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WO2016112805A1 - 一种复合型双涡轮液力变矩器以及无级变速器 - Google Patents

一种复合型双涡轮液力变矩器以及无级变速器 Download PDF

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Publication number
WO2016112805A1
WO2016112805A1 PCT/CN2016/070214 CN2016070214W WO2016112805A1 WO 2016112805 A1 WO2016112805 A1 WO 2016112805A1 CN 2016070214 W CN2016070214 W CN 2016070214W WO 2016112805 A1 WO2016112805 A1 WO 2016112805A1
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input
gear
output
carrier
coupled
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English (en)
French (fr)
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吴志强
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Priority to CN201680004316.5A priority Critical patent/CN107407390A/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
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing

Definitions

  • the present invention is in the field of torque converters and shifting, and more particularly, it is a composite twin-turbo torque converter and a continuously variable transmission for various ground vehicles, ships, railway locomotives, and machine tools.
  • the torque converter 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 twin-turbo torque converter and a continuously variable transmission which have the advantages of shortening the service life of the engine, simple structure, convenient operation, low cost, energy saving and high efficiency.
  • a compound twin-turbo torque converter comprising an input shaft (1), an output shaft (3), a coupling gear pair (4), an input gear pair (5), an overrunning clutch (6), and a twin-turbo hydraulic force change a torque device (7) and an output gear pair (8), wherein the input shaft (1) and the output shaft (3) are provided with a planetary gear (20), an input gear (21), an output carrier (22), Fixed gear (23), input small ring gear (24), connecting planet carrier (25), input large ring gear (26), input ring gear (27), output ring gear (28), input planet carrier (29),
  • the input gear (21) cooperates with the output carrier (22) and the fixed gear (23) through the planetary gears (20) on the output carrier (22), and fixes the input of the gear (23) and the overrunning clutch (6) ( 61) coupled with the fixed component
  • the output carrier (22) is coupled with the input large ring gear (26), and the input large ring gear (26) passes the planetary gear (20) and the input small ring gear (24
  • the output gear (42) of the coupling gear pair (4) is coupled to the input carrier (29), input The star frame (29) cooperates with the input ring gear (27) and the output ring gear (28) through the planetary gears (20) thereon, and the output ring gear (28) is coupled with the output shaft (3), and the input ring gear (27)
  • the input gear (51) of the input gear pair (5) and the output end (62) of the overrunning clutch (6) are coupled to the output end (72) of the twin-turbine torque converter (7), and the twin-turbo hydraulic force is changed.
  • the input end (71) of the torque device (7) is coupled to the output gear (82) of the output gear pair (8), the input gear (81) of the output gear pair (8), and the input gear (21) and the input shaft (1) Join.
  • a continuously variable transmission of a composite twin-turbo torque converter comprising an input shaft (1), an output shaft (3), a twin-turbo torque converter (4), an input gear pair (5), an overrunning clutch ( 6), a coupling gear pair (7), an input gear (8), an output gear pair (9), a planetary gear (20), a fixed planet carrier between the input shaft (1) and the output shaft (3) (21), input ring gear (22), output ring gear (23), connecting planet carrier (24), input gear (25), output large ring gear (26), input large gear (27), output planet carrier ( 28) Input the input large ring gear (29), output gear (30), input carrier (31), input pinion (32), input ring gear (22), twin-turbo torque converter (4)
  • the input gear (91) of the end (41) and the output gear pair (9) is coupled to the input shaft (1), and the input ring gear (22) is fixed to the fixed planet carrier by the planetary gear (20) on the fixed carrier (21) ( 21), the output ring gear (23) works together,
  • the output end (62) of the overrunning clutch (6) and the output gear (72) of the coupling gear pair (7) are coupled with the output gear (52) of the input gear pair (5), and coupled to the gear pair (7)
  • the input gear (71) is coupled to the coupling carrier (24)
  • the input gear (51) of the input gear pair (5) is coupled to the output (42) of the twin-turbine torque converter (4)
  • the output gear (30) Coupling with the input large ring gear (29), the input large ring gear (29) cooperates with the input large gear (27) and the output planet carrier (28) through the planetary gear (20) on the output carrier (28), and the input is large.
  • the gear (27) is coupled to the output gear (92) of the output gear pair (9), and the output carrier (28) is coupled to the output shaft (3).
  • the components that need to be coupled may be directly connected.
