WO2017005179A1 - 一种复合型双腔液力偶合器以及起动器 - Google Patents

一种复合型双腔液力偶合器以及起动器 Download PDF

Info

Publication number
WO2017005179A1
WO2017005179A1 PCT/CN2016/088743 CN2016088743W WO2017005179A1 WO 2017005179 A1 WO2017005179 A1 WO 2017005179A1 CN 2016088743 W CN2016088743 W CN 2016088743W WO 2017005179 A1 WO2017005179 A1 WO 2017005179A1
Authority
WO
WIPO (PCT)
Prior art keywords
input
gear
output
coupled
carrier
Prior art date
Application number
PCT/CN2016/088743
Other languages
English (en)
French (fr)
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 CN201680039009.0A priority Critical patent/CN107923506A/zh
Publication of WO2017005179A1 publication Critical patent/WO2017005179A1/zh

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/06—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
    • F16H2702/00—Combinations of two or more transmissions

Definitions

  • the present invention is in the field of fluid couplings and starting, and more particularly, it is a composite double-cavity 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 double-cavity 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.
  • a composite double-cavity fluid coupling and starter comprising an input shaft (1), a fixed one-way clutch (3), a dual-chamber hydraulic coupling (4), an output shaft (5), and an empty gear mechanism ( 6), coupling frame (7), coupling shaft (8), output gear pair (9), electromagnetic clutch (10), starter gear pair (11), input start gear pair (12), overrunning clutch (13), A planetary gear (20), an input carrier (21), an input gear (22), an output gear (23), and a fixed coupling carrier (24) are disposed between the input shaft (1) and the output shaft (5).
  • the output gear (122) and the input end (131) of the overrunning clutch (13) are coupled, the output end (132) of the overrunning clutch (13) and the input gear (22) and the output gear (112) of the starter gear pair (11) Coupling, the output gear (112) of the starter gear pair (11) cooperates with the starter gear pair (101 input gear (111), and the input gear (22) passes through the planetary gears on the input carrier (21) (20) ) with input planet carrier (21), output gear (23) Interworking, the output gear (23) is coupled with the input gear (91) of the coupling frame (7) and the output gear pair (9), and the input end (61) of the coupling shaft (8) and the empty gear mechanism (6), An output gear (92) of the output gear pair (9) and an input end (101) of the electromagnetic clutch (10) are coupled, and an output end (62) of the idle gear mechanism
  • the upper planetary gear (20) cooperates with the fixed carrier (27) and the output ring gear (28), and the output ring gear (28) is coupled with the input end (41) of the double cavity fluid coupling (4).
  • the output end (42) of the dual chamber fluid coupling (4) is coupled to the input ring gear (25), and the input ring gear (25) is fixedly coupled to the planet carrier (20) on the planet carrier (24) and the fixed coupling planet carrier (24)
  • the output pinion gears (26) cooperate with each other, the fixed coupling planet carrier (24) is coupled with the fixed planet carrier (27), the input end (31) of the fixed one-way clutch (3) and the fixed planet carrier (27) are fixed. Coupled with a fixed element, the output pinion (26) Fixing the one-way clutch (3) an output terminal (32) and the input planet carrier (21) is coupled.
  • a composite double-cavity fluid coupling comprising an input shaft (1), a dual-cavity fluid coupling (3), a one-way clutch (4), an output shaft (5), an input gear pair (6), and a coupling input a gear pair (7), an overrunning clutch (8), and an output gear pair (9), wherein the input shaft (1) and the output shaft (5) are provided with a planetary gear (20), an input pinion (21), Output carrier (22), input bull gear (23), input coupling carrier (24), fixed ring gear (25), output gear (26), input small ring gear (27), The input carrier (28), the output large ring gear (29), the input shaft (1) is coupled with the input pinion (21) and the input gear (91) of the output gear pair (9), and the output of the output gear pair (9)
  • the gear (92) is coupled to the input gear (61) of the input gear pair (6) and the input gear (71) of the input input gear pair (7), and the input gear (62) of the input gear pair (6) is coupled to the input carrier ( 28
  • 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 dual chamber fluid coupling can be replaced by a double guide wheel type 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 double chamber for various ground vehicles, ships, railway locomotives, and machine tools. Fluid coupling and starter.
  • 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 double-cavity fluid coupling and a starter include an input shaft 1 , a fixed one-way clutch 3 , a dual-chamber hydraulic coupling 4 , an output shaft 5 , and an idle gear mechanism 6 .
  • the coupling frame 7, the coupling shaft 8, the output gear pair 9, the electromagnetic clutch 10, the starter gear pair 11, the input start gear pair 12, the overrunning clutch 13, and the planetary gear 20 are disposed between the input shaft 1 and the output shaft 5.
  • the frame 27 and the output ring gear 28 cooperate with each other, and the output ring gear 28 is coupled with the input end 41 of the double cavity fluid coupling 4, and the output end 42 of the double cavity fluid coupling 4 is coupled with the input ring gear 25, and the input ring gear is input.
  • the output pinion 26 cooperate with each other, the fixed coupling planet carrier 24 is coupled with the fixed planet carrier 27, the input end 31 of the fixed one-way clutch 3 and the fixed
  • the planet carrier 27 is coupled to a stationary element, and the output pinion 26 and the output 32 of the fixed one-way clutch 3 are coupled to the input carrier 21.
  • the idle gear mechanism 6 is disengaged and the electromagnetic clutch 10 is engaged.
  • the input power of the starter is transmitted to the input gear 22 via the starter gear pair 11, and the input gear 22 is transmitted to the output gear through the planetary gear 20 on the input carrier 21.
