WO2017005183A1 - 一种复合型后辅室延长式限矩型液力偶合器以及起动器 - Google Patents

一种复合型后辅室延长式限矩型液力偶合器以及起动器 Download PDF

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Publication number
WO2017005183A1
WO2017005183A1 PCT/CN2016/088747 CN2016088747W WO2017005183A1 WO 2017005183 A1 WO2017005183 A1 WO 2017005183A1 CN 2016088747 W CN2016088747 W CN 2016088747W WO 2017005183 A1 WO2017005183 A1 WO 2017005183A1
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Prior art keywords
input
gear
output
ring gear
carrier
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PCT/CN2016/088747
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English (en)
French (fr)
Inventor
吴志强
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吴志强
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Application filed by 吴志强 filed Critical 吴志强
Priority to CN201680039171.2A priority Critical patent/CN108496028A/zh
Publication of WO2017005183A1 publication Critical patent/WO2017005183A1/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
    • 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
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type

Definitions

  • the invention belongs to the field of fluid coupling and starting, and more particularly to a composite rear auxiliary chamber extended torque type coupling and starting for various ground vehicles, ships, railway locomotives and machine tools. Device.
  • the fluid coupling is designed according to the principles of hydrostatics, etc. It can transmit little power and is not efficient; in addition, the cost is high.
  • the invention overcomes the deficiencies of the prior art, and provides a compound type rear auxiliary chamber extended torque type fluid coupling and a starter which are prolonged in service life, simple in structure, convenient in operation, low in cost, and energy-saving and high-efficiency.
  • Composite rear auxiliary chamber extended torque type fluid coupling and starter including input shaft (1), overrunning clutch (3), rear auxiliary chamber extended torque type fluid coupling (4), output Axle (5), empty gear mechanism (6), input gear pair (7), second one-way clutch (8), first one-way clutch (9), coupling shaft (10), output gear (11), a starter gear pair (12), an electromagnetic clutch (13), a start gear pair (14), a planetary gear (20) and an input carrier (21) are disposed between the input shaft (1) and the output shaft (5).
  • the input end (61) of the coupling shaft (10) and the neutral gear mechanism (6), the input gear (71) of the input gear pair (7), the output gear (11), and the input end of the electromagnetic clutch (13) (131)
  • the coupling gear (132) of the electromagnetic clutch (13) is coupled to the input gear (141) of the input gear pair (14), and the output end (62) of the idle gear mechanism (6) is coupled to the output shaft (5).
  • An output gear (72) of the input gear pair (7) is coupled to the input gear (29), and the input gear (29) passes through the planetary gear (20) on the fixed carrier (27) and the fixed carrier (27), the output gear ( 28)
  • the output gear (28) is coupled to the input end (81) of the second one-way clutch (8), the output end (92) of the first one-way clutch (9) and the second one-way clutch (8)
  • the output end (82) and the input end (41) of the rear auxiliary chamber extended torque type coupling (4) are coupled, and the output end of the rear auxiliary chamber extended torque type coupling (4) is 42) coupled with the coupling input planet carrier (24), the coupling input
  • the star frame (24) cooperates with the output small ring gear (25) and the fixed ring gear (26) through the planetary gear (20) thereon, and the output small ring gear (25) is coupled with the input planet carrier (21), and is fixed.
  • the ring gear (26) and the fixed planet carrier (27) are coupled to the stationary element.
  • a composite rear auxiliary chamber extended torque type fluid coupling comprising an input shaft (1), a rear auxiliary chamber extended torque type coupling (3), a one-way clutch (4), an output shaft ( 5), the overrunning clutch (6), the coupling frame (7), the input shaft (1) and the output shaft (5) are provided with a planetary gear (20), an input planet carrier (21), and a small input.
  • the input shaft (1) is coupled to the input small ring gear (22) and the input end (61) of the overrunning clutch (6), and the input end (61) of the overrunning clutch (6) is coupled to the input double planet carrier (27)
  • the input small ring gear (22) cooperates with the input carrier (21) and the output ring gear (23) through the planetary gear (20) on the input carrier (21), and the output ring gear (23) passes through the coupling frame ( 7) coupled to the input double-plane carrier (24), the input double-plane carrier (24) is coupled to the input pinion (29), and the planetary gear (20) and the output small ring gear through which the double-plane carrier (24) is input (25), the fixed ring gear (26) cooperates with each other, the fixed ring gear (26) is fixed with the fixing member, and the output small ring gear (24)
  • the output end (32) of the torque-limiting fluid coupling (3) and the input planet carrier (2 1) The input, the input double planet carrier (27) cooperates with the output large ring gear (28) and the input pinion (29) through the planetary gear (20) thereon, and outputs the large ring gear (28) and the output shaft. (5) Connection.
