WO2017005176A1 - Coupleur hydraulique combiné de broyeur à carter, et démarreur - Google Patents

Coupleur hydraulique combiné de broyeur à carter, et démarreur Download PDF

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Publication number
WO2017005176A1
WO2017005176A1 PCT/CN2016/088740 CN2016088740W WO2017005176A1 WO 2017005176 A1 WO2017005176 A1 WO 2017005176A1 CN 2016088740 W CN2016088740 W CN 2016088740W WO 2017005176 A1 WO2017005176 A1 WO 2017005176A1
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WO
WIPO (PCT)
Prior art keywords
input
gear
output
carrier
shaft
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Application number
PCT/CN2016/088740
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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 CN201680039167.6A priority Critical patent/CN107709836A/zh
Publication of WO2017005176A1 publication Critical patent/WO2017005176A1/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
    • 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 couplings and starting, and more particularly to a composite box-grinding 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 composite box-grinding 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.
  • Composite box-grinding fluid coupling and starter including input shaft (1), fixed one-way clutch (3), box-grinding fluid coupling (4), output shaft (5), empty gear Mechanism (6), input gear (7), coupling shaft (8), output gear pair (9), starter gear pair (10), electromagnetic clutch (11), input start gear pair (12), overrunning clutch (13 a fixed shaft (14), between the input shaft (1) and the output shaft (5), a planetary gear (20), an output carrier (21), an input ring gear (22), and an input gear (23) ), output gear (24), input planet carrier (25), fixed gear (26), fixed planet carrier (27), output small ring gear (28), input large ring gear (29), input shaft (1) and
  • the output gear (122) of the input starter gear pair (12) and the input end (131) of the overrunning clutch (13) are coupled, the output end (132) of the overrunning clutch (13) and the input ring gear (22) and the starter gear pair
  • the output gear (102) of (10) is coupled, the output gear (102) of the starter gear pair (
  • Planetary gear (20) on planet carrier (21) and output planet carrier (21 The input gears (23) cooperate with each other, the output carrier (21) is coupled to the input gear (91) of the output gear pair (9), and the input end of the coupling shaft (8) and the empty gear mechanism (6) (61) ), the input gear (7), the output gear (92) of the output gear pair (9), and the input end (111) of the electromagnetic clutch (11) are coupled, and the output end (62) and output shaft of the idle gear mechanism (6) (5) Coupling, the output end (112) of the electromagnetic clutch (11) is coupled with the input gear (121) of the input start gear pair (12), the input gear (7) is meshed with the input large ring gear (29), and the input large teeth
  • the ring (29) cooperates with the fixed planet carrier (27) and the output small ring gear (28) through the planetary gear (20) on the fixed planet carrier (27), and outputs a small ring gear (28) and a box-grinding hydraulic force.
  • the input end (41) of the coupling (4) is coupled, and the output end (42) of the box-grinding fluid coupling (4) is coupled to the input carrier (25), and the planetary gears passing through the input planet carrier (25) (20) Cooperating with the output gear (24) and the fixed gear (26), the output gear (24) is coupled with the input gear (23) and the output end (32) of the fixed one-way clutch (3), and the fixed gear (26) ) and the fixed planet carrier (27) is connected to the fixed shaft (14)
  • the input end (31) of the fixed one-way clutch (3) and the fixed shaft (14) are coupled to the fixed element.
  • a composite box-grinding fluid coupling comprising an input shaft (1), a one-way clutch (3), a box-grinding fluid coupling (4), an output shaft (5), an input gear (6), and a coupling An input gear (7) and an output gear pair (8), wherein the input shaft (1) and the output shaft (5) are provided with a planetary gear (20), an input pinion (21), and an input carrier (22).
  • 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.
  • the box-grinding fluid coupling can be replaced by an external hydraulic torque converter of the relief valve.
  • 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 box-grinding 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 box-grinding fluid coupling and a starter include an input shaft 1 , a fixed one-way clutch 3 , a box-grinding fluid coupling 4 , an output shaft 5 , and an idle gear mechanism. 6.
  • the input shaft 1 is coupled to the output gear 122 of the input starter gear pair 12 and the input end 131 of the overrunning clutch 13, and the output end 132 of the overrunning clutch 13 is coupled to the input ring gear 22 and the output gear 102 of the starter gear pair 10, the starter The output gear 102 of the gear pair 10 cooperates with the input gear 101 of the starter gear pair 10, and the input ring gear 22 cooperates with the output carrier 21 and the input gear 23 through the planetary gear 20 on the output carrier 21 to output the planet.
  • the input gear 91 of the wheel set 9 is coupled, and the coupling shaft 8 is coupled to the input end 61 of the neutral gear mechanism 6, the input gear 7, the output gear 92 of the output gear pair 9, and the input end 111 of the electromagnetic clutch 11, and the idle gear mechanism 6
  • the output end 62 is coupled to the output shaft 5
  • the output end 112 of the electromagnetic clutch 11 is coupled to the input gear 121 of the input starter gear pair 12
  • the input gear 7 is meshed with the input large ring gear 29, and the input large ring gear 29 is passed through the fixed carrier 27
  • the upper planetary gear 20 cooperates with the fixed carrier 27 and the output small ring gear 28, and the output small ring gear 28 is coupled with the input end 41 of the box-grinding fluid coupling 4, and the output of the box-grinding fluid coupling 4
  • the end 42 is coupled to the input carrier 25, the input carrier 25 is coupled to the output gear 24 and the fixed gear 26 via the planetary gear 20 thereon, and the output gear 24 is coupled to the input gear 23 and the output 32