  • the output gear 23 is transmitted to the input shaft 1 through the output gear pair 9, the coupling shaft 8, the electromagnetic clutch 10, and the input start gear pair 12, and then transmitted to the engine crankshaft, and the generated power is sufficient to overcome the engine starting resistance when the engine start.
  • the idle gear mechanism 6 After the engine is started, the idle gear mechanism 6 is engaged, the electromagnetic clutch 10 is disengaged, and the input gear 22 transmits the power transmitted from the engine to the input shaft 1 and the overrunning clutch 13 through the planetary gear 20 on the input carrier 21, and is transmitted to the output gear.
  • the output gear 23 diverts the power transmitted thereto into two paths, one through the output gear pair 9, the coupling shaft 8 and the air-gear mechanism 6, and is transmitted to the output shaft 5 of the present invention; the other path is transmitted to the output shaft 5 through the coupling frame 7
  • the ring gear 29 is input, the input ring gear 29 is transmitted to the output ring gear 28 through the planetary gear 20 on the fixed carrier 27, and the output ring gear 28 is passed through the double
  • the cavity fluid coupling 4 is transmitted to the input ring gear 25, and the input ring gear 25 is transmitted to the output pinion 26 through the planetary gear 20 on the fixed coupling carrier 24, and the output pinion 26 is transmitted to the input carrier 21 for transmission to the input.
  • the power of the carrier 21 and the power transmitted by the engine through the input shaft 1 and the overrunning clutch 13 to the input gear 22 are transmitted to the output gear 23 through the planetary gear 20 on the input carrier 21, and the output gear 23 is placed between the components.
  • the repeated cycle of the shifting is continuously performed, wherein the output rotational speed of the dual-chamber hydraulic coupler 4 is continuously steplessly changed in accordance with the change in the input power and the running resistance, so that the output rotational speed of the output gear 23 is also constantly changed.
  • the output gear pair 9, the coupling shaft 8, and the neutral gear mechanism 6 are 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 torque on the input carrier 21, the output gear 23, and the output shaft 5 changes with the change of the rotational speed thereof, and the lower the rotational speed, the transmission to the input carrier 21 and the output gear 23 And the torque on the output shaft 5 is larger, and conversely, the smaller, thereby realizing the composite double-cavity 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 is disengaged, the electromagnetic clutch 10 is engaged, and the engine speed is zero.
  • the starter is started, the input power of the starter is transmitted to the input gear 22 through the gear pair 11 of the starter. Since no power flows into the input carrier 21 at this time, and the input end 31 of the fixed one-way clutch 3 is coupled to the fixed component, the steering is restricted to make the input carrier 21 unable to rotate opposite to the engine, and the rotational speed is zero.
  • the power transmitted to the input gear 22 is transmitted to the output gear 23 through the planetary gear 20 input to the carrier 21, and the output gear 23 is again activated by the output gear pair 9, the coupling shaft 8, the electromagnetic clutch 10, and the input.
  • the gear pair 12 is transmitted to the input shaft 1 and then to the engine crankshaft. When the torque transmitted to the crankshaft of the engine is sufficient to overcome the starting resistance of the engine, the engine starts and begins to accelerate.
  • 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 10 is separated, and the output shaft 5 is rotated.
  • the input power of the engine is transmitted to the input gear 22 via the input shaft 1 and the overrunning clutch 13, wherein since no power flows into the input carrier 21 at this time, and the input end 31 of the fixed one-way clutch 3 is coupled to the fixed member,
  • the function of restricting the steering is such that the input carrier 21 cannot rotate opposite to the engine, and the rotational speed is zero.
  • the power transmitted to the input gear 22 is transmitted to the output through the planetary gear 20 input to the carrier 21.
  • the gear 23 and the output gear 23 divert the power transmitted thereto into two paths, one through the output gear pair 9, the coupling shaft 8 and the idle gear mechanism 6, and transmitted to the output shaft 5 of the present invention; the other path is transmitted through the coupling frame 7.
  • the input ring gear 29 is transmitted to the output ring gear 28 through the planet gears 20 on the fixed planet carrier 27, and the output ring gear 28 is passed through the double chamber fluid coupler.
  • the gear 4 is transmitted to the input ring gear 25, which is transmitted to the output pinion 26 through the planetary gear 20 on the fixed coupling carrier 24, and the output pinion 26 is transmitted to the input carrier 21 for transmission to the input carrier 21.
  • the power and the power transmitted from the engine through the input shaft 1 and the overrunning clutch 13 to the input gear 22 are transmitted to the output gear 23 through the planetary gear 20 on the input carrier 21, and the output gear 23 is continuously shifted between the components.
  • 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 double-cavity fluid coupling includes an input shaft 1, a dual-cavity fluid coupling 3, a one-way clutch 4, an output shaft 5, an input gear pair 6, and a coupling input gear pair 7 Overrunning clutch 8, output gear pair 9, said loss
  • a planetary gear 20, an input pinion 21, an output carrier 22, an input bull gear 23, an input coupling carrier 24, a fixed ring gear 25, an output gear 26, and an input small ring gear 27 are disposed between the input shaft 1 and the output shaft 5.
  • the input carrier 28 and the output large ring gear 29 are coupled to the input pinion 21 and the input gear 91 of the output gear pair 9.
  • the output gear 92 of the output gear pair 9 and the input gear 61 of the input gear pair 6 are coupled.