  • 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 rear auxiliary chamber extended torque type fluid coupling can be replaced by a vane adjustable hydraulic torque converter.
  • the air-locking mechanism can select a clutch instead.
  • the present invention When the present invention is applied to a vehicle, it is possible to automatically change the output torque and the speed change depending on the magnitude of the resistance that the vehicle is subjected to while traveling.
  • the invention enables the engine and the starter to operate in the region of the tempering speed, that is, the engine operates in a range of very small pollution discharge speeds, thereby avoiding the engine discharging a large amount of exhaust gas during idle speed and high speed operation, thereby reducing the number of exhaust gases.
  • the emission of exhaust gas is conducive to protecting the environment;
  • the invention can utilize the effect of internal speed difference to buffer and overload protection, which is beneficial to prolonging the service life of the engine and the drive train and the starter.
  • speed up which is beneficial to improve the driving performance of the vehicle;
  • the invention makes the input power uninterrupted, can ensure the vehicle has good acceleration and high average vehicle speed, reduces the wear of the engine, prolongs the overhaul interval mileage, and is beneficial to improving productivity;
  • the invention reduces the transmission mechanism of the current starter machine and reduces the manufacturing cost. After the engine is started, only the braking and separating measures of the starting motor are required to stop the transmission.
  • the present invention is a composite rear auxiliary system for various ground vehicles, ships, railway locomotives, and machine tools. Chamber extended torque type 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 rear auxiliary chamber extended torque type fluid coupling and a starter including an input shaft 1 , an overrunning clutch 3 , and a rear auxiliary chamber extended torque type fluid coupling 4 .
  • the input shaft 1 and the output shaft 5 are disposed with a planetary gear 20, an input carrier 21, an input ring gear 22, an output ring gear 23, a coupling input carrier 24, an output small ring gear 25, and a fixed ring gear. 26.
  • the fixed carrier 27, the output gear 28, the input gear 29, the input shaft 1 is coupled to the output gear 142 of the input gear pair 14, the input end 91 of the first one-way clutch 9, and the input end 31 of the overrunning clutch 3, the overrunning clutch
  • the output end 32 of the third gear is coupled to the input ring gear 22 and the output gear 122 of the starter gear pair 12, the output gear 122 of the starter gear pair 12 and the input gear 121 of the starter gear pair 12 cooperate with each other, and the input ring gear 22 passes.
  • the idle gear mechanism 6 is disengaged and the electromagnetic clutch 13 is engaged.
  • the input power of the starter is transmitted to the input ring gear 22 via the starter gear pair 12, and the input ring gear 22 is transmitted to the input gear carrier 22 through the planetary gear 20 on the input carrier 21.
  • the output ring gear 23 is output to the input shaft 1 through the output gear 11, the coupling shaft 10, the electromagnetic clutch 13 and the input gear pair 14, and is transmitted to the crankshaft of the engine, and the generated driving force is sufficient to overcome the engine starting resistance.
  • the engine starts.
  • the air-gear mechanism 6 is engaged, the electromagnetic clutch 13 is disengaged, and the input shaft 1 splits the power transmitted from the engine into two paths, all passing through the first one-way clutch 9 and the rear auxiliary chamber extended torque-limiting liquid.
  • the force coupling 4 is transmitted to the coupling input carrier 24, coupled to the input carrier 24 and transmitted to the output small ring gear 25 through the planetary gear 20 thereon, and then transmitted to the input carrier 21, and the other path is transmitted to the output through the overrunning clutch 3.
  • Ring gear 22, input planet carrier 21 is transmitted to the coupling input carrier 24, coupled to the input carrier 24 and transmitted to the output small ring gear 25 through the planetary gear 20 thereon, and then transmitted to the input carrier 21, and the other path is transmitted to the output through the overrunning clutch 3.
  • Ring gear 22, input planet carrier 21 is transmitted to the output through the overrunning clutch 3.
  • the input ring gear 22 merges the power transmitted to the respective power through the planetary gears 20 on the output coupling carrier 21 to the output ring gear 23, and the output ring gear 23 is transmitted to the coupling shaft 10 through the output gear 11, and the coupling shaft 10 transmits
  • the power split here is two ways, one is transmitted to the output shaft 5 of the present invention through the idle gear mechanism 6; the other is transmitted to the input gear 29 through the input gear pair 7, and the input gear 29 is passed through the planet on the fixed carrier 27.
  • the gear 20 is transmitted to the output gear 28, and the output gear 28 is transmitted to the coupled input carrier 24 through the second one-way clutch 8, the first one-way clutch 9, and the rear auxiliary chamber extended torque type coupling 4, and the input is coupled.
  • the planet carrier 24 is again transmitted through the planetary gears 20 thereon to the output small ring gear 25, and then to the input carrier 21, the input carrier 21, the input ring gear 22 is transmitted to the respective power through the output coupling planet carrier 21.