  • the method of coupling a shaft, a hollow or a coupling frame may be adopted, and may be connected through or across several other components; when the coupled component is When the gears or ring gears are engaged or coupled with each other, the components that do not need to be coupled can be rotated relative to each other.
  • the gear ratios of the gear pairs and the shifting mechanism are designed according to actual needs.
  • the torque converter can be selected from a fluid coupling, a pressure motor and a hydraulic pump, and an electromagnetic clutch.
  • 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 makes the engine and the starter operate in the economic speed region, that is, the engine works in the range of the very small pollution discharge speed, and avoids the engine discharging a large amount of exhaust gas during the idle speed and high speed operation, thereby reducing the exhaust gas. Emissions are 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 transmission system 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 speed, reduces the wear of the engine, prolongs the overhaul interval mileage, and is beneficial to improving productivity.
  • the present invention is a composite twin-turbo torque converter and a continuously variable transmission 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 view of a second embodiment of the present invention
  • the connection between two components in the drawing uses a thick solid line to indicate a fixed connection. The line indicates that the two elements can be rotated relative to each other.
  • Embodiment 1 is a diagrammatic representation of Embodiment 1:
  • a composite twin-turbo torque converter includes an input shaft 1 , an output shaft 3 , a coupling gear pair 4 , an input gear pair 5 , an overrunning clutch 6 , and a twin-turbo torque converter 7 .
  • the output gear pair 8 is provided with a planetary gear 20, an input gear 21, an output carrier 22, a fixed gear 23, an input small ring gear 24, a coupling carrier 25, and an input between the input shaft 1 and the output shaft 3.
  • the input end 61 of the 6 is coupled to the fixed component
  • the output carrier 22 is coupled to the input large ring gear 26, and the input large ring gear 26 cooperates with the input small ring gear 24 and the coupled planet carrier 25 through the planetary gear 20 thereon, and the input is small.
  • the ring gear 24 is coupled to the output end 52 of the input gear pair 5, the coupling carrier 25 is coupled to the input gear 41 of the coupling gear pair 4, and the output gear 42 of the coupling gear pair 4 is coupled to the input carrier 29 through which the input carrier 29 is Planet gear 20 and input ring gear 27, output
  • the ring 28 cooperates, the output ring gear 28 is coupled to the output shaft 3, the input ring gear 27, the input gear 51 of the input gear pair 5, and the output 62 of the overrunning clutch 6 are coupled to the output 72 of the twin-turbo torque converter 7.
  • the input end 71 of the twin-turbo torque converter 7 is coupled to the output gear 82 of the output gear pair 8, the input gear 81 of the output gear set 8 and the input gear 21 are coupled to the input shaft 1.
  • the input small ring gear 24 and the input large ring gear 26 converge the power transmitted thereto by the planetary gears 20 coupled to the carrier 25 to the coupling carrier 25, and the coupling carrier 25 is transmitted to the input carrier 29 through the coupling gear pair 4.
  • the input ring gear 27, the input carrier 29, and the power transmitted thereto through the planetary gears 20 on the input carrier 29 are merged to the output ring gear 28.
  • the two power flows will change according to the change of the rotational speed distribution between the two.
  • the large ring gear 26 is input.
  • the input planet carrier 29 is decelerated and increased in torque.
  • the rotational speed of the connecting carrier 25 and the output ring gear 28 also increases, that is, When the rotational speed of the input small ring gear 24 and the input ring gear 27 changes, the rotational speeds of the coupled carrier 25, the output ring gear 28, and the output shaft 3 also change.
  • the input power is split into two paths via the input shaft 1, and the first path is transmitted to the twin-turbo torque converter 7 via the output gear pair 8, and the twin-turbo torque converter 7 is split into two paths, one way to
  • the input ring gear 27 is input to the input pinion ring 24 through the input gear pair 5; the second path is passed to the input gear 21, and the power is transmitted to the output carrier 22 through the planetary gears 20 on the output carrier 22.
  • the output carrier 22 is further transmitted to the input large ring gear 26, the input small ring gear 24, the input large ring gear 26 is connected to the coupled planet carrier 25 by the planetary gears 20 coupled to the carrier 25, and then coupled
  • the gear pair 4 is transmitted to the input carrier 29, the input ring gear 27, the input carrier 29 and the power transmitted thereto through the planetary gears 20 on the input carrier 29 are merged to the output ring gear 28 and then transmitted to the output shaft 3, Thereby, the power of the engine is externally outputted through the output shaft 3.