  • the input gear 71 of the input gear pair 7 is coupled, the output gear 62 of the input gear pair 6 is coupled to the input carrier 28, the output gear 72 of the input input gear pair 7 is coupled to the input end 41 of the one-way clutch 4, and the input pinion 21 is passed
  • the planetary gears 20 on the output carrier 22 cooperate with the output carrier 22 and the input bull gear 23, and the input end 81 of the overrunning clutch 8 is coupled to the output carrier 22 and the input small ring gear 27, and the output end 82 of the overrunning clutch 8 Coupled with the output 42 of the one-way clutch 4 and the input 31 of the dual-chamber fluid coupling 3, the output 32 of the dual-chamber fluid coupling 3 is coupled to the input coupling carrier 24 through which the input coupled planet carrier 24 is coupled Planet gear 20
  • the fixed ring gear 25 and the output gear 26 cooperate with each other, the fixed ring gear 25 is fixed to the fixed component, the output gear 26 is coupled to the input large gear 23, and the input small ring gear 27 is passed through the planetary gear 20 and the input planet
  • the input pinion 21 and the input bull gear 23 converge the planetary gears 20 that are transmitted to the respective powers through the output coupling carrier 21 to the output coupling carrier 22, since the two-chamber hydraulic coupler 3 is associated with the input bull gear 23, Therefore, the rotational speed of the input large gear 23 can be constantly changed as the rotational speed of the dual-chamber hydraulic coupler 3 changes, so that the rotational speed of the output carrier 22 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 split to two through the output gear pair 9, one is transmitted to the input planet carrier 28 through the input gear pair 6, and the other is coupled through the input.
  • the gear pair 7, the one-way clutch 4, the output end 82 of the overrunning clutch 8, and the dual-chamber fluid coupling 3 are transmitted to the input coupling carrier 24, and then transmitted to the input bull gear 23 through the output gear 26, the input pinion 21, the input
  • the large gear 23 converges the planetary gears 20 transmitted to the respective powers through the output carrier 22 to the output carrier 22, and the output carrier 22 is split into two paths through the input end 81 of the overrunning clutch 8, and is transmitted to the input small teeth all the way.
  • the output shaft 5 is such that the power of the engine is externally output through the output shaft 5.
  • the power transmitted from the output end 82 of the overrunning clutch 8 and the dual-chamber fluid coupling 3 to the input coupling carrier 24 is increased.
  • the connecting planet carrier 24 transmits power to the output gear 26 through the planetary gears 20 thereon, and the output gear 26 is transmitted to the input bull gear 23, that is, the input power of the input large gear 23 increases accordingly, and the input pinion 21,
  • the input bull gear 23 converges the planetary gears 20 transmitted to the respective powers through the output carrier 22 to the output carrier 22, and the output carrier 22 repeats the above process to continuously change the rotational speed transmitted to the input small ring gear 27,
  • the input small ring gear 27 and the input carrier 28 converge the planetary gears 20 transmitted to the respective power through the input carrier 28 to the output large ring gear 29, and the output large ring gear 29 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 input to the small ring gear 27 varies with the input power or running resistance of the vehicle, and the lower the resistance, the rotational speed transmitted to the input small ring gear 27.
  • the input power, the input rotational speed and the load of the engine are unchanged, that is, the rotational speed of the input shaft 1
  • the torque is constant.
  • the output shaft 5 Before the car starts, the output shaft 5 has zero speed.
  • the input power of the engine is divided into two paths through the input shaft 1, one is transmitted to the input pinion 21, and the other is split to two paths through the output gear pair 9.
  • One way is transmitted to the input planet carrier 28 through the input gear pair 6, and the other is transmitted to the input coupling planet carrier 24 via the coupled input gear pair 7, the one-way clutch 4, the output 82 of the overrunning clutch 8, and the dual chamber fluid coupling 3 And then transmitted to the input bull gear 23 through the output gear 26, the input pinion 21, the input bull gear 23, and the planetary gear 20 transmitted to the respective power through the output carrier 22 is merged to the output carrier 22, and the output carrier 22 is output.
  • the input 81 of the overrunning clutch 8 By splitting the input 81 of the overrunning clutch 8 into two paths, one way is transmitted to the input small ring gear 27, at which time the input small ring gear 27 and the input carrier 28 pass the respective power through the planetary gears of the input carrier 28. 20 merges with the output large ring gear 29, and the output large ring gear 29 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 carrier 22 repeats the above process so that the rotational speed transmitted to the input small ring gear 27 is constantly changing, and the input small ring gear 27 and the input carrier 28 transmit the respective power through the input carrier 28
  • the upper planetary gear 20 merges with the output large ring gear 29, and the output large ring gear 29 is transmitted to the output shaft 5 of the present invention.
  • the torque transmitted to the output shaft 5 is transmitted through the transmission system to When the traction force generated on the moving wheel is enough to further overcome the resistance of the automobile, the vehicle continues to accelerate, and the rotational speed of the output end 32 of the dual-chamber hydraulic coupling 3 is also gradually increased, and the rotational speed of the input large gear 23 associated with it is also followed. Gradually increasing, so that the rotational speeds on the output carrier 22, the input small ring gear 27, and the output shaft 5 are continuously increased.

