WO2017005187A1 - Coupleur hydraulique à vitesse variable et démarreur composite - Google Patents

Coupleur hydraulique à vitesse variable et démarreur composite Download PDF

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Publication number
WO2017005187A1
WO2017005187A1 PCT/CN2016/088751 CN2016088751W WO2017005187A1 WO 2017005187 A1 WO2017005187 A1 WO 2017005187A1 CN 2016088751 W CN2016088751 W CN 2016088751W WO 2017005187 A1 WO2017005187 A1 WO 2017005187A1
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input
gear
output
carrier
coupled
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Ceased
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PCT/CN2016/088751
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English (en)
Chinese (zh)
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吴志强
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Priority to CN201680039159.1A priority Critical patent/CN107923508A/zh
Publication of WO2017005187A1 publication Critical patent/WO2017005187A1/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
    • 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
    • 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 compound speed regulating fluid coupling and a 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 compound speed regulating fluid coupling and a starter which prolong the service life of the engine, has a simple structure, is convenient to operate, has low cost, is energy-saving and high-efficiency.
  • Composite speed regulating fluid coupling and starter comprising input shaft (1), variable speed fluid coupling (3), second one-way clutch (4), output shaft (5), hanging Gear mechanism (6), input gear pair (7), output gear (8), electromagnetic clutch (9), output gear pair (10), first one-way clutch (11), starter gear pair (12), starting a gear pair (13) and an overrunning clutch (14), wherein the input shaft (1) and the output shaft (5) are provided with a planetary gear (20), an input small ring gear (21), and an output carrier (22).
  • the input shaft (1) is coupled to the output gear (132) of the start gear pair (13) and the input end (141) of the overrunning clutch (14), the output end (142) of the overrunning clutch (14) and the input small ring gear (21)
  • the input end (111) of the first one-way clutch (11) and the output gear (122) of the starter gear pair (12) are coupled, the output end (112) of the first one-way clutch (11) and the output gear pair
  • the input gear (101) of (10) is coupled, and the output gear (102) and output of the output gear pair (10) are connected.
  • the gear pair (7) input gear (71) is coupled, and the output gear (122) of the starter gear pair (12) cooperates with the input gear (121) of the starter gear pair (12) to input the small ring gear (21)
  • the planetary gear (20) on the output carrier (22) cooperates with the output carrier (22) and the input large ring gear (23) to output the input end of the carrier (22) and the empty gear mechanism (6).
  • the planetary gear (20) on the planet carrier (27) cooperates with the fixed carrier (27) and the output ring gear (28), and the output ring gear (28) is coupled with the input carrier (24), and the input carrier (24) )
  • the planetary gear (20) thereon cooperates with the fixed ring gear (25) and the output gear (26), and the fixed ring gear (25) is coupled with the fixed carrier (27) to fix the carrier (27) and fix it.
  • a compound speed regulating fluid coupling comprises an input shaft (1), a variable speed fluid coupling (3), a one-way clutch (4), an output shaft (5), an input gear pair (6), Output gear pair (7), overrunning clutch (8), the input shaft (1) Between the output shaft (5), a planetary gear (20), an input large gear (21), an output coupling carrier (22), an input pinion (23), an output gear (24), an input gear (25), Fixed planet carrier (26), output planet carrier (27), input large ring gear (28), input small ring gear (29), input shaft (1) and input large gear (21) and overrunning clutch (8) input The end (81) is coupled, the input end (81) of the overrunning clutch (8) is coupled with the input small ring gear (29), and the input end (31) of the variable speed fluid coupling (3) and the overrunning clutch (8) The output end (82) and the output end (42) of the one-way clutch (4) are coupled, the input end (41) of the one-way clutch (4) is coupled with the output gear (24), and the variable speed
  • the output coupling carrier (22) is coupled to the input gear (71) of the output gear pair (7), and the output gear (72) of the output gear pair (7) and the input gear of the input gear pair (6) are 61) Coupling, input gear pair (6) output gear (62) and input gear (2 5) and the input large ring gear (28) is coupled, and the input gear (25) cooperates with the output gear (24) and the fixed planet carrier (26) through the planetary gear (20) on the fixed planet carrier (26) to fix the planet.
  • the frame (26) is fixed to the fixing component, and the input large ring gear (28) cooperates with the output carrier (27) and the input small ring gear (29) through the planetary gears (20) on the output carrier (27).