  • the twin-turbo torque converter 7 when the rotational speed of the input shaft 1 is constant, the torque on the coupled carrier 25, the output ring gear 28, and the output shaft 3 varies with the change of the rotational speed thereof, and the lower the rotational speed is transmitted to the coupled carrier 25 and the output teeth.
  • the torque on the ring 28 and the output shaft 3 is larger, and conversely, the smaller, in the process, the twin-turbo torque converter 7 also acts as a torque converter, thereby realizing the difference in the driving resistance of the present invention with the vehicle.
  • a compound twin-turbo torque converter that changes torque and speed.
  • 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 3 is zero, and the input power of the engine passes through the input shaft 1 And transmitted to the input gear 21, and then the power is transmitted to the output carrier 22 through the planetary gears 20 on the output carrier 22, and the output carrier 22 is transferred to the input large ring gear 26, wherein there is no power or less at this time. Power flow into the input small ring gear 24.
  • the input ring gear 27 is input, and the input end 61 of the overrunning clutch 6 is coupled with the fixed component to restrict the steering, so that the steering of the input small ring gear 24 and the input ring gear 27 cannot be opposite to the input steering, and the rotational speed is zero.
  • the power transmitted to the input large ring gear 26 is transmitted to the coupled carrier 25 through the planetary gear 20 coupled to the carrier 25, and then transmitted to the input carrier 29 through the coupling gear pair 4.
  • the input carrier 29 then passes the power transmitted thereto through the planetary gears 20 on the input carrier 29 to the output ring gear 28, and then to the output shaft 3, and the torque transmitted to the output shaft 3 is transmitted to the transmission system through the transmission system.
  • the car starts and starts to accelerate, and the rotational speed of the output end 72 of the twin-turbo torque converter 7 is gradually increased, and the input small ring gear 24, input is connected thereto.
  • the rotational speed of the ring gear 27 also gradually increases, so that the torque of the coupling carrier 25, the output ring gear 28, and the output shaft 3 decreases as the number of revolutions increases.
  • Embodiment 2 is a diagrammatic representation of Embodiment 1:
  • a continuously variable transmission of a composite twin-turbo torque converter includes an input shaft 1, an output shaft 3, a twin-turbo torque converter 4, an input gear pair 5, an overrunning clutch 6, Coupling gear pair 7, input gear 8, output gear pair 9, between the input shaft 1 and the output shaft 3, a planetary gear 20, a fixed planet carrier 21, an input ring gear 22, an output ring gear 23, and a coupled planet carrier are disposed. 24.
  • the input end 41 of the torque converter 4 and the input gear 91 of the output gear pair 9 are coupled to the input shaft 1, and the input ring gear 22 cooperates with the fixed carrier 21 and the output ring gear 23 via the planetary gear 20 on the fixed carrier 21.
  • the fixed carrier 21 and the input end 61 of the overrunning clutch 6 are coupled to the fixed element, and the output ring gear 23 is coupled to the input gear 25.
  • the input gear 25 is coupled to the planet carrier 24 and the output large gear by the planetary gear 20 coupled to the carrier 24.
  • the ring 26 cooperates with the input gear 8 and the output large ring gear 26
  • the input planet carrier 31 is coupled
  • the input planet carrier 31 cooperates with the output gear 30 and the input pinion 32 through the planetary gear 20 thereon, and the input pinion 32, the output end 62 of the overrunning clutch 6, and the output gear of the coupling gear pair 7 72 is coupled to the output gear 52 of the input gear pair 5,
  • the input gear 71 of the coupling gear pair 7 is coupled to the coupling carrier 24, and the input gear 51 of the input gear pair 5 is coupled to the output 42 of the twin-turbo torque converter 4,
  • the output gear 30 is coupled to the input large ring gear 29, and the input large ring gear 29 cooperates with the input large gear 27 and the output carrier 28 through the planetary gear 20 on the output carrier 28, and the output of the input large gear 27 and the output gear pair 9
  • Gear 92 is coupled and output planet carrier 28 is coupled to output shaft 3.
  • the connecting carrier 24 and the input gear 25 converge the power transmitted thereto through the planetary gear 20 coupled to the carrier 24 to the output large ring gear 26, and the output large ring gear 26 is transmitted to the input carrier 31 through the input gear 8.