Landscapes

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

Abstract

一种复合型双腔液力偶合器以及具有该双腔液力偶合器的起动器，其中输入轴（1）与输入起动齿轮副（12）以及超越离合器（13）联接，超越离合器（13）与输入齿轮（22）以及起动机齿轮副（11）联接，输出齿轮（23）与联接架（7）以及输出齿轮副（9）联接，联接轴（8）与空挂档机构（6）、输出齿轮副（9）以及电磁离合器（10）联接，空挂档机构（6）与输出轴（5）联接，电磁离合器（10）与输入起动齿轮副（12）联接，联接架（7）与输入齿圈（29）联接，输出齿圈（28）与双腔液力偶合器（4）联接，双腔液力偶合器（4）与输入齿圈（25）联接，输出小齿轮（26）以及固定单向离合器（3）与输入行星架（21）联接。

Description

一种复合型双腔液力偶合器以及起动器 技术领域
本发明属于液力偶合器以及起动领域，更具体地说，它是一种用于各种地面车辆、船舶、铁道机车以及机床的复合型双腔液力偶合器以及起动器。
背景技术
目前，液力偶合器都是根据流体静力学等原理来设计的，它所能传递的功率不大，并且效率不高；另外，成本高。
发明内容
本发明克服了现有技术的不足，提供了一种延长发动机的使用寿命，结构简单，操控方便，低成本，节能高效的复合型双腔液力偶合器以及起动器。
为了实现本发明的目的，本发明采用的技术方案以下：
一种复合型双腔液力偶合器以及起动器，包括输入轴(1)、固定单向离合器(3)、双腔液力偶合器(4)、输出轴(5)、空挂档机构(6)、联接架(7)、联接轴(8)、输出齿轮副(9)、电磁离合器(10)、起动机齿轮副(11)、输入起动齿轮副(12)、超越离合器(13)，所述的输入轴(1)与输出轴(5)之间设有行星齿轮(20)、输入行星架(21)、输入齿轮(22)、输出齿轮(23)、固定联接行星架(24)、输入齿圈(25)、输出小齿轮(26)、固定行星架(27)、输出齿圈(28)、输入齿圈(29),输入轴(1)与输入起动齿轮副(12)的输出齿轮(122)以及超越离合器(13)的输入端(131)联接,超越离合器(13)的输出端(132)与输入齿轮(22)以及起动机齿轮副(11)的输出齿轮(112)联接,起动机齿轮副(11)的输出齿轮(112)与起动机齿轮副(101的输入齿轮(111)相互配合工作，输入齿轮(22)通过输入行星架(21)上的行星齿轮(20)与输入行星架(21)、输出齿轮(23)相互配合工作，输出齿轮(23)与联接架(7)以及输出齿轮副(9)的输入齿轮(91)联接，联接轴(8)与空挂档机构(6)的输入端(61)、输出齿轮副(9)的输出齿轮(92)以及电磁离合器(10)的输入端(101)联接，空挂档机构(6)的输出端(62)与输出轴(5)联接，电磁离合器(10)的输出端(102)与输入起动齿轮副(12)的输入齿轮(121)联接，联接架(7)与输入齿圈(29)联接，输入齿圈(29)通过固定行星架(27)上的行星齿轮(20)与固定行星架(27)、输出齿圈(28)相互配合工作，输出齿圈(28)与双腔液力偶合器(4)的输入端(41)联接,双腔液力偶合器(4)的输出端(42)与输入齿圈(25)联接，输入齿圈(25)通过固定联接行星架(24)上的行星齿轮(20)与固定联接行星架(24)、输出小齿轮(26)相互配合工作，固定联接行星架(24)与固定行星架(27)联接，固定单向离合器(3)的输入端(31)以及固定行星架(27)与固定元件联接，输出小齿轮(26)以及固定单向离合器(3)的输出端(32)与输入行星架(21)联接。
一种复合型双腔液力偶合器，包括输入轴(1)、双腔液力偶合器(3)、单向离合器(4)、输出轴(5)、输入齿轮副(6)、联接输入齿轮副(7)、超越离合器(8)、输出齿轮副(9)，所述的输入轴(1)与输出轴(5)之间设有行星齿轮(20)、输入小齿轮(21)、输出行星架(22)、输入大齿轮(23)、输入联接行星架(24)、固定齿圈(25)、输出齿轮(26)、输入小齿圈(27)、 输入行星架(28)、输出大齿圈(29)，输入轴(1)与输入小齿轮(21)以及输出齿轮副(9)的输入齿轮(91)联接,输出齿轮副(9)的输出齿轮(92)与输入齿轮副(6)的输入齿轮(61)以及联接输入齿轮副(7)的输入齿轮(71)联接,输入齿轮副(6)的输出齿轮(62)与输入行星架(28)联接,联接输入齿轮副(7)的输出齿轮(72)与单向离合器(4)的输入端(41)联接,输入小齿轮(21)通过输出行星架(22)上的行星齿轮(20)与输出行星架(22)、输入大齿轮(23)相互配合工作，超越离合器(8)的输入端(81)与输出行星架(22)以及输入小齿圈(27)联接,超越离合器(8)的输出端(82)与单向离合器(4)的输出端(42)以及双腔液力偶合器(3)的输入端(31)联接,双腔液力偶合器(3)的输出端(32)与输入联接行星架(24)联接,输入联接行星架(24)通过其上的行星齿轮(20)与固定齿圈(25)、输出齿轮(26)相互配合工作，固定齿圈(25)与固定元件固接,输出齿轮(26)与输入大齿轮(23)联接,输入小齿圈(27)通过输入行星架(28)上的行星齿轮(20)与输入行星架(28)、输出大齿圈(29)相互配合工作，输出大齿圈(29)与输出轴(5)联接。
所述各个需要联接的元件,而被其它若干元件分隔的元件,可采用中空或联接架的方法,穿过或跨过其它若干元件,与之连接；当联接的元件是齿轮或齿圈时，则相互啮合或联接；所述各个齿轮副以及变速机构的传动比，按实际需要设计。
所述双腔液力偶合器可以选择双导轮式液力变矩器代替。
所述空挂档机构可以选择离合器代替。
本发明应用于车辆时，能够根据车辆行驶时受到阻力的大小，自动地改变输出扭矩以及速度的变化。
本发明具有以下的优点：
(1)本发明大部份功率由齿圈、行星齿轮、行星架、齿轮传递，因而传动功率和传动效率都极大地提高,而且结构简单，更易于维修；
(2)本发明的变矩和变速是自动完成的，能实现高效率的传动，并且除了起步以外，都能使发动机和起动机在最佳范围内工作，与其它变速器相比，在发动机和起动机等效的前提下，它降低了发动机和起动机的制造成本；
(3)本发明使发动机和起动机处于经过济转速区域内运转，也就是使发动机在非常小污染排放的转速范围内工作，避免了发动机在怠速和高速运行时，排放大量废气，从而减少了废气的排放，有利于保护环境；
