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WO2017005182A1 - 一种复合式液力异型偶合器以及起动器 - Google Patents

一种复合式液力异型偶合器以及起动器 Download PDF

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Publication number
WO2017005182A1
WO2017005182A1 PCT/CN2016/088746 CN2016088746W WO2017005182A1 WO 2017005182 A1 WO2017005182 A1 WO 2017005182A1 CN 2016088746 W CN2016088746 W CN 2016088746W WO 2017005182 A1 WO2017005182 A1 WO 2017005182A1
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Prior art keywords
gear
input
output
coupled
coupling
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PCT/CN2016/088746
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English (en)
French (fr)
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吴志强
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Individual
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Priority to CN201680039010.3A priority Critical patent/CN107923507A/zh
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
    • F16H47/08—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion

Definitions

  • the invention belongs to the field of fluid couplings and starting, and more particularly to a composite hydraulic 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 hydraulic coupling and a starter which prolong the service life of the engine, has a simple structure, is convenient to operate, is low in cost, and is energy-saving and high-efficiency.
  • a composite hydraulic coupling and starter comprising an input shaft (1), a starter gear pair (3), a hydraulic profile coupling (4), a coupling frame (5), an output shaft (6), and an empty Gear shifting mechanism (7), coupling shaft (8), second one-way clutch (9), first one-way clutch (10), output gear pair (11), electromagnetic clutch (12), starting gear pair (13)
  • the overrunning clutch (14) is provided with a planetary gear (20), an input pinion (21), an output carrier (22), and an input large gear (23) between the input shaft (1) and the output shaft (6).
  • the coupling shaft (8) is coupled to the input end (71) of the neutral gear mechanism (7), the output gear (112) of the output gear pair (11), and the input end (121) of the electromagnetic clutch (12), the electromagnetic clutch ( 12)
  • the output gear (122) is coupled to the input gear (131) of the start gear pair (13), the output end (72) of the neutral gear mechanism (7) is coupled to the output shaft (6), and the coupling frame (5) is coupled to
  • the input carrier (29) is coupled, and the input planet carrier (29) cooperates with the fixed ring gear (27) and the output coupling gear (28) through the planetary gear (20) thereon, and the output coupling gear (28) and the input tooth
  • the ring (25) is coupled, and the input ring gear (25) cooperates with the fixed carrier (24) and the output gear (26) through the planetary gear (20) on the fixed carrier (24), and the output gear (26) and the first
  • the input end (91) of the two one-way clutch (9) is coupled, the output end (102) of the first one-way clutch (10)
  • a composite hydraulic profile coupling includes an input shaft (1), a hydraulic profile coupling (3), a one-way clutch (4), an output shaft (5), an output gear pair (6), and an input gear pair ( 7) an overrunning clutch (8) and a coupling gear pair (9), wherein the input shaft (1) and the output shaft (5) are provided with a planetary gear (20), an input gear (21), and an output gear (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 hydraulic profile coupling can be replaced by a multi-element working wheel hydraulic torque converter.
  • the air-locking mechanism can select a clutch instead.
  • the present invention When the present invention is applied to a vehicle, it is possible to automatically change the output torque and the speed change depending on the magnitude of the resistance that the vehicle is subjected to while traveling.
  • the invention enables the engine and the starter to operate in the region of the tempering speed, that is, the engine operates in a range of very small pollution discharge speeds, thereby avoiding the engine discharging a large amount of exhaust gas during idle speed and high speed operation, thereby reducing the number of exhaust gases.
  • the emission of exhaust gas is conducive to protecting the environment;
  • the invention can utilize the effect of internal speed difference to buffer and overload protection, which is beneficial to prolonging the service life of the engine and the drive train and the starter.
  • speed up which is beneficial to improve the driving performance of the vehicle;
  • the invention makes the input power uninterrupted, can ensure the vehicle has good acceleration and high average vehicle speed, reduces the wear of the engine, prolongs the overhaul interval mileage, and is beneficial to improving productivity;
  • the invention reduces the transmission mechanism of the current starter machine, 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 hydraulic profile 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 hydraulic profile coupling and starter includes an input shaft 1 , a starter gear pair 3 , a hydraulic profile coupling 4 , a coupling frame 5 , an output shaft 6 , and an idle gear mechanism 7.