  • the planetary gear 20 merges with the output ring gear 23, and the output ring gear 23 continuously repeats the shifting of the speed between the respective components, wherein the output speed of the rear auxiliary chamber extended torque type fluid coupling 4 is continuously
  • the output power and the running resistance are changed steplessly, so that the output rotational speed of the output ring gear 23 is also constantly changed, and is transmitted to the output shaft of the present invention through the output gear 11, the coupling shaft 10, and the neutral gear mechanism 6. 5, thereby achieving external output of the engine power through the output shaft 5.
  • the torques on the input carrier 21, the output ring gear 23, and the output shaft 5 vary with the change of the rotational speed thereof, and the lower the rotational speed, the transmission to the input carrier 21 and the output teeth.
  • the torque on the ring 23 and the output shaft 5 is larger, and conversely, the smaller, so as to realize the composite rear auxiliary chamber extended torque type fluid coupling which can change the torque and speed according to the difference of the running resistance of the vehicle. And the starter.
  • 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 13 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 12, Wherein, since no power flows into the input carrier 21 at this time, and the power transmitted to the input ring gear 22 is transmitted to the output ring gear 23 through the planetary gear 20 input to the carrier 21, the output ring gear 23 passes through the output gear. 11.
  • the coupling shaft 10, the electromagnetic clutch 13 and the input gear pair 14 are transmitted to the input shaft 1 and then transmitted to the crankshaft of the engine, and the generated starting power is sufficient to overcome the engine starting resistance and the engine is started.
  • the 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 13 is separated, and the input shaft 1 is The power split to the engine is divided into two paths, one pass through the first one-way clutch 9 and the rear auxiliary chamber extended torque type fluid coupling 4 to the coupled input planet carrier 24, coupled to the input planet carrier 24 and passed through
  • the planetary gear 20 is transmitted to the output small ring gear 25 and then to the input carrier 21, the other is transmitted to the output ring gear 22 through the overrunning clutch 3, and the input carrier 21, the input ring gear 22 is transmitted to the respective power through the output.
  • the planetary gears 20 connected to the carrier 21 converge on the output ring gear 23, and the output ring gear 23 is transmitted to the coupling shaft 10 through the output gear 11, and the coupling shaft 10 diverts the power transmitted thereto into two paths, all of which pass through the idle gear.
  • the mechanism 6 is transmitted to the output shaft 5 of the present invention; the other path is transmitted to the input gear 29 through the input gear pair 7, and the input gear 29 is transmitted to the output gear through the planetary gear 20 on the fixed carrier 27. 28, the output gear 28 is transmitted to the coupling input carrier 24 through the second one-way clutch 8, the first one-way clutch 9, and the rear auxiliary chamber extended torque type coupling 4, and the input carrier 22 is coupled thereto.
  • the upper planetary gear 20 is transmitted to the output small ring gear 25, and then transmitted to the input carrier 21, and the input carrier 21 and the input ring gear 22 converge the output to the respective power through the planetary gear 20 of the output coupling carrier 21.
  • the ring gear 23 and the output ring gear 23 continuously perform repeated cycles of shifting between the respective components, wherein the output rotational speed of the rear auxiliary chamber extended torque type fluid coupling 4 continuously changes with the running resistance.
  • the ground speed is shifted so that the output rotational speed of the output ring gear 23 is also constantly changed, and is transmitted to the output shaft 5 of the present invention through the output gear 11, the coupling shaft 10, and the neutral gear mechanism 6, so that the torque of the output shaft 5 is varied. As the speed increases, it decreases.
  • Embodiment 2 is a diagrammatic representation of Embodiment 1:
  • a composite rear auxiliary chamber extended torque type coupling including an input shaft 1, a rear auxiliary chamber extended torque type fluid coupling 3, a one-way clutch 4, an output shaft 5.
  • the overrunning clutch 6 and the coupling frame 7 are disposed between the input shaft 1 and the output shaft 5, and are provided with a planetary gear 20, an input carrier 21, an input small ring gear 22, an output ring gear 23, and an input double star carrier.
  • the output small ring gear 25, the fixed ring gear 26, the input double planet carrier 27, the output large ring gear 28, the input pinion 29, the input shaft 1 is coupled with the input small ring gear 22 and the input end 61 of the overrunning clutch 6,
  • the input end 61 of the overrunning clutch 6 is coupled to the input double planet carrier 27, and the input small ring gear 22 cooperates with the input carrier 21 and the output ring gear 23 through the planetary gear 20 on the input carrier 21, and the output ring gear 23 passes.
  • the coupling frame 7 is coupled to the input double star carrier 24, the input double star carrier 24 is coupled to the input pinion 29, and the input double planet carrier 24 cooperates with the output small ring gear 25 and the fixed ring gear 26 through the planetary gear 20 thereon.