(4)本发明能利用内部转速差起缓冲和过载保护的作用，有利于延长发动机和传动系以及起动机的使用寿命，另外，当行驶阻力增大，则能使车辆自动降速，反之则升速，有利于提高车辆的行驶性能；
(5)本发明使输入功率不间断，可保证车辆有良好的加速性和较高的平均车速，使发动机的磨损减少，延长了大修间隔里程，有利于提高生产率；
(6)本发明起动时，具有自动变矩和变速的性能，输入功率不间断，不会发生冲击现象，可保证发动机起动平稳、减少噪音，使发动机的起动磨损减少，并延长了起动电机以及蓄电池的使用寿命；
(7)本发明减少了现今起动机的传动机构，降低了制造成本，发动机起动后，只需对起动电机采取制动以及分离的措施，使其停止传动。
另外，本发明是是一种用于各种地面车辆、船舶、铁道机车以及机床的复合型双腔 液力偶合器以及起动器。
附图说明
说明书附图1为本发明实施例一的结构图；
说明书附图2为本发明实施例二的结构图；
附图中两个元件之间的连接处，运用粗实线表示固定连接，细实线表示两个元件可以相对转动。
具体实施方式
下面结合说明书附图与具体实施方式对本发明作进一步的详细说明：
实施例一：
如图1中所示，一种复合型双腔液力偶合器以及起动器，包括输入轴1、固定单向离合器3、双腔液力偶合器4、输出轴5、空挂档机构6、联接架7、联接轴8、输出齿轮副9、电磁离合器10、起动机齿轮副11、输入起动齿轮副12、超越离合器13，所述的输入轴1与输出轴5之间设有行星齿轮20、输入行星架21、输入齿轮22、输出齿轮23、固定联接行星架24、输入齿圈25、输出小齿轮26、固定行星架27、输出齿圈28、输入齿圈29,输入轴1与输入起动齿轮副12的输出齿轮122以及超越离合器13的输入端131联接,超越离合器13的输出端132与输入齿轮22以及起动机齿轮副11的输出齿轮112联接,起动机齿轮副11的输出齿轮112与起动机齿轮副11的输入齿轮111相互配合工作，输入齿轮22通过输入行星架21上的行星齿轮20与输入行星架21、输出齿轮23相互配合工作，输出齿轮23与联接架7以及输出齿轮副9的输入齿轮91联接，联接轴8与空挂档机构6的输入端61、输出齿轮副9的输出齿轮92以及电磁离合器10的输入端101联接，空挂档机构6的输出端62与输出轴5联接，电磁离合器10的输出端102与输入起动齿轮副12的输入齿轮121联接，联接架7与输入齿圈29联接，输入齿圈29通过固定行星架27上的行星齿轮20与固定行星架27、输出齿圈28相互配合工作，输出齿圈28与双腔液力偶合器4的输入端41联接,双腔液力偶合器4的输出端42与输入齿圈25联接，输入齿圈25通过固定联接行星架24上的行星齿轮20与固定联接行星架24、输出小齿轮26相互配合工作，固定联接行星架24与固定行星架27联接，固定单向离合器3的输入端31以及固定行星架27与固定元件联接，输出小齿轮26以及固定单向离合器3的输出端32与输入行星架21联接。
发动机起动前，分离空挂档机构6，接合电磁离合器10，起动机的输入功率经过起动机齿轮副11传递到输入齿轮22，输入齿轮22通过输入行星架21上的行星齿轮20传递到输出齿轮23，输出齿轮23再通过输出齿轮副9、联接轴8、电磁离合器10以及输入起动齿轮副12传递到输入轴1，再传递到发动机曲轴上，产生的起动力足以克服发动机起动阻力时，发动机起动。
发动机起动后，接合空挂档机构6，分离电磁离合器10，输入齿轮22通过输入行星架21上的行星齿轮20把由发动机经过输入轴1以及超越离合器13传递到此的功率，传递到输出齿轮23，输出齿轮23把传递到此的功率分流为两路，一路通过输出齿轮副9、联接轴8以及空挂档机构6，传递到本发明的输出轴5；另一路通过联接架7传递到输入齿圈29，输入齿圈29通过固定行星架27上的行星齿轮20传递到输出齿圈28，输出齿圈28则通过双 腔液力偶合器4传递到输入齿圈25，输入齿圈25通过固定联接行星架24上的行星齿轮20传递到输出小齿轮26，输出小齿轮26再传递到输入行星架21，传递到输入行星架21的功率以及由发动机经过输入轴1以及超越离合器13传递到输入齿轮22的功率，则通过输入行星架21上的行星齿轮20传递到输出齿轮23，输出齿轮23再在各个元件之间不断地进行变速的反复循环，其中，双腔液力偶合器4的输出转速不断地随着输入功率、行驶阻力的变化而无级地变速，从而使输出齿轮23的输出转速也不断地变化，并且通过输出齿轮副9、联接轴8以及空挂档机构6传递至本发明的输出轴5,从而实现了把发动机的功率通过输出轴5对外输出。
对于本发明，当输入轴1的转速不变，输入行星架21、输出齿轮23以及输出轴5上的扭矩随其转速的变化而变化，转速越低，传递到输入行星架21、输出齿轮23以及输出轴5上的扭矩就越大，反之，则越小，从而实现本发明能随车辆行驶阻力的不同，改变力矩以及速度的复合型双腔液力偶合器以及起动器。
本发明使用时，发动机起动前，分离空挂档机构6，接合电磁离合器10，发动机的转速为零，当起动机启动，起动机的输入功率经过起动机齿轮副11传递到输入齿轮22,其中，由于此时没有功率流入输入行星架21，并且固定单向离合器3的输入端31与固定元件联接，起限制转向的作用，使输入行星架21不能与发动机相反的转向转动，转速为零，此时，传递到输入齿轮22的功率，则通过输入行星架21上的行星齿轮20把功率传递到输出齿轮23，输出齿轮23再通过输出齿轮副9、联接轴8、电磁离合器10以及输入起动齿轮副12传递到输入轴1，再传递到发动机曲轴上，当传递到发动机的曲轴上的扭矩，产生的起动力足以克服发动机的起动阻力时，发动机则起动并开始加速。
发动机起动后，设发动机的输入功率、输入转速及其负荷不变，即输入轴1的转速与扭矩为常数，汽车起步前，接合空挂档机构6，分离电磁离合器10，输出轴5的转速为零，发动机的输入功率经过输入轴1以及超越离合器13，传递到输入齿轮22，其中，由于此时没有功率流入输入行星架21，并且固定单向离合器3的输入端31与固定元件联接，起限制转向的作用，使输入行星架21不能与发动机相反的转向转动，转速为零，此时，传递到输入齿轮22的功率，则通过输入行星架21上的行星齿轮20把功率传递到输出齿轮23，输出齿轮23把传递到此的功率分流为两路，一路通过输出齿轮副9、联接轴8以及空挂档机构6，传递到本发明的输出轴5；另一路通过联接架7传递到输入齿圈29，输入齿圈29通过固定行星架27上的行星齿轮20传递到输出齿圈28，输出齿圈28则通过双腔液力偶合器4传递到输入齿圈25，输入齿圈25通过固定联接行星架24上的行星齿轮20传递到输出小齿轮26，输出小齿轮26再传递到输入行星架21，传递到输入行星架21的功率以及由发动机经过输入轴1以及超越离合器13传递到输入齿轮22的功率，则通过输入行星架21上的行星齿轮20传递到输出齿轮23，输出齿轮23再在各个元件之间不断地进行变速的反复循环，其中，双腔液力偶合器4的输出转速不断地随着行驶阻力的变化而无级地变速，从而使输入齿轮23的输出转速也不断地变化，并且通过输出齿轮副9、联接轴8以及空挂档机构6传递至本发明的输出轴5,从而使输出轴5的扭矩随着转速的增加而减少。
