pair 14 141 is coupled, the output end 62 of the neutral gear mechanism 6 is coupled to the output shaft 5, and the output gear 72 of the coupling gear pair 7 is coupled to the coupling input carrier 28, and the planetary gear 20 and the input planetary carrier 28 are coupled thereto.
  • the small ring gear 27 and the fixed ring gear 29 cooperate with each other, and the output small ring gear 27 is coupled to the input end 41 of the first one-way clutch 4, and the fixed carrier 25 and the fixed ring gear 29 are coupled to the fixed element.
  • the idle gear mechanism 6 Before the engine is started, the idle gear mechanism 6 is disengaged and the electromagnetic clutch 12 is engaged.
  • the input power of the starter passes through the starter gear pair 13, is transmitted to the overrunning clutch 15 and is split into two paths, one pass to the input pinion 23, and the other pass.
  • the second one-way clutch 11, the output gear pair 10, the input gear pair 8, and the valve-controlled fluid-filled fluid coupling 3 are transmitted to the input gear 26, and the input gear 26 is transmitted to the output gear through the planetary gear 20 on the fixed carrier 25. 24, then pass To the input carrier 21, the input carrier 21, the input pinion 23 converge the planetary gear 20 transmitted to the respective power through the input coupling carrier 21 to the output ring gear 22, and the output ring gear 22 passes through the output gear 9, and is empty.
  • the input 61 of the gear mechanism 6, the electromagnetic clutch 12, and the starter gear pair 14 are transmitted to the input shaft 1 and then transmitted to the crankshaft of the engine, and the generated starting power is sufficient to overcome the engine starting resistance and the engine is started.
  • the idle gear mechanism 6 After the engine is started, the idle gear mechanism 6 is engaged, the electromagnetic clutch 12 is disengaged, the input shaft 1 is transmitted from the engine to the overrunning clutch 15 and then split into two paths, one pass to the input pinion 23 and the other through the second one-way clutch 11
  • the output gear pair 10, the input gear pair 8 and the valve-controlled fluid-filled fluid coupling 3 are transmitted to the input gear 26, and the input gear 26 is transmitted to the output gear 24 through the planetary gear 20 on the fixed carrier 25, and then transmitted to the input.
  • the carrier 21, the input carrier 21, and the input pinion 23 converge the planetary gears 20 transmitted to the respective powers through the input carrier 21 to the output ring gear 22, and the output ring gear 22 is transmitted thereto through the output gear 9.
  • the power split is two ways, one way is transmitted to the output shaft 5 of the present invention through the air-gear mechanism 6; the other is transmitted to the joint input planet carrier 28 through the air-gear mechanism 6 and the coupling gear pair 7, and the input planet carrier 28 is coupled and passed.
  • the planetary gear 20 is transmitted to the output small ring gear 27, and the output small ring gear 27 is transmitted to the input gear 26 through the first one-way clutch 4 and the valve-controlled fluid-filled fluid coupling 3, and the input teeth are input.
  • 26 is transmitted to the output gear 24 through the planet gears 20 on the fixed carrier 25, and then to the input carrier 21, the input carrier 21, the input pinion 23, and the planetary gears 20 that are transmitted to the respective powers through the input carrier 21.
  • the output ring gear 22 Converging on the output ring gear 22, the output ring gear 22 continuously repeats the shifting between the various components, wherein the output speed of the valve-controlled fluid-filled fluid coupling 3 continuously follows the input power and the running resistance.
  • the variable speed is changed steplessly, so that the output rotational speed of the output ring gear 22 is also constantly changed, and is transmitted to the output shaft 5 of the present invention through the output gear 9 and the neutral gear mechanism 6, thereby realizing the output of the engine power.
  • the shaft 5 is output to the outside.
  • the torques on the input carrier 21, the output ring gear 22, and the output shaft 5 vary with the change of the rotational speed thereof, and the lower the rotational speed, the transmission to the input carrier 21 and the output teeth.
  • the torque on the ring 22 and the output shaft 5 is larger, and vice versa, so that the composite valve-type fluid-filled fluid coupling and the starter capable of changing the torque and speed according to the driving resistance of the present invention are realized. .
  • the idle gear mechanism 6 When the invention is used, before the engine is started, the idle gear mechanism 6 is separated, the electromagnetic clutch 12 is engaged, and the engine speed is zero.
  • the starter When the starter is started, the input power of the starter is transmitted to the overrunning clutch 15 through the starter gear pair 13