  • the input shaft 1 is coupled to the input end 101 of the first one-way clutch 10, the output gear 132 of the starter gear set 13, and the input end 141 of the overrunning clutch 14, the output end 142 of the overrunning clutch 14 and the input pinion 21 and the starter gear pair
  • the output gear 32 of the starter gear pair 3 is coupled to the input gear 31 of the starter gear pair 3, and the input pinion 21 passes through the planetary gear 20 on the output carrier 22 and the output carrier 22, Input large gear 23 mutual Working together
  • the output carrier 22 is coupled to the coupling frame 5 and the input gear 111 of the output gear pair 11, the coupling shaft 8 and the input end 71 of the idle gear mechanism 7, the output gear pair 112 of the output gear pair 11, and the electromagnetic clutch 12
  • the input end 121 is coupled
  • the output gear 122 of the electromagnetic clutch 12 is coupled to the input gear 131 of the start gear pair 13
  • the output end 72 of the idle gear mechanism 7 is coupled to the output shaft 6, and
  • the coupling frame 5 is coupled to the input carrier 29 to input the planet The
  • the carrier 24 and the output gear 26 cooperate with each other, and the output gear 26 is coupled to the input end 91 of the second one-way clutch 9, the output end 102 of the first one-way clutch 10 and the output end 92 of the second one-way clutch 9 and the liquid
  • the input end 41 of the force-type coupling 4 is coupled, the output end 42 of the hydrodynamic coupling 4 is coupled to the input bull gear 23, the fixed planet carrier 24 is coupled to the fixed ring gear 27, and the fixed ring gear 27 is coupled to the fixed element.
  • the neutral shifting mechanism 7 is disengaged and the electromagnetic clutch 12 is engaged.
  • the input power of the starter is transmitted to the input pinion 21 through the starter gear pair 3, and the input pinion 21 is transmitted to the planetary gear 20 on the output carrier 22 to
  • the output carrier 22, the output carrier 22 is transmitted to the input shaft 1 through the output gear pair 11, the coupling shaft 8, the electromagnetic clutch 12, and the start gear pair 13, and then transmitted to the engine crankshaft, and the generated driving force is sufficient to overcome the engine starting resistance.
  • the idle gear mechanism 7 After the engine is started, the idle gear mechanism 7 is engaged, the electromagnetic clutch 12 is disengaged, and the input shaft 1 splits the power transmitted from the engine into two paths, one pass through the first one-way clutch 10 and the hydraulic profile coupling 4 to the input. Big
  • the gear 23 is passed through the overrunning clutch 14 to the input pinion 21, and the input pinion 21, the input bull gear 23, transmits the respective power to the respective output carrier 22 through the planetary gear 20 on the output carrier 22.
  • the output planet carrier 22 splits the power transmitted thereto into two paths, one through the output gear pair 11, the coupling shaft 8 and the air-gear mechanism 7 to the output shaft 6 of the present invention; the other path is transmitted to the output shaft 6 through the coupling frame 5
  • the input carrier 29 is input to the carrier 29 and transmitted to the output coupling gear 28 via the planetary gear 20 thereon.
  • the output coupling gear 28 is transmitted to the input ring gear 25, and the input ring gear 25 is passed through the planetary gear 20 on the fixed carrier 24.
  • the torque on the input bull gear 23, the output carrier 22, and the output shaft 6 varies with the change of the rotational speed thereof, and the lower the rotational speed, the transmission to the input large gear 23 and the output planet.
  • the torque on the frame 22 and the output shaft 6 is larger, and conversely, the smaller, thereby realizing the composite hydraulic coupling and the starter which can change the torque and speed according to the difference in the running resistance of the present invention.
  • the idle gear mechanism 7 When the invention is used, before the engine is started, the idle gear mechanism 7 is disengaged, the electromagnetic clutch 12 is engaged, and the engine speed is zero.
  • the starter When the starter is started, the input power of the starter is transmitted to the input pinion 21 through the starter gear pair 3, The input pinion 21 transmits power to the output carrier 22 through the planetary gears 20 on the output carrier 22, and the output carrier 22 is transmitted to the input shaft through the output gear pair 11, the coupling shaft 8, the electromagnetic clutch 12, and the start gear pair 13. 1, then transferred to the engine crankshaft, the generated starting power is enough to overcome the engine starting resistance, the engine starts.
  • the input power, input speed and load of the engine are set to be constant, that is, the speed and torque of the input shaft 1 are constant.
  • the idle gear mechanism 7 is engaged, the electromagnetic clutch 12 is separated, and the input shaft 1 is The power split to the engine is divided into two paths, one through the second one-way clutch 10 and the hydrodynamic coupling 4 to the coupled input bull gear 23, the other through the overrunning clutch 14 to the input pinion 21, the input pinion 21.