  • the fixed ring gear 26 is fixed with the fixing member, and the output small ring gear 25 and the single Connected to the input end 41 of the clutch 4, the output end 62 of the overrunning clutch 6 is coupled to the output end 42 of the one-way clutch 4 and the input end 31 of the rear auxiliary chamber extended torque type coupling 3, the rear auxiliary chamber extension
  • the output end 32 of the torque-type fluid coupling 3 is coupled to the input carrier 21, and the input double-carrier carrier 27 cooperates with the output large ring gear 28 and the input pinion 29 through the planetary gear 20 thereon, and outputs a large tooth.
  • the ring 28 is coupled to the output shaft 5.
  • the input carrier 21 and the input small ring gear 22 converge the planetary gears 20 transmitted to the respective powers through the input carrier 21 to the output ring gear 23, because the input carrier 21 and the rear auxiliary chamber extend the torque-type fluid coupling
  • the device 3 is coupled so that the rotational speed of the input carrier 21 can be constantly changed, so that the rotational speed of the output ring gear 23 also changes.
  • the input power is divided into two paths through the input shaft 1, one is transmitted to the input small ring gear 22, the other is transmitted to the overrunning clutch 6, and the overrunning clutch 6 is divided into two paths, one way is transmitted to the input double planet carrier 27, and the other is transmitted to the input double planet carrier 27,
  • the output ring gear 23 is transmitted to the input double-plane carrier 24 through the coupling frame 7, and the input double-plane carrier 24 is divided into two paths, one way is transmitted to the input pinion 29, and at this time, the double-frame carrier is input.
  • the ring gear 22 merges the power transmitted to the respective planets 20 through the input carrier 21 to the output ring gear 23, and the output ring gear 23 repeats the above process, so that the rotational speed transmitted to the input pinion 29 is constantly changed, and the input double The carrier 27 and the input pinion 29 converge the planetary gears 20 transmitted to the respective power through the input double planet carrier 27 to the output large ring gear 28, and the output large ring gear 28 is transmitted to the output shaft 5 of the present invention. Thereby, the power of the engine is externally outputted through the output shaft 5.
  • the rotational speed of the input shaft 1 when the rotational speed of the input shaft 1 is constant, the rotational speed of the input pinion 29 varies with the input power or running resistance of the vehicle, and the lower the resistance, the higher the rotational speed transmitted to the input pinion 29 The higher, and conversely, the lower, thereby realizing the composite rear auxiliary chamber extended torque type 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 Diverted to Two ways, one way is transmitted to the input small ring gear 22, the other way is transmitted to the overrunning clutch 6, the overrunning clutch 6 is divided into two paths, one way is transmitted to the input double planet carrier 27, and the other way is passed through the rear auxiliary room extended type limit type The fluid coupling 3 is transmitted to the input carrier 21, the input carrier 21, the input small ring gear 22, and the planetary gears 20 transmitted to the respective powers passing through the input carrier 21 are merged to the output ring gear 23, and the output ring gear 23 is output.
  • the input double-plane carrier 24 is transmitted to the coupling frame 7, and the input double-plane carrier 24 is divided into two paths, and is transmitted to the input pinion 29 at one time.
  • the input double-carrier carrier 27 and the input pinion 29 are transmitted to the respective
  • the power is transmitted to the output large ring gear 28 through the planetary gears 20 on the input double planet carrier 2, and the output large ring gear 28 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 ring gear 23, the output ring gear 23 repeats the above process, so that the rotational speed transmitted to the input pinion 29 is constantly changed, and the input double carrier 27 and the input pinion 29 are transmitted to the respective powers through the input double planet carrier.
  • the planetary gears 20 on the 27 merge with the output large ring gear 28, and the output large ring gears 28 are transmitted to the output shaft 5 of the present invention, and the torque transmitted to the output shaft 5 is transmitted to the drive wheels through the transmission system.
  • the gravitation is enough to further overcome the starting resistance of the car, the car starts and starts to accelerate, and the rotational speed of the output end 32 of the rear auxiliary chamber extended torque type coupling 3 is also gradually increased, and the input planet carrier 21 is associated with it.
  • the rotational speed also gradually increases, so that the rotational speeds on the output ring gear 23, the input pinion 29, and the output shaft 5 increase accordingly.