  • the flow is divided into two paths, one way is transmitted to the input pinion 23, and the other way is transmitted to the input gear 26 through the second one-way clutch 11, the output gear pair 10, the input gear pair 8, and the valve-controlled fluid-filled fluid coupling 3, and the input is input.
  • the gear 26 is transmitted to the output gear 24 through the planet gears 20 on the fixed carrier 25, and then to the input carrier 21, the input carrier 21, the input pinion 23, and the planets that transmit the respective powers through the input to the planet carrier 21.
  • the gear 20 is merged with the output ring gear 22, and the output ring gear 22 is transmitted to the input shaft 1 through the output gear 9, the input end 61 of the neutral gear mechanism 6, the electromagnetic clutch 12, and the start gear pair 14, and then transmitted to the engine crankshaft.
  • the engine generated is generated when the starting power is sufficient to overcome the engine starting resistance.
  • the input power, input speed and load of the engine are unchanged, that is, the speed and torque of the input shaft 1 are constant.
  • the idle gear mechanism 6 is engaged, the electromagnetic clutch 12 is separated, and the input shaft 1 is The engine is transmitted to the overrunning clutch 15 and then split into two paths, one way to the input pinion 23, the other way to the second one-way clutch 11, the output gear pair 10, the input gear pair 8 and the valve-controlled fluid-filled fluid coupling 3 It is transmitted to the input gear 26, which is transmitted to the output gear 24 through the planetary gear 20 on the fixed carrier 25, and then transmitted to the input carrier 21, and the input carrier 21 and the input pinion 23 are transmitted to the respective power input.
  • the planet gears 20 on the planet carrier 21 converge on the output ring gear 22, and the output ring gear 22 then splits the power transmitted thereto into two paths through the output gear 9, one way through the air
  • the gear shifting mechanism 6 is transmitted to the output shaft 5 of the present invention; the other is transmitted to the coupling input carrier 28 via the air-gear mechanism 6 and the coupling gear pair 7, and the input planet carrier 28 is coupled to the output through the planetary gear 20 thereon.
  • the small ring gear 27, the output small ring gear 27 is transmitted to the input gear 26 through the first one-way clutch 4 and the valve-controlled fluid-filled fluid coupling 3, and the input gear 26 is transmitted to the planetary gear 20 on the fixed carrier 25 to
  • the output gear 24 is transmitted to the input carrier 21, and the input carrier 21 and the input pinion 23 converge the planetary gear 20 transmitted to the respective power through the input carrier 21 to the output ring gear 22, and the output ring gear 22 is
  • the repeated cycle of shifting is continuously performed between the respective components, wherein the output rotational speed of the valve-controlled fluid-filled fluid coupling 3 continuously shifts steplessly with the change of the running resistance, thereby causing the output rotational speed of the output ring gear 22 It also constantly changes and is transmitted to the output shaft 5 of the present invention through the output gear 9 and the neutral gear mechanism 6, so that the torque of the output shaft 5 decreases as the number of revolutions increases.
  • Embodiment 2 is a diagrammatic representation of Embodiment 1:
  • a composite valve-regulated liquid-filled fluid coupling includes an input shaft 1, a valve-controlled liquid-filled fluid coupling 3, a one-way clutch 4, an output shaft 5, and an input gear pair 6 , the coupling shaft 7, the coupling frame 8, the coupling gear 9, the overrunning clutch 10, between the input shaft 1 and the output shaft 5, a planetary gear 20, an input carrier 21, an input gear 22, an output ring gear 23, and an output are provided.
  • the input end 101 of the 10 is coupled to the input gear 22, and the coupling shaft 7 is coupled to the input bull gear 27.
  • the input gear 22 cooperates with the input carrier 21 and the output ring gear 23 through the planetary gear 20 on the input carrier 21, and outputs the teeth.
  • the ring 23 is coupled to the input large ring gear 26 via a coupling frame 8 and meshes with a coupling gear 9 that is coupled to an input gear 61 of the input gear pair 6, and an output gear 62 of the input gear pair 6 is coupled to the input pinion 29,
  • the input large ring gear 26 passes through the planet on the fixed planet carrier 25
  • the gear 20 cooperates with the output small ring gear 24 and the fixed planet carrier 25, the fixed planet carrier 25 is fixedly connected with the fixed component, and the output small ring gear 24 is coupled with the input end 41 of the one-way clutch 4, and the output end of the one-way clutch 4 42 and the output end 102 of the overrunning clutch 10 is coupled to the input end 31 of the valve-controlled fluid-filled fluid coupling 3, and the output 32 of the valve-controlled fluid-filled fluid coupling 3 is coupled to the input carrier 21 for input to the large gear