  • the idle gear mechanism 6 is disengaged and the electromagnetic clutch 11 is engaged.
  • the input power of the starter is transmitted to the input ring gear 22 via the starter gear pair 10, and the input ring gear 22 is transmitted to the input gear carrier 22 through the planetary gear 20 on the output carrier 21.
  • the output carrier 21, the output carrier 21 is then transmitted to the input shaft 1 through the output gear pair 9, the coupling shaft 8, the electromagnetic clutch 11 and the input start gear pair 12, and then transmitted to the engine crankshaft, and the generated power is sufficient to overcome the engine start.
  • the resistance is reached, the engine starts.
  • the idle gear mechanism 6 After the engine is started, the idle gear mechanism 6 is engaged, the electromagnetic clutch 11 is disengaged, and the input ring gear 22 transmits the power transmitted from the engine to the input shaft 1 and the overrunning clutch 13 through the planetary gears 20 on the output carrier 21, and is transmitted to the output.
  • the carrier 21, the output carrier 21 is transmitted to the coupling shaft 8 through the output gear pair 9, the coupling shaft 8 splits the power transmitted thereto into two paths, one way through the idle gear mechanism 6 is transmitted to the output shaft 5 of the present invention;
  • the other path is transmitted to the input large ring gear 29 through the input gear 7, and the input large ring gear 29 is transmitted to the output small ring gear 28 through the planetary gear 20 on the fixed carrier 27, and the output small ring gear 28 is fluidly coupled by the box grinding type.
  • the device 4 is transmitted to the input carrier 25, and the input carrier 25 is transmitted to the output gear 24 through the planetary gear 20 thereon, and the output gear 24 is transmitted to the input gear 23, and transmitted to
  • the power input to the gear 23 and the power transmitted from the engine through the input shaft 1 and the overrunning clutch 13 to the input ring gear 22 are transmitted to the output carrier 21 through the planetary gears 20 on the output carrier 21, and the output carrier 21 is again
  • the repetitive cycle of shifting between the components is continuously performed, wherein the output rotational speed of the box-grinding fluid coupling 4 continuously shifts steplessly with changes in input power and running resistance, thereby causing the output speed of the output carrier 21 It is also constantly changing, and is transmitted to the output shaft 5 of the present invention through the output gear pair 9, the coupling shaft 8, and the neutral gear mechanism 6, thereby achieving external output of the engine power through the output shaft 5.
  • the torque on the output carrier 21, the input gear 23, and the output shaft 5 varies with the change in the rotational speed thereof, and the lower the rotational speed
  • the transmission to the output carrier 21, the input gear 23 And the torque on the output shaft 5 is larger, and conversely, the smaller, thereby realizing the composite box-grinding fluid coupling and the starter which can change the torque and the speed according to the difference in the running resistance of the vehicle.
  • the idle gear mechanism 6 When the invention is used, before the engine is started, the idle gear mechanism 6 is disengaged, the electromagnetic clutch 11 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 input ring gear 22 through the starter gear pair 10, Wherein, since no power flows into the input gear 23 at this time, and the input end 31 of the fixed one-way clutch 3 is coupled with the fixed element, the steering is restricted to make the input gear 23 unable to rotate opposite to the engine, and the rotational speed is zero.
  • 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 11 is separated, and the output shaft 5 is rotated.
  • the input power of the engine is transmitted to the input ring gear 22 via the input shaft 1 and the overrunning clutch 13, wherein since no power flows into the input gear 23 at this time, and the input end 31 of the fixed one-way clutch 3 is coupled to the fixed element,
  • the function of limiting the steering is such that the input gear 23 cannot rotate opposite to the steering of the engine, and the rotational speed is zero.
  • the power transmitted to the input ring gear 22 is transmitted to the output through the planetary gear 20 on the output carrier 21.
  • the planet carrier 21, the output planet carrier 21 is transmitted to the coupling shaft 8 through the output gear pair 9, and the coupling shaft 8 diverts the power transmitted thereto into two paths, one pass through the idle gear mechanism 6 to the output shaft 5 of the present invention,
  • the torque transmitted to the output shaft 5 the traction generated by the drive train to the drive wheel is sufficient to overcome the starting resistance of the car, the car starts and begins to increase.
  • the other path is transmitted to the input large ring gear 29 through the input gear 7, and the input large ring gear 29 is transmitted to the output small ring gear 28 through the planetary gear 20 on the fixed carrier 27, and the output small ring gear 28 is passed through the box grinding type hydraulic force.
  • the coupling 4 is transmitted to the input carrier 25, and the input carrier 25 is transmitted to the output gear 24 through the planetary gears 20 on the input carrier 25, and the output gear 24 is transmitted to the output carrier 21 for transmission to the output carrier 21.
  • the power transmitted from the engine through the input shaft 1 and the overrunning clutch 13 to the input ring gear 22 is transmitted to the output carrier 21 through the planetary gears 20 on the output carrier 21, and the output carrier 21 is continuously between the components.
  • the repeated cycle of the shifting is performed, wherein the output rotational speed of the box-grinding fluid coupling 4 is continuously steplessly changed in accordance with the change in the running resistance, so that the output rotational speed of the input gear 23 is also constantly changed, and the output gear is passed through