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Abstract

一种复合型后辅室延长式限矩型液力偶合器及具有该复合型后辅室延长式限矩型液力偶合器的起动器，其中输入轴（1）与输入齿轮副（14）、第一单向离合器（9）以及超越离合器（3）联接，超越离合器（3）与输入齿圈（22）以及起动机齿轮副（12）联接，输出齿圈（23）与输出齿轮（11）啮合，联接轴（10）与空挂档机构（6）、输入齿轮副（7）、输出齿轮（11）以及电磁离合器（13）联接，电磁离合器（13）与输入齿轮副（14）联接，空挂档机构（6）与输出轴（5）联接，输入齿轮副（7）与输入齿轮（29）联接，输出齿轮（28）与第二单向离合器（8）联接，第一单向离合器（9）与第二单向离合器（8）以及后辅室延长式限矩型液力偶合器（4）联接，后辅室延长式限矩型液力偶合器（4）与联接输入行星架（21）联接，输出小齿圈（25）与输入行星架（21）联接。

Description

一种复合型后辅室延长式限矩型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后辅室延长式限矩型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，节能高效的复合型后辅室延长式限矩型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：
一种复合型后辅室延长式限矩型液力偶合器以及起动器，包括输入轴(1)、超越离合器(3)、后辅室延长式限矩型液力偶合器(4)、输出轴(5)、空挂档机构(6)、输入齿轮副(7)、第二单向离合器(8)、第一单向离合器(9)、联接轴(10)、输出齿轮(11)、起动机齿轮副(12)、电磁离合器(13)、起动齿轮副(14)，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)、输入齿圈(22)、输出齿圈(23)、联接输入行星架(24)、输出小齿圈(25)、固定齿圈(26)、固定行星架(27)、输出齿轮(28)、输入齿轮(29),输入轴(1)与输入齿轮副(14)的输出齿轮(142)、第一单向离合器(9)的输入端(91)以及超越离合器(3)的输入端(31)联接,超越离合器(3)的输出端(32)与输入齿圈(22)以及起动机齿轮副(12)的输出齿轮(122)联接,起动机齿轮副(12)的输出齿轮(122)与起动机齿轮副(12)的输入齿轮(121)相互配合工作，输入齿圈(22)通过输入行星架(21)上的行星齿轮(20)与输入行星架(21)、输出齿圈(23)相互配合工作，输出齿圈(23)与输出齿轮(11)啮合，联接轴(10)与空挂档机构(6)的输入端(61)、输入齿轮副(7)的输入齿轮(71)、输出齿轮(11)以及电磁离合器(13)的输入端(131)联接，电磁离合器(13)的输出齿轮(132)与输入齿轮副(14)的输入齿轮(141)联接，空挂档机构(6)的输出端(62)与输出轴(5)联接，输入齿轮副(7)的输出齿轮(72)与输入齿轮(29)联接，输入齿轮(29)通过固定行星架(27)上的行星齿轮(20)与固定行星架(27)、输出齿轮(28)相互配合工作，输出齿轮(28)与第二单向离合器(8)的输入端(81)联接，第一单向离合器(9)的输出端(92)与第二单向离合器(8)的输出端(82)以及后辅室延长式限矩型液力偶合器(4)的输入端(41)联接，后辅室延长式限矩型液力偶合器(4)的输出端(42)与联接输入行星架(24)联接，联接输入行星架(24)通过其上的行星齿轮(20)与输出小齿圈(25)、固定齿圈(26)相互配合工作，输出小齿圈(25)与输入行星架(21)联接，固定齿圈(26)以及固定行星架(27)与固定元件联接。
一种复合型后辅室延长式限矩型液力偶合器，包括输入轴(1)、后辅室延长式限矩型液力偶合器(3)、单向离合器(4)、输出轴(5)、超越离合器(6)、联接架(7)，所述的输入轴(1)与输出轴(5)之间设有设有行星齿轮(20)、输入行星架(21)、输入小齿圈(22)、输出齿 圈(23)、输入双星行星架(24)、输出小齿圈(25)、固定齿圈(26)、输入双联行星架(27)、输出大齿圈(28)、输入小齿轮(29)，输入轴(1)与输入小齿圈(22)以及超越离合器(6)的输入端(61)联接,超越离合器(6)的输入端(61)与输入双联行星架(27)联接,输入小齿圈(22)通过输入行星架(21)上的行星齿轮(20)与输入行星架(21)、输出齿圈(23)相互配合工作，输出齿圈(23)通过联接架(7)与输入双星行星架(24)联接,输入双星行星架(24)与输入小齿轮(29)联接,并且输入双星行星架(24)通过其上的行星齿轮(20)与输出小齿圈(25)、固定齿圈(26)相互配合工作，固定齿圈(26)与固定件固接,输出小齿圈(25)与单向离合器(4)的输入端(41)联接,超越离合器(6)的输出端(62)与单向离合器(4)的输出端(42)以及后辅室延长式限矩型液力偶合器(3)的输入端(31)联接,后辅室延长式限矩型液力偶合器(3)的输出端(32)与输入行星架(21)联接,输入双联行星架(27)通过其上的行星齿轮(20)与输出大齿圈(28)、输入小齿轮(29)相互配合工作，输出大齿圈(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。