  • the output planet carrier (27) is coupled to the output shaft (5).
  • 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.
  • variable speed fluid coupling can be replaced by a radial turbine 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, reduces the manufacturing cost, and only needs to face after the engine is started.
  • the motor is braked and separated to stop the drive.
  • the present invention is a composite variable speed 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 speed regulating fluid coupling and a starter include an input shaft 1 , a variable speed fluid coupling 3 , a second one-way clutch 4 , an output shaft 5 , and an idle gear Mechanism 6, input gear pair 7, output gear 8, electromagnetic clutch 9, output gear pair 10, first one-way clutch 11, starter gear pair 12, start gear pair 13, overrunning clutch 14, said input shaft 1 and A planetary gear 20, an input small ring gear 21, an output carrier 22, an input large ring gear 23, an input carrier 24, a fixed ring gear 25, an output gear 26, a fixed carrier 27, and an output ring gear are disposed between the output shafts 5.
  • the input ring gear 29, the input shaft 1 is coupled with the output gear 132 of the start gear pair 13 and the input end 141 of the overrunning clutch 14, the output end 142 of the overrunning clutch 14 and the input small ring gear 21, the first one-way clutch 11
  • the input end 111 and the output gear 122 of the starter gear pair 12 are coupled, the output end 112 of the first one-way clutch 11 is coupled to the input gear 101 of the output gear pair 10, and the output gear 102 and the input gear pair 7 of the output gear pair 10 are input.
  • the gear 71 is coupled to the output gear of the starter gear pair 12 122 cooperates with the input gear 121 of the starter gear pair 12, and the input small ring gear 21 cooperates with the output carrier 22 and the input large ring gear 23 through the planetary gear 20 on the output carrier 22, and outputs the planet carrier 22 and
  • the input end 61 of the empty gear mechanism 6 and the input ring gear 29 are coupled, the output end 62 of the neutral gear mechanism 6 is coupled to the output shaft 5, the input ring gear 29 is meshed with the output gear 8, and the input gear 8 is input to the electromagnetic clutch 9.
  • the end 91 is coupled, the output end 92 of the electromagnetic clutch 9 and the input gear pair 13 are coupled to the input gear 131, and the input ring gear 29 cooperates with the fixed carrier 27 and the output ring gear 28 through the planetary gear 20 on the fixed carrier 27.
  • the output ring gear 28 is coupled to the input carrier 24, and the input carrier 24 cooperates with the fixed ring gear 25 and the output gear 26 through the planetary gear 20 thereon, and the fixed ring gear 25 is coupled with the fixed carrier 27 to fix the carrier 27 Coupling with the fixed element, the output gear 26 is coupled to the input 41 of the second one-way clutch 4, the output 42 of the second one-way clutch 4, and the output gear 72 of the input gear pair 7 and the variable speed fluid coupling 3 Input 31 Then, the output speed of the hydraulic coupling 3 input end 32 and the ring gear 23 is coupled.
  • the idle gear mechanism 6 Before the engine is started, the idle gear mechanism 6 is disengaged and the electromagnetic clutch 9 is engaged.
  • the input power of the starter is transmitted to the overrunning clutch 14 through the starter gear pair 12, and the overrunning clutch 14 is split into two paths, one pass and the same to the input small teeth.
  • the other side of the ring 21 is transmitted to the input large ring gear 23 through the first one-way clutch 11, the output gear pair 10, the input gear pair 7, and the variable speed type fluid coupling 3, and the input small ring gear 21 and the input large ring gear 23
  • the planetary gears 20 that are transmitted to the respective powers through the output carrier 22 are merged to the output carrier 22, and the output carrier 22 is transmitted to the input shaft through the input ring gear 29, the output gear 8, the electromagnetic clutch 9, and the start gear pair 13. 1, then transferred to the engine crankshaft, resulting from The engine is started when the power is sufficient to overcome the engine starting resistance.
  • the idle gear mechanism 6 After the engine is started, the idle gear mechanism 6 is engaged, the electromagnetic clutch 9 is disengaged, the input shaft 1 transmits the power transmitted thereto by the engine to the overrunning clutch 14, and the overrunning clutch 14 is divided into two paths, one pass and the same to the input small teeth.
  • the other side of the ring 21 is transmitted to the input large ring gear 23 through the first one-way clutch 11, the output gear pair 10, the input gear pair 7, and the variable speed type fluid coupling 3, and the input small ring gear 21 and the input large ring gear 23