  • the secondary 9, the coupling shaft 8, and the idle gear mechanism 6 are transmitted to the output shaft 5 of the present invention, 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 box-grinding fluid coupling includes an input shaft 1, a one-way clutch 3, a box-grinding fluid coupling 4, an output shaft 5, an input gear 6, and a coupling input gear 7.
  • Output gear pair 8 the input shaft 1 and the output shaft
  • a planetary gear 20 an input pinion 21, an input carrier 22, an output bull gear 23, a fixed carrier 24, an output small ring gear 25, an input large ring gear 26, an output carrier 27, and an input ring gear 28 are provided.
  • the input gear 29 is coupled to the input pinion 21 and the input gear 29.
  • the input pinion 21 cooperates with the input carrier 22 and the output bull gear 23 through the planetary gear 20 on the input carrier 22 to output a large gear.
  • the planetary gears 20 on the planet carrier 24 cooperate with the fixed planet carrier 24 and the output small ring gear 25, and the fixed planet carrier 24 and the input end 31 of the one-way clutch 3 are fixed to the fixed component, and the small ring gear 25 and the box mill are output.
  • the input end 41 of the fluid coupling 4 is coupled, the output 42 of the box-grinding fluid coupling 4 is coupled to the output 32 of the one-way clutch 3 and the input carrier 22, and the input gear 6 is meshed with the input ring gear 28, Input ring gear 28 through the output
  • the planetary gears 20 on the carrier 27 cooperate with the output carrier 27 and the input gear 29, and the output carrier 27 is coupled to the output shaft 5.
  • the input pinion 21 and the input carrier 22 converge the planetary gears 20 transmitted to the respective powers through the input carrier 22 to the output bull gear 23, and since the box-grinding fluid coupling 4 is coupled to the input carrier 22, the input
  • the rotational speed of the carrier 22 can be constantly varied as the rotational speed of the tank-grinding fluid coupling 4 changes, so that the rotational speed of the output bull gear 23 also changes.
  • the input power is split into two paths through the input shaft 1, one is transmitted to the input pinion 21, and the other is transmitted to the input gear 29, and the input pinion 21 converges the power transmitted thereto through the planetary gear 20 on the input carrier 22 to the output.
  • the large gear 23, the output large gear 23 is divided into two paths by coupling the output gear pair 8, one way is transmitted to the input ring gear 28 through the input gear 6, and at this time, the input ring gear 28 and the input 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 power that the other path transmits to the input large ring gear 26 through the coupling input gear 7 increases accordingly, and the input large ring gear 26 passes through the fixed planet carrier 24.
  • the planetary gear 20 transmits power to the output small ring gear 25, and the output small ring gear 25 is transmitted to the input carrier 22 through the box-grinding fluid coupling 4, that is, the input power of the input carrier 22 increases accordingly.
  • the input pinion 21 and the input carrier 22 converge the planetary gears 20 transmitted to the respective powers through the input carrier 22 to the output bull gear 23, and the output bull gear 23 repeats the above process to be transmitted to the input ring gear 28.
  • the rotational speed is constantly changing, the input ring gear 28 and the input gear 29 converge the respective power transmitted through the planetary gear 20 on the output carrier 27 to the output carrier 27, and the output carrier 27 is transmitted to the output shaft 5 of the present invention, thereby It is achieved that the power of the engine is externally output 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 ring gear 28 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 ring gear 28 is. On the contrary, the lower the degree, the composite type of box-grinding fluid coupling which can change the speed according to 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 split is two paths, one is transmitted to the input pinion 21, and the other is transmitted to the input gear 29, and the input pinion 21 converges the power transmitted thereto through the planetary gear 20 on the input carrier 22 to the output bull gear 23, and the output is large.
  • the gear 23 is split into two paths by coupling the output gear pair 8, one path being transmitted through the input gear 6 to the input ring gear 28, at which time the input ring gear 28 and the input gear 29 are transmitted to their respective powers through the output carrier 27.
  • the planet gears 20 converge on the output planet carrier 27,
  • the output carrier 27 is then transmitted to the output shaft 5 of the present invention, thereby realizing the external output of the engine through the output shaft 5, and the torque transmitted to the output shaft 5 is sufficient to be transmitted through the transmission system to the drive wheel.
  • the resistance of the automobile is overcome, the car starts to accelerate.
  • the resistance of the output shaft 5 decreases, the power of the other path transmitted to the input large ring gear 26 through the coupling input gear 7 increases accordingly, and the input large ring gear 26 is increased.
  • the power is transmitted to the output small ring gear 25 through the planetary gears 20 on the fixed carrier 24, and the output small ring gear 25 is transmitted to the input carrier 22 through the box-grinding fluid coupling 4, that is, the input to the input carrier 22.
  • the input pinion 21 and the input carrier 22 converge the planetary gears 20 that are transmitted to the respective powers through the input carrier 22 to the output bull gear 23, and the output gears 23 repeat the above process to transmit
  • the rotational speed to the input ring gear 28 is constantly changing, and the input ring gear 28 and the input gear 29 merge the power transmitted to the respective power through the planetary gear 20 on the output carrier 27 to the output carrier 27, and the output
  • the star frame 27 is transmitted to the output shaft 5 of the present invention, thereby realizing the external output of the engine through the output shaft 5.