所述后辅室延长式限矩型液力偶合器可以选择导叶可调式液力变矩器代替。
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后辅 室延长式限矩型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，一种复合型后辅室延长式限矩型液力偶合器以及起动器，包括输入轴1、超越离合器3、后辅室延长式限矩型液力偶合器4、输出轴5、空挂档机构6、输入齿轮副7、第二单向离合器8、第一单向离合器9、联接轴10、输出齿轮11、起动机齿轮副12、电磁离合器13、起动齿轮副14，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、输入齿圈22、输出齿圈23、联接输入行星架24、输出小齿圈25、固定齿圈26、固定行星架27、输出齿轮28、输入齿轮29,输入轴1与输入齿轮副14的输出齿轮142、第一单向离合器9的输入端91以及超越离合器3的输入端31联接,超越离合器3的输出端32与输入齿圈22以及起动机齿轮副12的输出齿轮122联接,起动机齿轮副12的输出齿轮122与起动机齿轮副12的输入齿轮121相互配合工作，输入齿圈22通过输入行星架21上的行星齿轮20与输入行星架21、输出齿圈23相互配合工作，输出齿圈23与输出齿轮11啮合，联接轴10与空挂档机构6的输入端61、输入齿轮副7的输入齿轮71、输出齿轮11以及电磁离合器13的输入端131联接，电磁离合器13的输出齿轮132与输入齿轮副14的输入齿轮141联接，空挂档机构6的输出端62与输出轴5联接，输入齿轮副7的输出齿轮72与输入齿轮29联接，输入齿轮29通过固定行星架27上的行星齿轮20与固定行星架27、输出齿轮28相互配合工作，输出齿轮28与第二单向离合器8的输入端81联接，第一单向离合器9的输出端92与第二单向离合器8的输出端82以及后辅室延长式限矩型液力偶合器4的输入端41联接，后辅室延长式限矩型液力偶合器4的输出端42与联接输入行星架24联接，联接输入行星架24通过其上的行星齿轮20与输出小齿圈25、固定齿圈26相互配合工作，输出小齿圈25与输入行星架21联接，固定齿圈26以及固定行星架27与固定元件联接。
发动机起动前，分离空挂档机构6，接合电磁离合器13，起动机的输入功率经过起动机齿轮副12传递到输入齿圈22，输入齿圈22通过输入行星架21上的行星齿轮20传递到输出齿圈23，输出齿圈23再通过输出齿轮11、联接轴10、电磁离合器13以及输入齿轮副14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13，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9以及后辅室延长式限矩型液力偶合器4传递到联接输入行星架24，联接输入行星架24再通过其上的行星齿轮20传递到输出小齿圈25，再传递到输入行星架21，另一路通过超越离合器3传递到输出齿圈22，输入行星架 21、输入齿圈22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汇流于输出齿圈23，输出齿圈23再通过输出齿轮11传递到联接轴10，联接轴10把传递到此的功率分流为两路，一路通过空挂档机构6传递到本发明的输出轴5；另一路通过输入齿轮副7传递到输入齿轮29，输入齿轮29再通过固定行星架27上的行星齿轮20传递到输出齿轮28，输出齿轮28再通过第二单向离合器8、第一单向离合器9以及后辅室延长式限矩型液力偶合器4传递到联接输入行星架24，联接输入行星架24再通过其上的行星齿轮20传递到输出小齿圈25，再传递到输入行星架21，输入行星架21、输入齿圈22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汇流于输出齿圈23，输出齿圈23则在各个元件之间不断地进行变速的反复循环，其中，后辅室延长式限矩型液力偶合器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，从而使输出齿圈23的输出转速也不断地变化，并且通过输出齿轮11、联接轴10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、输出齿圈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、输出齿圈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后辅室延长式限矩型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13，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12传递到输入齿圈22,其中，由于此时没有功率流入输入行星架21，传递到输入齿圈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圈23，输出齿圈23再通过输出齿轮11、联接轴10、电磁离合器13以及输入齿轮副14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6，分离电磁离合器13，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