  • the input carrier 31 and the input pinion 32 converge the power transmitted thereto through the planetary gears 20 on the input carrier 31 to the output gear 30.
  • the two power flows will change according to the change of the rotational speed distribution between the two.
  • the rotational speed of the connecting carrier 24 and the input pinion 32 is zero, the input gear 25 and the input planet are input.
  • the frame 31 is reduced in speed, and when the rotational speed of the connecting carrier 24 and the input pinion 32 is continuously increased, the rotational speed of the output large ring gear 26 and the output gear 30 also increases, that is, when the planetary carrier is coupled 24.
  • the rotational speed of the input pinion 32 changes, the rotational speeds of the output large ring gear 26, the output gear 30, and the output shaft 3 also change.
  • the input power is divided into three paths via the input shaft 1, the first path is output to the input large gear 27 via the output gear pair 9, and the second path is transmitted to the input gear pair 5 via the twin-turbine torque converter 4, and the input is input.
  • the gear pair 5 is split into two paths, one for the input pinion 32, the other for the coupled gear pair 7, to the coupled planet carrier 24; the third for the input ring gear 22, and for the planet on the fixed planet carrier 21
  • the gear 20 transmits power to the output ring gear 23 and then to the output
  • the input gear 25, the connecting carrier 24, the input gear 25 and the planetary gear 20 coupled to the carrier 24 converge the power transmitted thereto to the output large ring gear 26, and then through the input gear 8, to the input carrier 31, the input
  • the carrier 31 and the input pinion 32 converge the power transmitted thereto through the planetary gears 20 on the input carrier 31 to the output gear 30, and the output gear 30 is transmitted to the input large ring gear 29, the input large gear 27, and the input large teeth.
  • the ring 29 converge
  • the twin-turbo torque converter 4 when the rotational speed of the input shaft 1 is constant, the torque on the output large ring gear 26, the output gear 30, and the output shaft 3 varies with the change of the rotational speed thereof, and the lower the rotational speed is transmitted to the output large ring gear 26 and the output.
  • the torque on the gear 30 and the output shaft 3 is larger, and conversely, the smaller, in the process, the twin-turbo torque converter 4 also acts as a torque converter, thereby realizing the difference in the driving resistance of the present invention with the vehicle.
  • a continuously variable transmission of a composite twin-turbo torque converter that changes torque and speed.
  • 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 3 is zero, and the input power of the engine passes through the input shaft 1 Passing to the input ring gear 22 and transmitting power to the output ring gear 23 through the planet gears 20 on the fixed planet carrier 21, and then to the input gear 25, wherein no or less power flows into the coupled planet carrier at this time.
  • the input pinion 32, and the input end 61 of the overrunning clutch 6 is coupled with the fixed component to limit the steering, so that the steering of the connecting carrier 24 and the input pinion 32 cannot be opposite to the input steering, and the rotational speed is zero.
  • the power transmitted to the input gear 25 is transferred to the output large ring gear 26 through the planetary gear 20 coupled to the carrier 24, and then transmitted to the input carrier 31 through the input gear 8, and the input planet
  • the frame 31 is coupled to the output gear 30 via the planetary gears 20 thereon, and the output gear 30 is transmitted to the input large ring gear 29, the input large gear 27, and the input large ring gear 29 through the output.
  • the planetary gears 20 on the star frame 28 converge the power transmitted thereto to the output carrier 28, and the output carrier 28 is transferred to the output shaft 3, and the torque transmitted to the output shaft 3 is transmitted to the drive wheels via the transmission system.
  • the vehicle starts and starts to accelerate, and the rotational speed of the output end 42 of the twin-turbo torque converter 4 is also gradually increased, and the speed of the coupled carrier 24 and the input pinion 32 is associated with it. It also gradually increases, so that the torque of the output large ring gear 26, the output gear 30, and the output shaft 3 decreases as the number of revolutions increases.