  • the input bull gear 23 converges the respective powers through the planet gears 20 on the output carrier 22 to the output carrier 22, and the output carrier 22 splits the power transmitted thereto into two paths, one through the output gear pair. 11.
  • the coupling shaft 8 and the idle gear mechanism 7 are transmitted to the output shaft 6 of the present invention; the other passage is transmitted through the coupling frame 5 to the input carrier 29, and the input carrier 29 is transmitted to the output coupling gear through the planetary gear 20 thereon. 28, the output coupling gear 28 is transmitted to the input ring gear 25, and the input ring gear 25 is transmitted to the output gear 26 through the planetary gear 20 on the fixed carrier 24, and the output gear 26 is output.
  • the second one-way clutch 9, the first one-way clutch 10, and the hydrodynamic coupling 4 are transmitted to the input bull gear 23, and the input pinion 21 and the input large gear 23 transmit the respective power to the output carrier 22.
  • the planetary gear 20 merges with the output carrier 22, and the output carrier 22 continuously repeats the shifting of the shifting between the respective components, wherein the output rotational speed of the hydrodynamic coupling 4 is continuously stepless as the running resistance changes. Shifting the ground so that the output rotational speed of the output carrier 22 is also constantly changing, and is transmitted to the output shaft 6 of the present invention through the output gear pair 11, the coupling shaft 8, and the neutral gear mechanism 7, so that the torque of the output shaft 6 is varied. As the speed increases, it decreases.
  • Embodiment 2 is a diagrammatic representation of Embodiment 1:
  • a composite hydraulic profile coupling includes an input shaft 1, a hydraulic profile coupling 3, a one-way clutch 4, an output shaft 5, an output gear pair 6, an input gear pair 7, and an overrunning clutch.
  • Coupling gear pair 9 the input shaft 1 and the output shaft 5 are provided with a planetary gear 20, an input gear 21, an output gear 22, an input carrier 23, a fixed carrier 24, an input ring gear 25, a coupling output gear 26, an input large gear 27, and an output carrier 28.
  • the input pinion 29 is coupled to the input carrier 13 and the input end 81 of the overrunning clutch 8, the input end 81 of the overrunning clutch 8 is coupled to the input gear 61 of the output gear pair 6, and the output gear 62 of the output gear pair 6 is output.
  • the output 82 of the overrunning clutch 8 is coupled to the input end 31 of the hydrodynamic clutch 3 and the output 42 of the one-way clutch 4, the input 41 of the one-way clutch 4 and the input gear pair 7
  • the output gear 72 is coupled, the input gear 71 of the input gear pair 7 is coupled to the coupling output gear 26, the output 32 of the hydrodynamic coupling 3 is coupled to the input gear 21, and the input gear 21 is passed through the planetary gear 20 on the input carrier 23.
  • the output gear 22 and the input carrier 23 cooperate with each other.
  • the output gear 22 is coupled to the input gear 91 of the coupling gear pair 9.
  • the output gear 92 of the coupling gear pair 9 is coupled to the input ring gear 25 and the input bull gear 27, and the input ring gear 25 is input.
  • the planetary gear 20 on the fixed carrier 24 cooperates with the fixed carrier 24 and the coupled output gear 26, the fixed carrier 24 is fixed to the fixed component, and the input large gear 27 passes through the planetary gear 20 and the output on the output carrier 28.
  • the planet carrier 28 and the input pinion 29 cooperate with each other, and the output carrier 28 is coupled to the output shaft 5.
  • the input gear 21 and the input carrier 23 converge the transmission power to the respective output gears 22 through the planetary gears 20 on the input carrier 23. Since the output gear 22 is coupled to the hydrodynamic coupling 3, the rotational speed of the output gear 22 can be It constantly changes with the change in the rotational speed of the hydrodynamic coupling 3, so that the rotational speed of the output gear 22 also changes.
  • the input power is split into two paths through the input shaft 1, one way is transmitted to the input planet carrier 23, and the other path is split into two paths through the overrunning clutch 8, one way is transmitted to the hydraulic profile coupling 3, and then transmitted to the input gear 21, the other way It is transmitted to the input pinion 29 through the output gear pair 6, the input gear 21, the input carrier 23, and the planetary gear 20 transmitted to the respective power passing through the input carrier 23 is merged with the output gear 22, and the output gear 22 is passed through the coupling gear pair.
  • the coupling output gear 26 is transmitted to the input gear 21 through the input gear pair 7, the one-way clutch 4, the overrunning clutch 8, and the hydrodynamic coupling 3, that is, the input power of the input gear 21 is increased accordingly.