  • the planetary gears 20 that are transmitted to the respective powers through the output carrier 22 are merged to the output carrier 22, and the output carrier 22 is split into two paths, one way being transmitted to the output shaft 5 of the present invention through the idle gear mechanism 6; Passing all the way to the input ring gear 29, the input ring gear 29 is transmitted to the output ring gear 28 via the planet gears 20 on the fixed planet carrier 27, the output ring gear 28 is transferred to the input planet carrier 24, through which the input planet carrier 24 passes.
  • the planetary gear 20 is transmitted to the output gear 26, and the output gear 26 is transmitted to the input large ring gear 23 through the second one-way clutch 4 and the variable speed type fluid coupling 3, and the input small ring gear 21 and the input large ring gear 23 Passed to each
  • the self-power is converge on the output carrier 22 through the planetary gears 20 on the output carrier 22, and the output carrier 22 continuously repeats the shifting between the respective components, wherein the output of the variable speed fluid coupling 3
  • the rotational speed continuously shifts steplessly as the input power and the running resistance change, so that the output rotational speed of the output carrier 22 also constantly changes, and is transmitted to the output shaft 5 of the present invention through the neutral gear mechanism 6, thereby realizing The power of the engine is externally output through the output shaft 5.
  • the torque input to the large ring gear 23, the output carrier 22, and the output shaft 5 varies with the change of the rotational speed thereof, and the lower the rotational speed is transmitted to the input large ring gear 23,
  • the torque on the output planet carrier 22 and the output shaft 5 is larger, and vice versa, so that the composite speed-regulating fluid coupling and the starter that can change the torque and speed according to the driving resistance of the present invention are realized. .
  • the idle gear mechanism 6 is disengaged, the electromagnetic clutch 9 is engaged, and the engine speed is zero.
  • the starter is started, the input power of the starter is transmitted to the overrunning clutch 14 through the starter gear pair 12, beyond The clutch 14 is further divided into two paths, one pass through to the input small ring gear 21, and the other path is transmitted to the input through the first one-way clutch 11, the output gear pair 10, the input gear pair 7, and the variable speed fluid coupling 3.
  • the large ring gear 23, the input small ring gear 21, the input large ring gear 23, and the planetary gears 20 transmitted to the respective powers passing through the output carrier 22 are merged to the output carrier 22, and the output carrier 22 is passed through the input ring gear 29,
  • the output gear 8, the electromagnetic clutch 9 and the starter gear pair 13 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 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 9 is separated, and the input shaft 1 is
  • the power transmitted to the engine is transmitted to the overrunning clutch 14, and the overrunning clutch 14 is split into two paths, one pass through to the input small ring gear 21, and the other pass through the first one-way clutch 11, the output gear pair 10, and the input gear pair. 7 and the variable speed type fluid coupling 3 are transmitted to the input large ring gear 23, the input small ring gear 21, the input large ring gear 23, and the planetary gears 20 transmitted to the respective powers passing through the output carrier 22 are merged to the output carrier.
  • the output planet carrier 22 is split into two paths, one is transmitted to the output shaft 5 of the present invention through the air-gear mechanism 6; the other is transmitted to the input ring gear 29, and the input ring gear 29 is passed through the fixed carrier 27.
  • the planetary gear 20 is transmitted to the output ring gear 28, the output ring gear 28 is transmitted to the input carrier 24, the input carrier 24 is transmitted to the output gear 26 through the planetary gear 20 thereon, and the output gear 26 is passed through the second single
  • the clutch 4 and the variable speed fluid coupling 3 are transmitted to the input large ring gear 23, the input small ring gear 21, and the input large ring gear 23 converge the planetary gears 20 transmitted to the respective powers through the output carrier 22 to the output planet.
  • the frame 22 and the output carrier 22 continuously perform repeated cycles of shifting between the respective components, wherein the output speed of the variable speed fluid coupling 3 is not
  • the ground speed is steplessly shifted as the running resistance changes, so that the output rotational speed of the output carrier 22 is also constantly changed, and is transmitted to the output shaft 5 of the present invention through the neutral gear mechanism 6, thereby causing the output shaft 5
  • the torque decreases as the speed increases.
  • Embodiment 2 is a diagrammatic representation of Embodiment 1:
  • a composite speed regulating fluid coupling includes an input shaft 1, a variable speed fluid coupling 3, a one-way clutch 4, an output shaft 5, an input gear pair 6, and an output gear pair. 7.