实施例二：
如图2中所示，一种复合型双腔液力偶合器，包括输入轴1、双腔液力偶合器3、单向离合器4、输出轴5、输入齿轮副6、联接输入齿轮副7、超越离合器8、输出齿轮副9，所述的输 入轴1与输出轴5之间设有行星齿轮20、输入小齿轮21、输出行星架22、输入大齿轮23、输入联接行星架24、固定齿圈25、输出齿轮26、输入小齿圈27、输入行星架28、输出大齿圈29，输入轴1与输入小齿轮21以及输出齿轮副9的输入齿轮91联接,输出齿轮副9的输出齿轮92与输入齿轮副6的输入齿轮61以及联接输入齿轮副7的输入齿轮71联接,输入齿轮副6的输出齿轮62与输入行星架28联接,联接输入齿轮副7的输出齿轮72与单向离合器4的输入端41联接,输入小齿轮21通过输出行星架22上的行星齿轮20与输出行星架22、输入大齿轮23相互配合工作，超越离合器8的输入端81与输出行星架22以及输入小齿圈27联接,超越离合器8的输出端82与单向离合器4的输出端42以及双腔液力偶合器3的输入端31联接,双腔液力偶合器3的输出端32与输入联接行星架24联接,输入联接行星架24通过其上的行星齿轮20与固定齿圈25、输出齿轮26相互配合工作，固定齿圈25与固定元件固接,输出齿轮26与输入大齿轮23联接,输入小齿圈27通过输入行星架28上的行星齿轮20与输入行星架28、输出大齿圈29相互配合工作，输出大齿圈29与输出轴5联接。
输入小齿轮21、输入大齿轮23把传递到各自的功率通过输出联接行星架21上的行星齿轮20汇流于输出联接行星架22，由于双腔液力偶合器3与输入大齿轮23相互关联,所以输入大齿轮23的转速可以不断地随着双腔液力偶合器3转速的变化而变化,从而使输出行星架22的转速也随之变化。
输入功率经过输入轴1分流为两路，一路传递到输入小齿轮21，另一路经过输出齿轮副9再分流为两路，一路通过输入齿轮副6传递到输入行星架28，另一路通过联接输入齿轮副7、单向离合器4、超越离合器8的输出端82以及双腔液力偶合器3传递到输入联接行星架24，再通过输出齿轮26传递到输入大齿轮23，输入小齿轮21、输入大齿轮23把传递到各自的功率通过输出行星架22上的行星齿轮20汇流于输出行星架22，输出行星架22再通过超越离合器8的输入端81分流为两路，一路传递到输入小齿圈27，此时，输入小齿圈27与输入行星架28把传递到各自的功率通过输入行星架28上的行星齿轮20汇流于输出大齿圈29，输出大齿圈29则传递至本发明的输出轴5,从而实现了把发动机的功率通过输出轴5对外输出。
当发动机的输入功率增大或者输出轴5的阻力减少时，另一路通过超越离合器8的输出端82以及双腔液力偶合器3传递到输入联接行星架24的功率随之而增大，输入联接行星架24则通过其上的行星齿轮20把功率传递到输出齿轮26，输出齿轮26再传递到输入大齿轮23，即输入大齿轮23的输入功率随之而增大，输入小齿轮21、输入大齿轮23把传递到各自的功率通过输出行星架22上的行星齿轮20汇流于输出行星架22，输出行星架22再重复上述过程，使传递到输入小齿圈27上的转速不断变化，输入小齿圈27与输入行星架28把传递到各自的功率通过输入行星架28上的行星齿轮20汇流于输出大齿圈29，输出大齿圈29则传递到本发明的输出轴5,从而实现了把发动机的功率通过输出轴5对外输出。
对于本发明，当输入轴1的转速不变，输入小齿圈27上的转速，则随着车辆输入功率或者行驶阻力的不同而变化，阻力越低，传递到输入小齿圈27上的转速就越高，反之，则越低，从而实现本发明能随着车辆输入功率或者行驶阻力的不同而改变速度的复合型双腔液力偶合器。
本发明使用时，设发动机的输入功率、输入转速及其负荷不变，即输入轴1的转速 与扭矩为常数，汽车起步前，输出轴5的转速为零，发动机的输入功率经过输入轴1分流为两路，一路传递到输入小齿轮21，另一路经过输出齿轮副9再分流为两路，一路通过输入齿轮副6传递到输入行星架28，另一路通过联接输入齿轮副7、单向离合器4、超越离合器8的输出端82以及双腔液力偶合器3传递到输入联接行星架24，再通过输出齿轮26传递到输入大齿轮23，输入小齿轮21、输入大齿轮23把传递到各自的功率通过输出行星架22上的行星齿轮20汇流于输出行星架22，输出行星架22再通过超越离合器8的输入端81分流为两路，一路传递到输入小齿圈27，此时，输入小齿圈27与输入行星架28把传递到各自的功率通过输入行星架28上的行星齿轮20汇流于输出大齿圈29，输出大齿圈29则传递至本发明的输出轴5,从而实现了把发动机的功率通过输出轴5对外输出。
当传递到输出轴5上的扭矩，经过传动系统传动到驱动轮上产生的牵引力足以克服汽车行阻力时,汽车则开始加速，此时，当输出轴5的阻力减少时，另一路通过超越离合器8的输出端82以及双腔液力偶合器3传递到输入联接行星架24的功率随之而增大，输入联接行星架24则通过其上的行星齿轮20把功率传递到输出齿轮26，输出齿轮26再传递到输入大齿轮23，即输入大齿轮23的输入功率随之而增大，输入小齿轮21、输入大齿轮23把传递到各自的功率通过输出行星架22上的行星齿轮20汇流于输出行星架22，输出行星架22再重复上述过程，使传递到输入小齿圈27上的转速不断变化，输入小齿圈27与输入行星架28把传递到各自的功率通过输入行星架28上的行星齿轮20汇流于输出大齿圈29，输出大齿圈29则传递到本发明的输出轴5,当传递到输出轴5上的扭矩，经过传动系统传动到驱动轮上产生的牵引力足以进一步克服汽车行阻力时,汽车则继续加速，双腔液力偶合器3的输出端32的转速也逐渐升高，与之相互关联的输入大齿轮23的转速也随之逐渐升高，从而使输出行星架22、输入小齿圈27以及输出轴5上的转速随之增加而不断地升高。