  • the input gear 21 and the input carrier 23 merge the planetary gears 20 transmitted to the respective powers through the input carrier 23 to the output gear 22, and the output gear 22 repeats the above process to continuously transmit the rotational speed to the input large gear 27.
  • the input bull gear 27 and the input pinion 29 converge the planetary gears 20 that are transmitted to the respective power through the output carrier 28 to the output carrier 28, and the output carrier 28 is transmitted to the output shaft 5 of the present invention.
  • the power of the engine is externally output through the output shaft 5.
  • the rotational speed input to the large gear 27 changes with the input power or running resistance of the vehicle, and the lower the resistance, the higher the rotational speed transmitted to the input bull gear 27 High, and vice versa, the lower the cross-section, so that the composite hydrodynamic coupling of the present invention can change speed with different input power or 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 Diverted to Two ways, one way is transmitted to the input planet carrier 23, the other way is split into two paths through the overrunning clutch 8, one way is transmitted to the hydraulic profile coupling 3, and then to the input gear 21, and the other way is transmitted to the input through the output gear pair 6.
  • the pinion gear 29, the input gear 21, and the input carrier 23 converge the planetary gears 20 that are transmitted to the respective powers through the input carrier 23 to the output gear 22, and the output gears 22 are split into two paths by the coupling gear pair 9, one pass.
  • the input bull gear 27 and the input pinion 29 converge the planetary gear 20 transmitted to the respective power through the output carrier 28 to the output carrier 28, and the output carrier 28 is transmitted to the present invention.
  • the output shaft 5 is such that the power of the engine is externally output through the output shaft 5.
  • the vehicle starts to accelerate.
  • the resistance of the output shaft 5 decreases, the other is transmitted to the input.
  • the power of the ring gear 25 is increased accordingly, and the input ring gear 25 transmits power to the coupled output gear 26 through the planetary gears 20 on the fixed carrier 24, and the output gear 26 is coupled to the input gear pair 7 and the one-way clutch 4.