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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 combiné de broyeur à carter et un démarreur. Un arbre d'entrée (1) est raccordé à une paire d'engrenages de mise en marche d'entrée (12) et à une extrémité d'entrée (131) d'une roue libre (13). La roue libre (13) est raccordée à une couronne dentée d'entrée (22) et à une paire de couronnes de démarreur (10). Un porte-satellites de sortie (21) est raccordé à une paire d'engrenages de sortie (9). Un arbre de couplage (8) est raccordé à un mécanisme de dérive du zéro (6), à un engrenage d'entrée (7), à la paire d'engrenages de sortie (9), et à un embrayage électromagnétique (11). Le mécanisme de dérive du zéro (6) est raccordé à un arbre de sortie (5). L'embrayage électromagnétique (11) est raccordé à la paire d'engrenages de mise en marche d'entrée (12). L'engrenage d'entrée (7) vient en prise avec une grande couronne d'entrée (29). Un petit engrenage de sortie (28) est raccordé à un coupleur hydraulique de broyeur à carter (4). Le coupleur hydraulique de broyeur à carter (4) est raccordé à un porte-satellites d'entrée (25). Un engrenage de sortie (24) est raccordé à un engrenage d'entrée (23) en tant qu'embrayage à entraînement unidirectionnel fixe (3).
PCT/CN2016/088740 2015-07-07 2016-07-06 Coupleur hydraulique combiné de broyeur à carter, et démarreur WO2017005176A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201680039167.6A CN107709836A (zh) 2015-07-07 2016-07-06 一种复合型箱磨式液力偶合器以及起动器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201510389851.4A CN105042013A (zh) 2015-07-07 2015-07-07 一种复合型箱磨式液力偶合器以及起动器
CN201510389851.4 2015-07-07