  • the input carrier 21 and the input gear 22 merge the power transmitted to the respective power through the planetary gear 20 on the input carrier 21 to the output ring gear 23, since the input carrier 21 is coupled to the valve-controlled fluid-filled fluid coupling 3,
  • the rotational speed of the input carrier 21 can be constantly varied as the rotational speed of the valve-controlled fluid-filled fluid coupling 3 changes, so that the rotational speed of the output ring gear 23 also changes.
  • the input power is split into two paths through the input shaft 1, one way is transmitted to the input bull gear 27 through the coupling shaft 7, and the other path is split into two paths through the overrunning clutch 10, and one way is transmitted to the valve-controlled liquid-filled fluid coupling 3, and then It is transmitted to the input carrier 21, and the other is transmitted to the input gear 22.
  • the input carrier 21 and the input gear 22 converge the respective powers through the planetary gears 20 on the input carrier 21 to the output ring gear 23, and output the ring gear 23.
  • the flow is split into two paths, one pass through the coupling gear 9 and the input gear pair 6 to the input pinion 29, at this time, the input pinion 29 and the input bull gear 27 pass the respective power through the planetary gears on the output carrier 28.
  • 20 merges with the output carrier 28, and the output carrier 28 is transmitted to the output shaft 5 of the present invention, thereby realizing external output of the engine power through the output shaft 5.
  • the power of the other path transmitted to the input ring gear 26 through the coupling frame 8 increases accordingly, and the input large ring gear 26 passes through the planet on the fixed carrier 25.
  • the gear 20 transmits power to the output small ring gear 24, and the output small ring gear 24 passes through the one-way clutch 4 and the valve-controlled liquid-filled hydraulic coupling
  • the input device 3 is transmitted to the input carrier 21, that is, the input power of the input carrier 21 is increased, and the input carrier 21 and the input gear 22 converge the output power to the output through the planetary gear 20 on the input carrier 21.
  • the ring gear 23, the output ring gear 23 repeats the above process, so that the rotational speed transmitted to the input pinion 29 is constantly changed, and the input pinion 29 and the input bull gear 27 transmit the respective power to the planetary gears on the output carrier 28. 20 merges with the output carrier 28, and the output carrier 28 is transmitted to the output shaft 5 of the present invention, thereby realizing external output of the engine power through the output shaft 5.
  • the rotational speed of the input shaft 1 when the rotational speed of the input shaft 1 is constant, the rotational speed of the input pinion 29 varies with the input power or running resistance of the vehicle, and the lower the resistance, the higher the rotational speed transmitted to the input pinion 29 The higher, conversely, the lower, thereby realizing the composite valve-regulated liquid-filled fluid coupling of the present invention which can change speed depending on the input power or 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 5 is zero, and the input power of the engine passes through the input shaft 1
  • the flow is divided into two paths, one is transmitted to the input bull gear 27 through the coupling shaft 7, and the other is divided into two through the overrunning clutch 10, and is transmitted to the valve-controlled liquid-filled fluid coupling 3, and then transmitted to the input carrier 21
  • the other path is transmitted to the input gear 22, and the input carrier 21 and the input gear 22 merge the respective powers through the planetary gears 20 on the input carrier 21 to the output ring gear 23, and the output ring gear 23 is split into two paths.
  • the planetary gear 20 on the carrier 21 merges with the output ring gear 23, and the output ring gear 23 repeats the above process to continuously change the rotational speed transmitted to the input pinion 29, and the input pinion 29 and the input large gear 27 are transmitted to the respective
  • the power is converged through the planet gears 20 on the output planet carrier 28 to the output planet carrier 28, and the output planet carrier 28 is passed to the output shaft 5 of the present invention, and the torque transmitted to the output shaft 5 is transmitted through the transmission system.
  • the traction force generated on the driving wheel is sufficient to further overcome the resistance of the automobile, the automobile starts to accelerate, and the rotational speed of the output end 32 of the valve-controlled fluid-filled fluid coupling 3 is also gradually increased, and the input carrier 21 connected thereto is connected.
  • the rotational speed is also gradually increased, so that the rotational speeds of the output ring gear 23, the output small ring gear 24, the input pinion 29, and the output shaft 5 are continuously increased.