  • the overrunning clutch 8 and the hydraulically shaped coupling 3 are transmitted to the input gear 21, that is, the input power of the input gear 21 is increased, and the input gear 21 and the input carrier 23 transmit the respective powers to the input carrier 23.
  • the planetary gear 20 merges with the output gear 22, and the output gear 22 repeats the above process to continuously change the rotational speed transmitted to the input bull gear 27, and the input large gear 27 and the input pinion 29 transmit the respective power to the output carrier.
  • the planet gears 20 on 28 converge on the output planet carrier 28, and the output planet carrier 28 is transferred to the output shaft 5 of the present invention, and the torque transmitted to the output shaft 5 is transmitted through
  • the vehicle continues to accelerate, and the rotational speed of the output end 32 of the hydraulic profile coupling 3 is also gradually increased, and the rotational speed of the input gear 21 associated with it is also This is gradually increased, so that the rotational speeds on the output gear 22, the input bull gear 27, and the output shaft 5 are continuously increased.

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  • General Engineering & Computer Science (AREA)
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Abstract

一种复合式液力异型偶合器以及具有该复合式液力异型偶合器的起动器，其中输入轴（1）与第一单向离合器（10）、起动齿轮副（13）以及超越离合器（14）联接，超越离合器（14）与输入小齿轮（21）以及起动机齿轮副（3）联接，输出行星架（22）与联接架（5）以及输出齿轮副（11）联接，联接轴（8）与空挂档机构（7）、输出齿轮副（11）以及电磁离合器（12）联接，电磁离合器（12）与起动齿轮副（13）联接，空挂档机构（7）与输出轴（6）联接，联接架（5）与输入行星架（29）联接，输出联接齿轮（28）与输入齿圈（25）联接，输出齿轮（26）与第二单向离合器（9）联接，第一单向离合器（10）与第二单向离合器（9）以及液力异型偶合器（4）联接，液力异型偶合器（4）与输入大齿轮（23）联接。

Description

一种复合式液力异型偶合器以及起动器 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式液力异型偶合器以及起动器。
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，节能高效的复合式液力异型偶合器以及起动器。
为了实现本发明的目的，本发明采用的技术方案以下：
一种复合式液力异型偶合器以及起动器，包括输入轴(1)、起动机齿轮副(3)、液力异型偶合器(4)、联接架(5)、输出轴(6)、空挂档机构(7)、联接轴(8)、第二单向离合器(9)、第一单向离合器(10)、输出齿轮副(11)、电磁离合器(12)、起动齿轮副(13)、超越离合器(14)，所述的输入轴(1)与输出轴(6)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)、固定行星架(24)、输入齿圈(25)、输出齿轮(26)、固定齿圈(27)、输出联接齿轮(28)、输入行星架(29),输入轴(1)与第一单向离合器(10)的输入端(101)、起动齿轮副(13)的输出齿轮(132)以及超越离合器(14)的输入端(141)联接,超越离合器(14)的输出端(142)与输入小齿轮(21)以及起动机齿轮副(3)的输出齿轮(32)联接,起动机齿轮副(3)的输出齿轮(32)与起动机齿轮副(3)的输入齿轮(31)相互配合工作，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，输出行星架(22)与联接架(5)以及输出齿轮副(11)的输入齿轮(111)联接，联接轴(8)与空挂档机构(7)的输入端(71)、输出齿轮副(11)的输出齿轮(112)以及电磁离合器(12)的输入端(121)联接，电磁离合器(12)的输出齿轮(122)与起动齿轮副(13)的输入齿轮(131)联接，空挂档机构(7)的输出端(72)与输出轴(6)联接，联接架(5)与输入行星架(29)联接，输入行星架(29)通过其上的行星齿轮(20)与固定齿圈(27)、输出联接齿轮(28)相互配合工作，输出联接齿轮(28)与输入齿圈(25)联接，输入齿圈(25)通过固定行星架(24)上的行星齿轮(20)与固定行星架(24)、输出齿轮(26)相互配合工作，输出齿轮(26)与第二单向离合器(9)的输入端(91)联接，第一单向离合器(10)的输出端(102)与第二单向离合器(9)的输出端(92)以及液力异型偶合器(4)的输入端(41)联接，液力异型偶合器(4)的输出端(42)与输入大齿轮(23)联接，固定行星架(24)与固定齿圈(27)联接，固定齿圈(27)与固定元件联接。