9以及后辅室延长式限矩型液力偶合器4传递到联接输入行星架24，联接输入行星架24再通过其上的行星齿轮20传递到输出小齿圈25，再传递到输入行星架21，另一路通过超越离合器3传递到输出齿圈22，输入行星架21、输入齿圈22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汇流于输出齿圈23，输出齿圈23再通过输出齿轮11传递到联接轴10，联接轴10把传递到此的功率分流为两路，一路通过空挂档机构6传递到本发明的输出轴5；另一路通过输入齿轮副7传递到输入齿轮29，输入齿轮29再通过固定行星架27上的行星齿轮20传递到输出齿轮28，输出齿轮28再通过第二单向离合器8、第一单向离合器9以及后辅室延长式限矩型液力偶合器4传递到联接输入行星架24，联接输入行星架24再通过其上的行星齿轮20传递到输出小齿圈25，再传递到输入行星架21，输入行星架21、输入齿圈22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汇流于输出齿圈23，输出齿圈23则在各个元件之间不断地进行变速的反复循环，其中，后辅室延长式限矩型液力偶合器4的输出转速不断地随着行驶阻力的变化而无级地变速，从而使输出齿圈23的输出转速也不断地变化，并且通过输出齿轮11、联接轴10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，一种复合型后辅室延长式限矩型液力偶合器，包括输入轴1、后辅室延长式限矩型液力偶合器3、单向离合器4、输出轴5、超越离合器6、联接架7，所述的输入轴1与输出轴5之间设有设有行星齿轮20、输入行星架21、输入小齿圈22、输出齿圈23、输入双星行星架24、输出小齿圈25、固定齿圈26、输入双联行星架27、输出大齿圈28、输入小齿轮29，输入轴1与输入小齿圈22以及超越离合器6的输入端61联接,超越离合器6的输入端61与输入双联行星架27联接,输入小齿圈22通过输入行星架21上的行星齿轮20与输入行星架21、输出齿圈23相互配合工作，输出齿圈23通过联接架7与输入双星行星架24联接,输入双星行星架24与输入小齿轮29联接,并且输入双星行星架24通过其上的行星齿轮20与输出小齿圈25、固定齿圈26相互配合工作，固定齿圈26与固定件固接,输出小齿圈25与单向离合器4的输入端41联接,超越离合器6的输出端62与单向离合器4的输出端42以及后辅室延长式限矩型液力偶合器3的输入端31联接,后辅室延长式限矩型液力偶合器3的输出端32与输入行星架21联接,输入双联行星架27通过其上的行星齿轮20与输出大齿圈28、输入小齿轮29相互配合工作，输出大齿圈28与输出轴5联接。
输入行星架21、输入小齿圈22把传递到各自的功率通过输入行星架21上的行星齿轮20汇流于输出齿圈23，由于输入行星架21与后辅室延长式限矩型液力偶合器3联接,所以输入行星架21的转速可以不断地改变,从而使输出齿圈23的转速也随之变化。
输入功率经过输入轴1把功率分流为两路，一路传递到输入小齿圈22，另一路传递到超越离合器6，超越离合器6再分流为两路，一路传递到输入双联行星架27，另一路经过后辅室延长式限矩型液力偶合器3，传递到输入行星架21，输入行星架21、输入小齿圈22把传递到各自的功率通过输入行星架21上的行星齿轮20汇流于输出齿圈23，输出齿圈23再通过联接架7传递到输入双星行星架24，输入双星行星架24再分流为两路，一路传递到输入小齿轮29，此时，输入双联行星架27与输入小齿轮29把传递到各自的功率通过输入双联行星架2上的行星齿轮20汇流于输出大齿圈28，输出大齿圈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，另一路则通过其上的行星齿轮20把功率传递到输出小齿圈25的功率随之而增大，输出小齿圈25再通过单向离合器4、超越离合器6以及后辅室延长式限矩型液力偶合器3传递到输入行星架21，即输入行星架21的输入功率随之而增大，输入行星架21、输入小齿圈22把传递到各自的功率通过输入行星架21上的行星齿轮20汇流于输出齿圈23，输出齿圈23再重复上述过程，使传递到输入小齿轮29上的转速不断变化，输入双联行星架27与输入小齿轮29把传递到各自的功率通过输入双联行星架27上的行星齿轮20汇流于输出大齿圈28，输出大齿圈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，输入小齿轮29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，传递到输入小齿轮29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后辅室延长式限矩型液力偶合器。