  • Overrunning clutch 8 between the input shaft 1 and the output shaft 5, a planetary gear 20, an input large gear 21, an output coupling carrier 22, an input pinion 23, an output gear 24, an input gear 25, and a fixed planet are provided.
  • the frame 26, the output carrier 27, the input large ring gear 28, the input small ring gear 29, the input shaft 1 is coupled to the input large gear 21 and the input end 81 of the overrunning clutch 8, the input end 81 of the overrunning clutch 8 and the input small ring gear 29, the input end 31 of the variable speed hydraulic coupling 3 is coupled with the output end 82 of the overrunning clutch 8 and the output end 42 of the one-way clutch 4, and the input end 41 of the one-way clutch 4 is coupled with the output gear 24 to adjust the speed
  • the output end 32 of the type fluid coupling 3 is coupled to the input pinion 23, and the input pinion 23 cooperates with the output coupling carrier 22 and the input large gear 21 through the planetary gear 20 on the output coupling carrier 22, and outputs the coupled planet.
  • the frame 22 is coupled to the input gear 71 of the output gear pair 7
  • the output gear 72 of the output gear pair 7 is coupled to the input gear 61 of the input gear pair 6,
  • the output gear 62 of the input gear pair 6 is coupled to the input gear 25 and the input large ring gear 28, and the input gear 25 is passed through the fixed carrier 26.
  • the planetary gear 20 cooperates with the output gear 24 and the fixed carrier 26 to fix the fixed carrier 26 and the fixed component.
  • the input large ring gear 28 passes through the planetary gear 20 on the output carrier 27 and the output carrier 27, and the input small teeth.
  • the rings 29 cooperate with each other and the output carrier 27 is coupled to the output shaft 5.
  • the input large gear 21 and the input pinion 23 converge the planetary gears 20 transmitted to the respective powers through the output coupling carrier 22 to the output coupling carrier 22, since the variable speed fluid coupling 3 is coupled to the input pinion 23, Therefore, the rotational speed of the input pinion 23 can be constantly changed as the rotational speed of the variable speed fluid coupling 3 changes, so that the rotational speed of the output coupled carrier 22 also changes.
  • the input power is split into two paths through the input shaft 1, one is transmitted to the input large gear 21, the other is divided into two through the overrunning clutch 8, and one is transmitted to the input pinion 23 through the variable speed fluid coupling 3, and the other path is passed. It is transmitted to the input small ring gear 29, and the input large gear 21 and the input pinion 23 converge the planetary gears 20 transmitted to the respective powers through the output coupling carrier 22 to the output coupling carrier 22, and the output coupling planet carrier 22 passes through the output.
  • the gear pair 7 is transmitted to the input gear pair 6, and the input gear pair 6 is divided into two paths, one way is transmitted to the input large ring gear 28, at this time, the input large ring gear 28 and the input small ring gear 29 are transmitted to their respective powers.
  • the planetary gears 20 on the output carrier 27 merge with the output carrier 27, and the output carrier 27 is transmitted to the output shaft 5 of the present invention, thereby realizing the external output of the engine power through the output shaft 5.
  • 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 way is transmitted to the input large gear 21, the other way is divided into two by the overrunning clutch 8, one is transmitted to the input pinion 23 through the variable speed fluid coupling 3, and the other is transmitted to the input small ring gear. 29.
  • the input bull gear 21 and the input pinion 23 converge the planetary gears 20 that are transmitted to the respective powers through the output coupling carrier 22 to the output coupling carrier 22, and the output coupled carrier 22 is then transmitted to the input through the output gear pair 7.
  • the gear pair 6 and the input gear pair 6 are split into two paths, one way to the input large ring gear 28, at which time the input large ring gear 28 and the input small ring gear 29 are transmitted to their respective powers through the output carrier 27.
  • the planetary gear 20 merges with the output carrier 27, and the output carrier 27 is transmitted to the output shaft 5 of the present invention, thereby realizing the external output of the engine power through the output shaft 5.
  • the output coupling planet carrier 22 repeats the above process, so that the rotational speed transmitted to the input large ring gear 28 is constantly changing, and the input large ring gear 28 and the input small ring gear 29 are transmitted to their respective powers through the output planet carrier.
  • the planet gears 20 on 27 converge on the output planet carrier 27, and the output planet carrier 27 is transmitted to the output shaft 5 of the present invention.