一种复合式液力异型偶合器，包括输入轴(1)、液力异型偶合器(3)、单向离合器(4)、输出轴(5)、输出齿轮副(6)、输入齿轮副(7)、超越离合器(8)、联接齿轮副(9)，所述的输入轴(1)与输出轴(5)之间设有行星齿轮(20)、输入齿轮(21)、输出齿轮(22)、输入行 星架(23)、固定行星架(24)、输入齿圈(25)、联接输出齿轮(26)、输入大齿轮(27)、输出行星架(28)、输入小齿轮(29)，输入轴(1)与输入行星架(23)以及超越离合器(8)的输入端(81)联接,超越离合器(8)的输入端(81)与输出齿轮副(6)的输入齿轮(61)联接,输出齿轮副(6)的输出齿轮(62)与输入小齿轮(29)联接,超越离合器(8)的输出端(82)与液力异型偶合器(3)的输入端(31)以及单向离合器(4)的输出端(42)联接,单向离合器(4)的输入端(41)与输入齿轮副(7)的输出齿轮(72)联接,输入齿轮副(7)的输入齿轮(71)与联接输出齿轮(26)联接,液力异型偶合器(3)的输出端(32)与输入齿轮(21)联接,输入齿轮(21)通过输入行星架(23)上的行星齿轮(20)与输出齿轮(22)、输入行星架(23)相互配合工作，输出齿轮(22)与联接齿轮副(9)的输入齿轮(91)联接,联接齿轮副(9)的输出齿轮(92)与输入齿圈(25)以及输入大齿轮(27)联接,输入齿圈(25)通过固定行星架(24)上的行星齿轮(20)与固定行星架(24)、联接输出齿轮(26)相互配合工作，固定行星架(24)与固定元件固接,输入大齿轮(27)通过输出行星架(28)上的行星齿轮(20)与输出行星架(28)、输入小齿轮(29)相互配合工作，输出行星架(28)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。
所述液力异型偶合器可以选择多元件工作轮液力变矩器代替。
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式液力异型偶合器以及起动器。
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，一种复合式液力异型偶合器以及起动器，包括输入轴1、起动机齿轮副3、液力异型偶合器4、联接架5、输出轴6、空挂档机构7、联接轴8、第二单向离合器9、第一单向离合器10、输出齿轮副11、电磁离合器12、起动齿轮副13、超越离合器14，所述的输入轴1与输出轴6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、固定行星架24、输入齿圈25、输出齿轮26、固定齿圈27、输出联接齿轮28、输入行星架29,输入轴1与第一单向离合器10的输入端101、起动齿轮副13的输出齿轮132以及超越离合器14的输入端141联接,超越离合器14的输出端142与输入小齿轮21以及起动机齿轮副3的输出齿轮32联接,起动机齿轮副3的输出齿轮32与起动机齿轮副3的输入齿轮31相互配合工作，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，输出行星架22与联接架5以及输出齿轮副11的输入齿轮111联接，联接轴8与空挂档机构7的输入端71、输出齿轮副11的输出齿轮副112以及电磁离合器12的输入端121联接，电磁离合器12的输出齿轮122与起动齿轮副13的输入齿轮131联接，空挂档机构7的输出端72与输出轴6联接，联接架5与输入行星架29联接，输入行星架29通过其上的行星齿轮20与固定齿圈27、输出联接齿轮28相互配合工作，输出联接齿轮28与输入齿圈25联接，输入齿圈25通过固定行星架24上的行星齿轮20与固定行星架24、输出齿轮26相互配合工作，输出齿轮26与第二单向离合器9的输入端91联接，第一单向离合器10的输出端102与第二单向离合器9的输出端92以及液力异型偶合器4的输入端41联接，液力异型偶合器4的输出端42与输入大齿轮23联接，固定行星架24与固定齿圈27联接，固定齿圈27与固定元件联接。
发动机起动前，分离空挂档机构7，接合电磁离合器12，起动机的输入功率经过起动机齿轮副3传递到输入小齿轮21，输入小齿轮21通过输出行星架22上的行星齿轮20传递到输出行星架22，输出行星架22再通过输出齿轮副11、联接轴8、电磁离合器12以及起动齿轮副13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7，分离电磁离合器12，输入轴1把由发动机传递到此的功率分流为两路，一路通过第一单向离合器10以及液力异型偶合器4传递到输入大 齿轮23，另一路通过超越离合器14传递到输入小齿轮21，输入小齿轮21、输入大齿轮23把传递到各自的功率通过通过输出行星架22上的行星齿轮20传递到汇流于输出行星架22，输出行星架22再把传递到此的功率分流为两路，一路通过输出齿轮副11、联接轴8以及空挂档机构7传递到本发明的输出轴6；另一路通过联接架5传递到输入行星架29输入行星架29再通过其上的行星齿轮20传递到输出联接齿轮28，输出联接齿轮28再传递到输入齿圈25，输入齿圈25再通过固定行星架24上的行星齿轮20传递到输出齿轮26，输出齿轮26再通过第二单向离合器9、第一单向离合器10以及液力异型偶合器4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则在各个元件之间不断地进行变速的反复循环，其中，液力异型偶合器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，从而使输出行星架22的输出转速也不断地变化，并且通过输出齿轮副11、联接轴8以及空挂档机构7传递至本发明的输出轴6,从而实现了把发动机的功率通过输出轴6对外输出。