Claims (2)

  1. 一种复合型双腔液力偶合器以及起动器，包括输入轴(1)、固定单向离合器(3)、双腔液力偶合器(4)、输出轴(5)、空挂档机构(6)、联接架(7)、联接轴(8)、输出齿轮副(9)、电磁离合器(10)、起动机齿轮副(11)、输入起动齿轮副(12)、超越离合器(13)，其特征在于：所述的输入轴(1)与输出轴(5)之间设有行星齿轮(20)、输入行星架(21)、输入齿轮(22)、输出齿轮(23)、固定联接行星架(24)、输入齿圈(25)、输出小齿轮(26)、固定行星架(27)、输出齿圈(28)、输入齿圈(29),输入轴(1)与输入起动齿轮副(12)的输出齿轮(122)以及超越离合器(13)的输入端(131)联接,超越离合器(13)的输出端(132)与输入齿轮(22)以及起动机齿轮副(11)的输出齿轮(112)联接,起动机齿轮副(11)的输出齿轮(112)与起动机齿轮副(11)的输入齿轮(111)相互配合工作，输入齿轮(22)通过输入行星架(21)上的行星齿轮(20)与输入行星架(21)、输出齿轮(23)相互配合工作，输出齿轮(23)与联接架(7)以及输出齿轮副(9)的输入齿轮(91)联接，联接轴(8)与空挂档机构(6)的输入端(61)、输出齿轮副(9)的输出齿轮(92)以及电磁离合器(10)的输入端(101)联接，空挂档机构(6)的输出端(62)与输出轴(5)联接，电磁离合器(10)的输出端(102)与输入起动齿轮副(12)的输入齿轮(121)联接，联接架(7)与输入齿圈(29)联接，输入齿圈(29)通过固定行星架(27)上的行星齿轮(20)与固定行星架(27)、输出齿圈(28)相互配合工作，输出齿圈(28)与双腔液力偶合器(4)的输入端(41)联接,双腔液力偶合器(4)的输出端(42)与输入齿圈(25)联接，输入齿圈(25)通过固定联接行星架(24)上的行星齿轮(20)与固定联接行星架(24)、输出小齿轮(26)相互配合工作，固定联接行星架(24)与固定行星架(27)联接，固定单向离合器(3)的输入端(31)以及固定行星架(27)与固定元件联接，输出小齿轮(26)以及固定单向离合器(3)的输出端(32)与输入行星架(21)联接。
  2. 一种复合型双腔液力偶合器，包括输入轴(1)、双腔液力偶合器(3)、单向离合器(4)、输出轴(5)、输入齿轮副(6)、联接输入齿轮副(7)、超越离合器(8)、输出齿轮副(9)，其特征在于：所述的输入轴(1)与输出轴(5)之间设有行星齿轮(20)、输入小齿轮(21)、输出行星架(22)、输入大齿轮(23)、输入联接行星架(24)、固定齿圈(25)、输出齿轮(26)、输入小齿圈(27)、输入行星架(28)、输出大齿圈(29)，输入轴(1)与输入小齿轮(21)以及输出齿轮副(9)的输入齿轮(91)联接,输出齿轮副(9)的输出齿轮(92)与输入齿轮副(6)的输入齿轮(61)以及联接输入齿轮副(7)的输入齿轮(71)联接,输入齿轮副(6)的输出齿轮(62)与输入行星架(28)联接,联接输入齿轮副(7)的输出齿轮(72)与单向离合器(4)的输入端(41)联接,输入小齿轮(21)通过输出行星架(22)上的行星齿轮(20)与输出行星架(22)、输入大齿轮(23)相互配合工作，超越离合器(8)的输入端(81)与输出行星架(22)以及输入小齿圈(27)联接,超越离合器(8)的输出端(82)与单向离合器(4)的输出端(42)以及双腔液力偶合器(3)的输入端(31)联接,双腔液力偶合器(3)的输出端(32)与输入联接行星架(24)联接,输入联接行星架(24)通过其上的行星齿轮(20)与固定齿圈(25)、输出齿轮(26)相互配合工作，固定齿圈(25)与固定元件固接,输出齿轮(26)与输入大齿轮(23)联接,输入小齿圈(27)通过输入行星架(28)上的行星齿轮(20)与输入行星架(28)、输出大齿圈(29)相互配合工作，输出大齿圈(29)与输出轴(5)联接。
PCT/CN2016/088743 2015-07-07 2016-07-06 一种复合型双腔液力偶合器以及起动器 WO2017005179A1 (zh)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201680039009.0A CN107923506A (zh) 2015-07-07 2016-07-06 一种复合型双腔液力偶合器以及起动器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201510389855.2A CN105134904A (zh) 2015-07-07 2015-07-07 一种复合型双腔液力偶合器以及起动器
CN201510389855.2 2015-07-07