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

Abstract

Cette invention concerne un coupleur hydraulique composite rempli de liquide commandé par vanne et un démarreur comprenant ledit coupleur hydraulique composite rempli de liquide hydraulique commandé par vanne. Un arbre d'entrée (1) est relié à une paire de couronnes dentées de démarreur (14) et à une roue libre (15) ; une seconde roue libre (11) est reliée à une paire de pignons de sortie (10) ; la paire de pignons de sortie (10) est reliée à une paire de pignons d'entrée (8) ; un coupleur hydraulique rempli de liquide commandé par vanne (3) est relié à la paire de pignons d'entrée (8) à une première roue libre (4) et à un pignon d'entrée (26) ; un pignon de sortie (24) est relié à un porte-satellites d'entrée (21) ; un mécanisme de changement de dérive du zéro (6) est relié à un arbre de sortie (5), à une paire de pignons de liaison (7), à un pignon de sortie (9), et à un embrayage électromagnétique (12) ; l'embrayage électromagnétique (12) est relié à la paire de couronnes dentées de démarreur (14) ; une paire de pignons de liaison (7) est reliée à un porte-satellites de liaison d'entrée (28) ; une petite couronne de sortie (27) est reliée à une première roue libre (4).
PCT/CN2016/088750 2015-07-07 2016-07-06 Coupleur hydraulique composite rempli de liquide commandé par vanne et démarreur WO2017005186A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201680039176.5A CN108603578A (zh) 2015-07-07 2016-07-06 一种复合型阀控充液式液力偶合器以及起动器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201510389863.7A CN105042011A (zh) 2015-07-07 2015-07-07 一种复合型阀控充液式液力偶合器以及起动器
CN201510389863.7 2015-07-07

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Publication Number Publication Date
WO2017005186A1 true WO2017005186A1 (fr) 2017-01-12

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CN (2) CN105042011A (fr)
HK (1) HK1216327A1 (fr)
WO (1) WO2017005186A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105042011A (zh) * 2015-07-07 2015-11-11 吴志强 一种复合型阀控充液式液力偶合器以及起动器

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB624858A (en) * 1942-01-09 1949-06-17 Borg Warner Improvements in or relating to variable-speed transmissions and control mechanisms therefor
DE19809464A1 (de) * 1998-03-06 1999-09-16 Voith Turbo Kg Anfahrvarianten für 6-Gang-Wandlerautomatgetriebe
WO2003016751A1 (fr) * 2001-08-17 2003-02-27 Korotkov Eduard Konstantinovic Transmission holonome universelle a variation infinie de couple
CN102358159A (zh) * 2011-08-05 2012-02-22 上海中科深江电动车辆有限公司 具有液力变矩器的混合驱动系统
CN104500681A (zh) * 2014-12-12 2015-04-08 吴志强 一种复合型阀控充液式液力偶合器以及起动器
CN104534053A (zh) * 2014-12-12 2015-04-22 吴志强 一种复合型液力传动器以及起动器
CN105042011A (zh) * 2015-07-07 2015-11-11 吴志强 一种复合型阀控充液式液力偶合器以及起动器

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1058796B1 (fr) * 1998-03-06 2002-09-25 Voith Turbo GmbH & Co. KG Boite de vitesses compound hydrodynamico-mecanique a plusieurs vitesses, notamment boite de vitesses automatique a convertisseur, a six vitesses

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB624858A (en) * 1942-01-09 1949-06-17 Borg Warner Improvements in or relating to variable-speed transmissions and control mechanisms therefor
DE19809464A1 (de) * 1998-03-06 1999-09-16 Voith Turbo Kg Anfahrvarianten für 6-Gang-Wandlerautomatgetriebe
WO2003016751A1 (fr) * 2001-08-17 2003-02-27 Korotkov Eduard Konstantinovic Transmission holonome universelle a variation infinie de couple
CN102358159A (zh) * 2011-08-05 2012-02-22 上海中科深江电动车辆有限公司 具有液力变矩器的混合驱动系统
CN104500681A (zh) * 2014-12-12 2015-04-08 吴志强 一种复合型阀控充液式液力偶合器以及起动器
CN104534053A (zh) * 2014-12-12 2015-04-22 吴志强 一种复合型液力传动器以及起动器
CN105042011A (zh) * 2015-07-07 2015-11-11 吴志强 一种复合型阀控充液式液力偶合器以及起动器

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HK1216327A1 (zh) 2016-11-04
CN108603578A (zh) 2018-09-28
CN105042011A (zh) 2015-11-11

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