对于本发明，当输入轴1的转速不变，输入大齿轮23、输出行星架22以及输出轴6上的扭矩随其转速的变化而变化，转速越低，传递到输入大齿轮23、输出行星架22以及输出轴6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式液力异型偶合器以及起动器。
本发明使用时，发动机起动前，分离空挂档机构7，接合电磁离合器12，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3传递到输入小齿轮21,输入小齿轮21通过输出行星架22上的行星齿轮20把功率传递到输出行星架22，输出行星架22再通过输出齿轮副11、联接轴8、电磁离合器12以及起动齿轮副13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，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7，分离电磁离合器12，输入轴1把由发动机传递到此的功率分流为两路，一路通过第二单向离合器10以及液力异型偶合器4传递到联接输入大齿轮23，另一路通过超越离合器14传递到输入小齿轮21，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再把传递到此的功率分流为两路，一路通过输出齿轮副11、联接轴8以及空挂档机构7传递到本发明的输出轴6；另一路通过联接架5传递到输入行星架29，输入行星架29再通过其上的行星齿轮20传递到输出联接齿轮28，输出联接齿轮28再传递到输入齿圈25，输入齿圈25再通过固定行星架24上的行星齿轮20传递到输出齿轮26，输出齿轮26再通过第二单向离合器9、第一单向离合器10以及液力异型偶合器4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则在各个元件之间不断地进行变速的反复循环，其中，液力异型偶合器4的输出转速不断地随着行驶阻力的变化而无级地变速，从而使输出行星架22的输出转速也不断地变化，并且通过输出齿轮副11、联接轴8以及空挂档机构7传递至本发明的输出轴6,从而使输出轴6的扭矩随着转速的增加而减少。
实施例二：
如图2中所示，一种复合式液力异型偶合器，包括输入轴1、液力异型偶合器3、单向离合器4、输出轴5、输出齿轮副6、输入齿轮副7、超越离合器8、联接齿轮副9，所述的输入轴 1与输出轴5之间设有行星齿轮20、输入齿轮21、输出齿轮22、输入行星架23、固定行星架24、输入齿圈25、联接输出齿轮26、输入大齿轮27、输出行星架28、输入小齿轮29，输入轴1与输入行星架23以及超越离合器8的输入端81联接,超越离合器8的输入端81与输出齿轮副6的输入齿轮61联接,输出齿轮副6的输出齿轮62与输入小齿轮29联接,超越离合器8的输出端82与液力异型偶合器3的输入端31以及单向离合器4的输出端42联接,单向离合器4的输入端41与输入齿轮副7的输出齿轮72联接,输入齿轮副7的输入齿轮71与联接输出齿轮26联接,液力异型偶合器3的输出端32与输入齿轮21联接,输入齿轮21通过输入行星架23上的行星齿轮20与输出齿轮22、输入行星架23相互配合工作，输出齿轮22与联接齿轮副9的输入齿轮91联接,联接齿轮副9的输出齿轮92与输入齿圈25以及输入大齿轮27联接,输入齿圈25通过固定行星架24上的行星齿轮20与固定行星架24、联接输出齿轮26相互配合工作，固定行星架24与固定元件固接,输入大齿轮27通过输出行星架28上的行星齿轮20与输出行星架28、输入小齿轮29相互配合工作，输出行星架28与输出轴5联接。
输入齿轮21、输入行星架23把传递到各自的功率通过输入行星架23上的行星齿轮20汇流于输出齿轮22，由于输出齿轮22与液力异型偶合器3联接,所以输出齿轮22的转速可以不断地随着液力异型偶合器3转速的变化而变化,从而使输出齿轮22的转速也随之变化。
输入功率经过输入轴1分流为两路，一路传递到输入行星架23，另一路经过超越离合器8再分流为两路，一路传递到液力异型偶合器3，再传递到输入齿轮21，另一路通过输出齿轮副6传递到输入小齿轮29，输入齿轮21、输入行星架23把传递到各自的功率通过输入行星架23上的行星齿轮20汇流于输出齿轮22，输出齿轮22再通过联接齿轮副9分流为两路，一路传递到输入大齿轮27，此时，输入大齿轮27与输入小齿轮29把传递到各自的功率通过输出行星架28上的行星齿轮20汇流于输出行星架28，输出行星架28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，另一路传递到输入齿圈25的功率随之而增大，输入齿圈25则通过固定行星架24上的行星齿轮20把功率传递到联接输出齿轮26，联接输出齿轮26再通过输入齿轮副7、单向离合器4、超越离合器8以及液力异型偶合器3传递到输入齿轮21，即输入齿轮21输入的功率随之而增大，输入齿轮21、输入行星架23把传递到各自的功率通过输入行星架23上的行星齿轮20汇流于输出齿轮22，输出齿轮22再重复上述过程，使传递到输入大齿轮27上的转速不断变化，输入大齿轮27与输入小齿轮29把传递到各自的功率通过输出行星架28上的行星齿轮20汇流于输出行星架28，输出行星架28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，输入大齿轮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，传递到输入大齿轮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式液力异型偶合器。