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

Abstract

一种复合型双涡轮液力变矩器，其中，输出行星架（22）与输入大齿圈（26）联接，输入小齿圈（24）与输入齿轮副（5）联接，联接行星架（25）与联接齿轮副（4）联接，联接齿轮副（4）与输入行星架（29）联接，输出齿圈（28）与输出轴（3）联接，输入齿圈（27）、输入齿轮副（5）以及超越离合器（6）与双涡轮液力变矩器（7）联接，双涡轮液力变矩器（7）与输出齿轮副（8）联接，输出齿轮副（8）以及输入齿轮（21）与输入轴（1）联接。此外，还提供了一种复合型双涡轮液力变矩器的无级变速器。

Description

一种复合型双涡轮液力变矩器以及无级变速器 技术领域
本发明属于液力变矩器以及变速领域，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涡轮液力变矩器以及无级变速器。
背景技术
目前，液力变矩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涡轮液力变矩器以及无级变速器。
为了实现本发明的目的，本发明采用的技术方案以下：
一种复合型双涡轮液力变矩器，包括输入轴(1)、输出轴(3)、联接齿轮副(4)、输入齿轮副(5)、超越离合器(6)、双涡轮液力变矩器(7)、输出齿轮副(8)，所述的输入轴(1)与输出轴(3)之间设有行星齿轮(20)、输入齿轮(21)、输出行星架(22)、固定齿轮(23)、输入小齿圈(24)、联接行星架(25)、输入大齿圈(26)、输入齿圈(27)、输出齿圈(28)、输入行星架(29),输入齿轮(21)通过输出行星架(22)上的行星齿轮(20)与输出行星架(22)、固定齿轮(23)配合工作，固定齿轮(23)以及超越离合器(6)的输入端(61)与固定元件联接,输出行星架(22)与输入大齿圈(26)联接,输入大齿圈(26)通过其上的行星齿轮(20)与输入小齿圈(24)、联接行星架(25)配合工作，输入小齿圈(24)与输入齿轮副(5)的输出端(52)联接,联接行星架(25)与联接齿轮副(4)的输入齿轮(41)联接,联接齿轮副(4)的输出齿轮(42)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)与输入齿圈(27)、输出齿圈(28)配合工作，输出齿圈(28)与输出轴(3)联接，输入齿圈(27)、输入齿轮副(5)的输入齿轮(51)以及超越离合器(6)的输出端(62)与双涡轮液力变矩器(7)的输出端(72)联接,双涡轮液力变矩器(7)的输入端(71)与输出齿轮副(8)的输出齿轮(82)联接,输出齿轮副(8)的输入齿轮(81)以及输入齿轮(21)与输入轴(1)联接。
一种复合型双涡轮液力变矩器的无级变速器，包括输入轴(1)、输出轴(3)、双涡轮液力变矩器(4)、输入齿轮副(5)、超越离合器(6)、联接齿轮副(7)、输入齿轮(8)、输出齿轮副(9)，所述的输入轴(1)与输出轴(3)之间设有行星齿轮(20)、固定行星架(21)、输入齿圈(22)、输出齿圈(23)、联接行星架(24)、输入齿轮(25)、输出大齿圈(26)、输入大齿轮(27)、输出行星架(28)、输入大齿圈(29)、输出齿轮(30)、输入行星架(31)、输入小齿轮(32),输入齿圈(22)、双涡轮液力变矩器(4)的输入端(41)以及输出齿轮副(9)的输入齿轮(91)与输入轴(1)联接,输入齿圈(22)通过固定行星架(21)上的行星齿轮(20)与固定行星架(21)、输出齿圈(23)配合工作，固定行星架(21)以及超越离合器(6)的输入端(61)与固定元件联接,输出齿圈(23)与输入齿轮(25)联接,输入齿轮(25)通过联接行星架(24)上的行星齿轮(20)与联接行星架(24)、输出大齿圈(26)配合工作，输入齿轮(8)与输 出大齿圈(26)以及输入行星架(31)联接,输入行星架(31)通过其上的行星齿轮(20)与输出齿轮(30)、输入小齿轮(32)配合工作，输入小齿轮(32)、超越离合器(6)的输出端(62)以及联接齿轮副(7)的输出齿轮(72)与输入齿轮副(5)的输出齿轮(52)联接,联接齿轮副(7)的输入齿轮(71)与联接行星架(24)联接,输入齿轮副(5)的输入齿轮(51)与双涡轮液力变矩器(4)的输出端(42)联接,输出齿轮(30)与输入大齿圈(29)联接,输入大齿圈(29)通过输出行星架(28)上的行星齿轮(20)与输入大齿轮(27)、输出行星架(28)配合工作，输入大齿轮(27)与输出齿轮副(9)的输出齿轮(92)联接,输出行星架(28)与输出轴(3)联接。