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

Abstract

L'invention concerne un coupleur hydraulique à vitesse variable et démarreur composite qui comprend : un arbre d'entrée (1), un coupleur hydraulique à vitesse variable (3), un second embrayage unidirectionnel (4), un arbre de sortie (5), un mécanisme de point neutre (6), une paire d'engrenages d'entrée (7), un engrenage de sortie (8), un embrayage électromagnétique (9), une paire d'engrenages de sortie (10), un premier embrayage unidirectionnel (11), une paire d'engrenages de démarreur (12), une paire d'engrenages de démarrage (13) et un embrayage à inertie (14) ; l'arbre d'entrée (1) étant relié à la paire d'engrenages d'entrée (13) et à l'embrayage à inertie (14) ; l'extrémité de sortie (62) du mécanisme de point neutre (6) étant reliée à l'arbre de sortie (5) ; l'extrémité de sortie (32) du coupleur hydraulique à vitesse variable (3) étant reliée à une grande couronne dentée d'entrée (23) ; ledit coupleur/démarreur comprenant également des liaisons entre lesdits composants et d'autres composants.
PCT/CN2016/088751 2015-07-07 2016-07-06 Coupleur hydraulique à vitesse variable et démarreur composite Ceased WO2017005187A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201680039159.1A CN107923508A (zh) 2015-07-07 2016-07-06 一种复合式调速型液力偶合器以及起动器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201510389864.1A CN105003608A (zh) 2015-07-07 2015-07-07 一种复合式调速型液力偶合器以及起动器
CN201510389864.1 2015-07-07

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Publication Number Publication Date
WO2017005187A1 true WO2017005187A1 (fr) 2017-01-12

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PCT/CN2016/088751 Ceased WO2017005187A1 (fr) 2015-07-07 2016-07-06 Coupleur hydraulique à vitesse variable et démarreur composite

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CN (2) CN105003608A (fr)
HK (1) HK1211672A1 (fr)
WO (1) WO2017005187A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105003608A (zh) * 2015-07-07 2015-10-28 吴志强 一种复合式调速型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
US3425297A (en) * 1965-11-01 1969-02-04 Inpower Works Ltd Fluid torque transmitter
EP0521769A1 (fr) * 1991-07-03 1993-01-07 Regie Nationale Des Usines Renault S.A. Dispositif de changement de vitesses automatique transversal en bout à double descente d'engrenages
CN102062193A (zh) * 2010-07-07 2011-05-18 吴志强 一种复合式调速型液力偶合器
CN104455299A (zh) * 2014-12-12 2015-03-25 吴志强 一种复合型恒充式液力偶合器以及起动器
CN104482161A (zh) * 2014-12-12 2015-04-01 吴志强 一种复合式液力异型偶合器以及起动器
CN104534054A (zh) * 2014-12-12 2015-04-22 吴志强 一种复合式调速型液力偶合器以及起动器
CN105003608A (zh) * 2015-07-07 2015-10-28 吴志强 一种复合式调速型液力偶合器以及起动器

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3425297A (en) * 1965-11-01 1969-02-04 Inpower Works Ltd Fluid torque transmitter
EP0521769A1 (fr) * 1991-07-03 1993-01-07 Regie Nationale Des Usines Renault S.A. Dispositif de changement de vitesses automatique transversal en bout à double descente d'engrenages
CN102062193A (zh) * 2010-07-07 2011-05-18 吴志强 一种复合式调速型液力偶合器
CN104455299A (zh) * 2014-12-12 2015-03-25 吴志强 一种复合型恒充式液力偶合器以及起动器
CN104482161A (zh) * 2014-12-12 2015-04-01 吴志强 一种复合式液力异型偶合器以及起动器
CN104534054A (zh) * 2014-12-12 2015-04-22 吴志强 一种复合式调速型液力偶合器以及起动器
CN105003608A (zh) * 2015-07-07 2015-10-28 吴志强 一种复合式调速型液力偶合器以及起动器

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CN107923508A (zh) 2018-04-17
HK1211672A1 (en) 2016-05-27
CN105003608A (zh) 2015-10-28

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