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圈22，另一路传递到超越离合器6，超越离合器6再分流为两路，一路传递到输入双联行星架27，另一路经过后辅室延长式限矩型液力偶合器3，传递到输入行星架21，输入行星架21、输入小齿圈22把传递到各自的功率通过输入行星架21上的行星齿轮20汇流于输出齿圈23，输出齿圈23再通过联接架7传递到输入双星行星架24，输入双星行星架24再分流为两路，一路传递到输入小齿轮29，此时，输入双联行星架27与输入小齿轮29把传递到各自的功率通过输入双联行星架2上的行星齿轮20汇流于输出大齿圈28，输出大齿圈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，另一路则通过其上的行星齿轮20把功率传递到输出小齿圈25的功率随之而增大，输出小齿圈25再通过单向离合器4、超越离合器6以及后辅室延长式限矩型液力偶合器3传递到输入行星架21，即输入行星架21的输入功率随之而增大，输入行星架21、输入小齿圈22把传递到各自的功率通过输入行星架21上的行星齿轮20汇流于输出齿圈23，输出齿圈23再重复上述过程，使传递到输入小齿轮29上的转速不断变化，输入双联行星架27与输入小齿轮29把传递到各自的功率通过输入双联行星架27上的行星齿轮20汇流于输出大齿圈28，输出大齿圈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起步阻力时,汽车则起步并开始加速，后辅室延长式限矩型液力偶合器3的输出端32的转速也逐渐升高，与之相联的输入行星架21的转速也随之逐渐升高，从而使输出齿圈23、输入小齿轮29以及输出轴5上的转速随之增加而升高。

Claims (2)

  1. 一种复合型后辅室延长式限矩型液力偶合器以及起动器，包括输入轴(1)、超越离合器(3)、后辅室延长式限矩型液力偶合器(4)、输出轴(5)、空挂档机构(6)、输入齿轮副(7)、第二单向离合器(8)、第一单向离合器(9)、联接轴(10)、输出齿轮(11)、起动机齿轮副(12)、电磁离合器(13)、起动齿轮副(14)，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)、输入齿圈(22)、输出齿圈(23)、联接输入行星架(24)、输出小齿圈(25)、固定齿圈(26)、固定行星架(27)、输出齿轮(28)、输入齿轮(29),输入轴(1)与输入齿轮副(14)的输出齿轮(142)、第一单向离合器(9)的输入端(91)以及超越离合器(3)的输入端(31)联接,超越离合器(3)的输出端(32)与输入齿圈(22)以及起动机齿轮副(12)的输出齿轮(122)联接,起动机齿轮副(12)的输出齿轮(122)与起动机齿轮副(12)的输入齿轮(121)相互配合工作，输入齿圈(22)通过输入行星架(21)上的行星齿轮(20)与输入行星架(21)、输出齿圈(23)相互配合工作，输出齿圈(23)与输出齿轮(11)啮合，联接轴(10)与空挂档机构(6)的输入端(61)、输入齿轮副(7)的输入齿轮(71)、输出齿轮(11)以及电磁离合器(13)的输入端(131)联接，电磁离合器(13)的输出齿轮(132)与输入齿轮副(14)的输入齿轮(141)联接，空挂档机构(6)的输出端(62)与输出轴(5)联接，输入齿轮副(7)的输出齿轮(72)与输入齿轮(29)联接，输入齿轮(29)通过固定行星架(27)上的行星齿轮(20)与固定行星架(27)、输出齿轮(28)相互配合工作，输出齿轮(28)与第二单向离合器(8)的输入端(81)联接，第一单向离合器(9)的输出端(92)与第二单向离合器(8)的输出端(82)以及后辅室延长式限矩型液力偶合器(4)的输入端(41)联接，后辅室延长式限矩型液力偶合器(4)的输出端(42)与联接输入行星架(24)联接，联接输入行星架(24)通过其上的行星齿轮(20)与输出小齿圈(25)、固定齿圈(26)相互配合工作，输出小齿圈(25)与输入行星架(21)联接，固定齿圈(26)以及固定行星架(27)与固定元件联接。
  2. 一种复合型后辅室延长式限矩型液力偶合器，包括输入轴(1)、后辅室延长式限矩型液力偶合器(3)、单向离合器(4)、输出轴(5)、超越离合器(6)、联接架(7)，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)、输入小齿圈(22)、输出齿圈(23)、输入双星行星架(24)、输出小齿圈(25)、固定齿圈(26)、输入双联行星架(27)、输出大齿圈(28)、输入小齿轮(29)，输入轴(1)与输入小齿圈(22)以及超越离合器(6)的输入端(61)联接,超越离合器(6)的输入端(61)与输入双联行星架(27)联接,输入小齿圈(22)通过输入行星架(21)上的行星齿轮(20)与输入行星架(21)、输出齿圈(23)相互配合工作，输出齿圈(23)通过联接架(7)与输入双星行星架(24)联接,输入双星行星架(24)与输入小齿轮(29)联接,并且输入双星行星架(24)通过其上的行星齿轮(20)与输出小齿圈(25)、固定齿圈(26)相互配合工作，固定齿圈(26)与固定件固接,输出小齿圈(25)与单向离合器(4)的输入端(41)联接,超越离合器(6)的输出端(62)与单向离合器(4)的输出端(42)以及后辅室延长式限矩型液力偶合器(3)的输入端(31)联接,后辅室延长式限矩型液力偶合器(3)的输出端(32)与输入行星架(21)联接,输入双联行星架(27)通过其上的行星齿轮(20)与输出大齿圈(28)、输入小齿轮(29)相互配合工作，输出大齿圈(28)与输出轴(5)联接。
PCT/CN2016/088747 2015-07-07 2016-07-06 一种复合型后辅室延长式限矩型液力偶合器以及起动器 WO2017005183A1 (zh)

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