所述各个需要联接的元件,可直接连接，当被其它若干元件分隔时,可采用联接轴、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；各个不需要联接的元件，可以相对转动。
所述各个齿轮副以及变速机构的传动比，按实际需要设计。
所述液力变矩器可选用液力偶合器、压马达和液压泵以及电磁离合器。
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统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。
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涡轮液力变矩器以及无级变速器。
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，一种复合型双涡轮液力变矩器，包括输入轴1、输出轴3、联接齿轮副4、输入齿轮副5、超越离合器6、双涡轮液力变矩器7、输出齿轮副8，所述的输入轴1与输出轴3之间设有行星齿轮20、输入齿轮21、输出行星架22、固定齿轮23、输入小齿圈24、联接行星架25、输入大齿圈26、输入齿圈27、输出齿圈28、输入行星架29,输入齿轮21通过输出行星架22上的行星齿轮20与输出行星架22、固定齿轮23配合工作，固定齿轮23以及超越离合器6的输入端61与固定元件联接,输出行星架22与输入大齿圈26联接,输入大齿圈26通过其上的行星齿轮20与输入小齿圈24、联接行星架25配合工作，输入小齿圈24与输入齿轮副5的输出端52联接,联接行星架25与联接齿轮副4的输入齿轮41联接,联接齿轮副4的输出齿轮42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与输入齿圈27、输出齿圈28配合工作，输出齿圈28与输出轴3联接，输入齿圈27、输入齿轮副5的输入齿轮51以及超越离合器6的输出端62与双涡轮液力变矩器7的输出端72联接,双涡轮液力变矩器7的输入端71与输出齿轮副8的输出齿轮82联接,输出齿轮副8的输入齿轮81以及输入齿轮21与输入轴1联接。
输入小齿圈24、输入大齿圈26通过联接行星架25上的行星齿轮20把传递到此的功率汇流于联接行星架25,联接行星架25通过联接齿轮副4,传递到输入行星架29,输入齿圈27、输入行星架29再通过输入行星架29上的行星齿轮20把传递到此的功率汇流于输出齿圈28。
由于上述各个元件的转速分配关系可以改变,两路功率流将根据两者之间转速分配的变化而变化，当输入小齿圈24、输入齿圈27的转速为零时，输入大齿圈26、输入行星架29则降速增矩，当输入小齿圈24、输入齿圈27的转速不断升高时，联接行星架25、输出齿圈28的转速也随之升高，也就是说，当输入小齿圈24、输入齿圈27的转速发生变化时，联接行星架25、输出齿圈28以及输出轴3的转速也随之变化。
输入功率经输入轴1把功率分流为两路，第一路经输出齿轮副8，传递到双涡轮液力变矩器7，双涡轮液力变矩器7再分流为两路，一路传递到输入齿圈27,另一路经输入齿轮副5,再传递到输入小齿圈24；第二路经输入齿轮21，再通过输出行星架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再传递到输入大齿圈26，输入小齿圈24、输入大齿圈26通过联接行星架25上的行星齿轮20把传递到此的功率汇流于联接行星架25,再通过联接齿轮副4传递到输入行星架29,输入齿圈27、输入行星架29再通过输入行星架29上的行星齿轮20把传递到此的功率汇流于输出齿圈28，再传递到输出轴3,从而实现了把发动机的功率通过输出轴3对外输出。
对于本发明，当输入轴1的转速不变，联接行星架25、输出齿圈28以及输出轴3上的扭矩随其转速的变化而变化，转速越低，传递到联接行星架25、输出齿圈28以及输出轴3上的扭矩就越大，反之，则越小，在此过程中，双涡轮液力变矩器7也起变矩的作用，从而实现本发明能随车辆行驶阻力的不同而改变力矩以及速度的复合型双涡轮液力变矩器。