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，一路传递到输入行星架23，另一路经过超越离合器8再分流为两路，一路传递到液力异型偶合器3，再传递到输入齿轮21，另一路通过输出齿轮副6传递到输入小齿轮29，输入齿轮21、输入行星架23把传递到各自的功率通过输入行星架23上的行星齿轮20汇流于输出齿轮22，输出齿轮22再通过联接齿轮副9分流为两路，一路传递到输入大齿轮27，此时，输入大齿轮27与输入小齿轮29把传递到各自的功率通过输出行星架28上的行星齿轮20汇流于输出行星架28，输出行星架28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，另一路传递到输入齿圈25的功率随之而增大，输入齿圈25则通过固定行星架24上的行星齿轮20把功率传递到联接输出齿轮26，联接输出齿轮26再通过输入齿轮副7、单向离合器4、超越离合器8以及液力异型偶合器3传递到输入齿轮21，即输入齿轮21输入的功率随之而增大，输入齿轮21、输入行星架23把传递到各自的功率通过输入行星架23上的行星齿轮20汇流于输出齿轮22，输出齿轮22再重复上述过程，使传递到输入大齿轮27上的转速不断变化，输入大齿轮27与输入小齿轮29把传递到各自的功率通过输出行星架28上的行星齿轮20汇流于输出行星架28，输出行星架28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，液力异型偶合器3的输出端32的转速也逐渐升高，与之相联的输入齿轮21的转速也随之逐渐升高，从而使输出齿轮22、输入大齿轮27以及输出轴5上的转速随之增加而不断地升高。

Claims (2)

  1. 一种复合式液力异型偶合器以及起动器，包括输入轴(1)、起动机齿轮副(3)、液力异型偶合器(4)、联接架(5)、输出轴(6)、空挂档机构(7)、联接轴(8)、第二单向离合器(9)、第一单向离合器(10)、输出齿轮副(11)、电磁离合器(12)、起动齿轮副(13)、超越离合器(14)，其特征在于：所述的输入轴(1)与输出轴(6)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)、固定行星架(24)、输入齿圈(25)、输出齿轮(26)、固定齿圈(27)、输出联接齿轮(28)、输入行星架(29),输入轴(1)与第一单向离合器(10)的输入端(101)、起动齿轮副(13)的输出齿轮(132)以及超越离合器(14)的输入端(141)联接,超越离合器(14)的输出端(142)与输入小齿轮(21)以及起动机齿轮副(3)的输出齿轮(32)联接,起动机齿轮副(3)的输出齿轮(32)与起动机齿轮副(3)的输入齿轮(31)相互配合工作，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，输出行星架(22)与联接架(5)以及输出齿轮副(11)的输入齿轮(111)联接，联接轴(8)与空挂档机构(7)的输入端(71)、输出齿轮副(11)的输出齿轮(112)以及电磁离合器(12)的输入端(121)联接，电磁离合器(12)的输出齿轮(122)与起动齿轮副(13)的输入齿轮(131)联接，空挂档机构(7)的输出端(72)与输出轴(6)联接，联接架(5)与输入行星架(29)联接，输入行星架(29)通过其上的行星齿轮(20)与固定齿圈(27)、输出联接齿轮(28)相互配合工作，输出联接齿轮(28)与输入齿圈(25)联接，输入齿圈(25)通过固定行星架(24)上的行星齿轮(20)与固定行星架(24)、输出齿轮(26)相互配合工作，输出齿轮(26)与第二单向离合器(9)的输入端(91)联接，第一单向离合器(10)的输出端(102)与第二单向离合器(9)的输出端(92)以及液力异型偶合器(4)的输入端(41)联接，液力异型偶合器(4)的输出端(42)与输入大齿轮(23)联接，固定行星架(24)与固定齿圈(27)联接，固定齿圈(27)与固定元件联接。
  2. 一种复合式液力异型偶合器，包括输入轴(1)、液力异型偶合器(3)、单向离合器(4)、输出轴(5)、输出齿轮副(6)、输入齿轮副(7)、超越离合器(8)、联接齿轮副(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)、输入齿轮(21)、输出齿轮(22)、输入行星架(23)、固定行星架(24)、输入齿圈(25)、联接输出齿轮(26)、输入大齿轮(27)、输出行星架(28)、输入小齿轮(29)，输入轴(1)与输入行星架(23)以及超越离合器(8)的输入端(81)联接,超越离合器(8)的输入端(81)与输出齿轮副(6)的输入齿轮(61)联接,输出齿轮副(6)的输出齿轮(62)与输入小齿轮(29)联接,超越离合器(8)的输出端(82)与液力异型偶合器(3)的输入端(31)以及单向离合器(4)的输出端(42)联接,单向离合器(4)的输入端(41)与输入齿轮副(7)的输出齿轮(72)联接,输入齿轮副(7)的输入齿轮(71)与联接输出齿轮(26)联接,液力异型偶合器(3)的输出端(32)与输入齿轮(21)联接,输入齿轮(21)通过输入行星架(23)上的行星齿轮(20)与输出齿轮(22)、输入行星架(23)相互配合工作，输出齿轮(22)与联接齿轮副(9)的输入齿轮(91)联接,联接齿轮副(9)的输出齿轮(92)与输入齿圈(25)以及输入大齿轮(27)联接,输入齿圈(25)通过固定行星架(24)上的行星齿轮(20)与固定行星架(24)、联接输出齿轮(26)相互配合工作，固定行星架(24)与固定元件固接,输入大齿轮(27)通过输出行星架(28)上的行星齿轮(20)与输出行星架(28)、输入小齿轮(29)相互配合工作，输出行星架(28)与输出轴(5)联接。
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