Publications (1)

Publication Number Publication Date
WO2017005179A1 true WO2017005179A1 (zh) 2017-01-12

Family

ID=54720383

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2016/088743 WO2017005179A1 (zh) 2015-07-07 2016-07-06 一种复合型双腔液力偶合器以及起动器

Country Status (3)

Country Link
CN (2) CN105134904A (zh)
HK (1) HK1216333A1 (zh)
WO (1) WO2017005179A1 (zh)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105134904A (zh) * 2015-07-07 2015-12-09 吴志强 一种复合型双腔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
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
CN104633040A (zh) * 2014-12-12 2015-05-20 吴志强 一种复合型双腔液力偶合器以及起动器
CN105134904A (zh) * 2015-07-07 2015-12-09 吴志强 一种复合型双腔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
CA2322883C (en) * 1998-03-06 2004-08-10 Voith Turbo Gmbh & Co., Kg Hydrodynamic-mechanical multi-speed compound transmission, especially a six-speed torque-converter transmission

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
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
CN104633040A (zh) * 2014-12-12 2015-05-20 吴志强 一种复合型双腔液力偶合器以及起动器
CN105134904A (zh) * 2015-07-07 2015-12-09 吴志强 一种复合型双腔液力偶合器以及起动器

Also Published As

Publication number Publication date
CN105134904A (zh) 2015-12-09
CN107923506A (zh) 2018-04-17
HK1216333A1 (zh) 2016-11-04

Similar Documents

Publication Publication Date Title
WO2017005177A1 (zh) 一种复合型箱体式液力偶合器以及起动器
WO2017005184A1 (zh) 一种复合式限矩型水介质液力偶合器以及起动器
CN101761630B (zh) 一种复合型封闭行星锥式无级变速兼起动器
WO2017005181A1 (zh) 一种复合谐波齿轮传动的液力偶合器以及起动器
WO2017005179A1 (zh) 一种复合型双腔液力偶合器以及起动器
WO2016112800A1 (zh) 一种复合型综合式液力变矩器以及无级变速器
WO2017005185A1 (zh) 一种复合型恒充式液力偶合器以及起动器
WO2016112804A1 (zh) 一种复合型轴流式液力变矩器以及无级变速器
WO2017005178A1 (zh) 一种复合型外壳带侧辅室的液力偶合器以及起动器
WO2017005176A1 (zh) 一种复合型箱磨式液力偶合器以及起动器
WO2017005180A1 (zh) 一种复合型后置齿轮箱体式液力偶合器以及起动器
WO2017005182A1 (zh) 一种复合式液力异型偶合器以及起动器
WO2017005183A1 (zh) 一种复合型后辅室延长式限矩型液力偶合器以及起动器
WO2017005186A1 (zh) 一种复合型阀控充液式液力偶合器以及起动器
WO2016112810A1 (zh) 一种复合型叶轮式液力变矩器以及无级变速器
WO2017005187A1 (zh) 一种复合式调速型液力偶合器以及起动器
WO2016112808A1 (zh) 一种复合型向心式液力变矩器以及无级变速器
WO2016112805A1 (zh) 一种复合型双涡轮液力变矩器以及无级变速器
WO2016112809A1 (zh) 一种复合型双泵轮液力变矩器以及无级变速器
WO2016112811A1 (zh) 一种复合型双导轮式液力变矩器以及无级变速器
WO2016112803A1 (zh) 一种复合型导叶可调式液力变矩器以及无级变速器
WO2017004782A1 (zh) 一种复合型液力传动器
WO2016112806A1 (zh) 一种复合型溢流阀外置式液力变矩器以及无级变速器
WO2016112802A1 (zh) 一种复合型可调液力变矩器以及无级变速器
WO2016112801A1 (zh) 一种复合型多元件工作轮液力变矩器以及无级变速器

Legal Events

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

Ref document number: 16820830

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 16820830

Country of ref document: EP

Kind code of ref document: A1