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3的转速为零，发动机的输入功率经输入轴1，传递到输入齿轮21，再通过输出行星架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再传递到输入大齿圈26，其中，由于此时没有功率或比较少的功率流入输入小齿圈 24、输入齿圈27，并且超越离合器6的输入端61与固定元件联接,起限制转向的作用，使输入小齿圈24、输入齿圈27的转向不能与输入的转向相反，转速为零，此时，传递到输入大齿圈26的功率，则通过联接行星架25上的行星齿轮20把传递到此的功率汇流于联接行星架25,再通过联接齿轮副4传递到输入行星架29,输入行星架29再通过输入行星架29上的行星齿轮20把传递到此的功率汇流于输出齿圈28，再传递到输出轴3,当传递到输出轴3上的扭矩，经传动系统传动到驱动轮上产生的牵引力足以克服汽车起步阻力时,汽车则起步并开始加速，双涡轮液力变矩器7的输出端72的转速也逐渐增加，与之相联的输入小齿圈24、输入齿圈27的转速也随之逐渐增加，从而使联接行星架25、输出齿圈28以及输出轴3的扭矩随着转速的增加而减少。
实施例二：
如图2中所示，一种复合型双涡轮液力变矩器的无级变速器，包括输入轴1、输出轴3、双涡轮液力变矩器4、输入齿轮副5、超越离合器6、联接齿轮副7、输入齿轮8、输出齿轮副9，所述的输入轴1与输出轴3之间设有行星齿轮20、固定行星架21、输入齿圈22、输出齿圈23、联接行星架24、输入齿轮25、输出大齿圈26、输入大齿轮27、输出行星架28、输入大齿圈29、输出齿轮30、输入行星架31、输入小齿轮32,输入齿圈22、双涡轮液力变矩器4的输入端41以及输出齿轮副9的输入齿轮91与输入轴1联接,输入齿圈22通过固定行星架21上的行星齿轮20与固定行星架21、输出齿圈23配合工作，固定行星架21以及超越离合器6的输入端61与固定元件联接,输出齿圈23与输入齿轮25联接,输入齿轮25通过联接行星架24上的行星齿轮20与联接行星架24、输出大齿圈26配合工作，输入齿轮8与输出大齿圈26以及输入行星架31联接,输入行星架31通过其上的行星齿轮20与输出齿轮30、输入小齿轮32配合工作，输入小齿轮32、超越离合器6的输出端62以及联接齿轮副7的输出齿轮72与输入齿轮副5的输出齿轮52联接,联接齿轮副7的输入齿轮71与联接行星架24联接,输入齿轮副5的输入齿轮51与双涡轮液力变矩器4的输出端42联接,输出齿轮30与输入大齿圈29联接,输入大齿圈29通过输出行星架28上的行星齿轮20与输入大齿轮27、输出行星架28配合工作，输入大齿轮27与输出齿轮副9的输出齿轮92联接,输出行星架28与输出轴3联接。
联接行星架24、输入齿轮25通过联接行星架24上的行星齿轮20把传递到此的功率汇流于输出大齿圈26,输出大齿圈26再通过输入齿轮8,传递到输入行星架31,输入行星架31、输入小齿轮32通过输入行星架31上的行星齿轮20把传递到此的功率汇流于输出齿轮30。
由于上述各个元件的转速分配关系可以改变,两路功率流将根据两者之间转速分配的变化而变化，当联接行星架24、输入小齿轮32的转速为零时，输入齿轮25、输入行星架31则降速增矩，当联接行星架24、输入小齿轮32的转速不断升高时，输出大齿圈26、输出齿轮30的转速也随之升高，也就是说，当联接行星架24、输入小齿轮32的转速发生变化时，输出大齿圈26、输出齿轮30以及输出轴3的转速也随之变化。
输入功率经输入轴1把功率分流为三路，第一路经输出齿轮副9,传递到输入大齿轮27；第二路经双涡轮液力变矩器4,传递到输入齿轮副5，输入齿轮副5再分流为两路，一路传递到输入小齿轮32，另一路经联接齿轮副7,传递到联接行星架24；第三路经输入齿圈22,并通过固定行星架21上的行星齿轮20把功率传递到输出齿圈23，再传递到输 入齿轮25,联接行星架24、输入齿轮25通过联接行星架24上的行星齿轮20把传递到此的功率汇流于输出大齿圈26,再通过输入齿轮8,传递到输入行星架31,输入行星架31、输入小齿轮32通过输入行星架31上的行星齿轮20把传递到此的功率汇流于输出齿轮30,输出齿轮30再传递到输入大齿圈29,输入大齿轮27、输入大齿圈29通过输出行星架28上的行星齿轮20把传递到此的功率汇流于输出行星架28，输出行星架28再传递到输出轴3,从而实现了把发动机的功率通过输出轴3对外输出。