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WO2017005176A1 true WO2017005176A1 (fr) 2017-01-12

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CN (2) CN105042013A (fr)
HK (1) HK1216326A1 (fr)
WO (1) WO2017005176A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105042013A (zh) * 2015-07-07 2015-11-11 吴志强 一种复合型箱磨式液力偶合器以及起动器

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102312938A (zh) * 2010-07-07 2012-01-11 吴志强 一种复合型箱磨式液力偶合器
US8747267B2 (en) * 2008-07-10 2014-06-10 Rochester Institute Of Technology Gear-based continuously variable transmission systems and methods thereof
CN103939559A (zh) * 2014-05-07 2014-07-23 吴志强 一种复合型液力传动器
CN104482162A (zh) * 2014-12-12 2015-04-01 吴志强 一种复合型箱体式液力偶合器以及起动器
CN104500680A (zh) * 2014-12-12 2015-04-08 吴志强 一种复合型后辅室延长式限矩型液力偶合器以及起动器
CN104534052A (zh) * 2014-12-12 2015-04-22 吴志强 一种复合型箱磨式液力偶合器以及起动器
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
CN105042013A (zh) * 2015-07-07 2015-11-11 吴志强 一种复合型箱磨式液力偶合器以及起动器

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8747267B2 (en) * 2008-07-10 2014-06-10 Rochester Institute Of Technology Gear-based continuously variable transmission systems and methods thereof
CN102312938A (zh) * 2010-07-07 2012-01-11 吴志强 一种复合型箱磨式液力偶合器
CN103939559A (zh) * 2014-05-07 2014-07-23 吴志强 一种复合型液力传动器
CN104482162A (zh) * 2014-12-12 2015-04-01 吴志强 一种复合型箱体式液力偶合器以及起动器
CN104500680A (zh) * 2014-12-12 2015-04-08 吴志强 一种复合型后辅室延长式限矩型液力偶合器以及起动器
CN104534052A (zh) * 2014-12-12 2015-04-22 吴志强 一种复合型箱磨式液力偶合器以及起动器
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
CN105042013A (zh) * 2015-07-07 2015-11-11 吴志强 一种复合型箱磨式液力偶合器以及起动器

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CN107709836A (zh) 2018-02-16
CN105042013A (zh) 2015-11-11
HK1216326A1 (zh) 2016-11-04

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