对于本发明，当输入轴1的转速不变，输出大齿圈26、输出齿轮30以及输出轴3上的扭矩随其转速的变化而变化，转速越低，传递到输出大齿圈26、输出齿轮30以及输出轴3上的扭矩就越大，反之，则越小，在此过程中，双涡轮液力变矩器4也起变矩的作用，从而实现本发明能随车辆行驶阻力的不同而改变力矩以及速度的复合型双涡轮液力变矩器的无级变速器。
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3的转速为零，发动机的输入功率经输入轴1，传递到输入齿圈22,并通过固定行星架21上的行星齿轮20把功率传递到输出齿圈23，再传递到输入齿轮25,其中，由于此时没有或比较少的功率流入联接行星架24、输入小齿轮32，并且超越离合器6的输入端61与固定元件联接,起限制转向的作用，使联接行星架24、输入小齿轮32的转向不能与输入的转向相反，转速为零，此时，传递到输入齿轮25的功率，则通过联接行星架24上的行星齿轮20把传递到此的功率汇流于输出大齿圈26,再通过输入齿轮8,传递到输入行星架31,输入行星架31通过其上的行星齿轮20把传递到此的功率汇流于输出齿轮30,输出齿轮30再传递到输入大齿圈29,输入大齿轮27、输入大齿圈29通过输出行星架28上的行星齿轮20把传递到此的功率汇流于输出行星架28，输出行星架28再传递到输出轴3,当传递到输出轴3上的扭矩，经传动系统传动到驱动轮上产生的牵引力足以克服汽车起步阻力时,汽车则起步并开始加速，双涡轮液力变矩器4输出端42的转速也逐渐增加，与之相联的联接行星架24、输入小齿轮32的转速也随之逐渐增加，从而使输出大齿圈26、输出齿轮30以及输出轴3的扭矩随着转速的增加而减少。

Claims (2)

  1. 一种复合型双涡轮液力变矩器，包括输入轴(1)、输出轴(3)、联接齿轮副(4)、输入齿轮副(5)、超越离合器(6)、双涡轮液力变矩器(7)、输出齿轮副(8)，其特征在于：所述的输入轴(1)与输出轴(3)之间设有行星齿轮(20)、输入齿轮(21)、输出行星架(22)、固定齿轮(23)、输入小齿圈(24)、联接行星架(25)、输入大齿圈(26)、输入齿圈(27)、输出齿圈(28)、输入行星架(29),输入齿轮(21)通过输出行星架(22)上的行星齿轮(20)与输出行星架(22)、固定齿轮(23)配合工作，固定齿轮(23)以及超越离合器(6)的输入端(61)与固定元件联接,输出行星架(22)与输入大齿圈(26)联接,输入大齿圈(26)通过其上的行星齿轮(20)与输入小齿圈(24)、联接行星架(25)配合工作，输入小齿圈(24)与输入齿轮副(5)的输出端(52)联接,联接行星架(25)与联接齿轮副(4)的输入齿轮(41)联接,联接齿轮副(4)的输出齿轮(42)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)与输入齿圈(27)、输出齿圈(28)配合工作，输出齿圈(28)与输出轴(3)联接，输入齿圈(27)、输入齿轮副(5)的输入齿轮(51)以及超越离合器(6)的输出端(62)与双涡轮液力变矩器(7)的输出端(72)联接,双涡轮液力变矩器(7)的输入端(71)与输出齿轮副(8)的输出齿轮(82)联接,输出齿轮副(8)的输入齿轮(81)以及输入齿轮(21)与输入轴(1)联接。
  2. 一种复合型双涡轮液力变矩器的无级变速器，包括输入轴(1)、输出轴(3)、双涡轮液力变矩器(4)、输入齿轮副(5)、超越离合器(6)、联接齿轮副(7)、输入齿轮(8)、输出齿轮副(9)，其特征在于：所述的输入轴(1)与输出轴(3)之间设有行星齿轮(20)、固定行星架(21)、输入齿圈(22)、输出齿圈(23)、联接行星架(24)、输入齿轮(25)、输出大齿圈(26)、输入大齿轮(27)、输出行星架(28)、输入大齿圈(29)、输出齿轮(30)、输入行星架(31)、输入小齿轮(32),输入齿圈(22)、双涡轮液力变矩器(4)的输入端(41)以及输出齿轮副(9)的输入齿轮(91)与输入轴(1)联接,输入齿圈(22)通过固定行星架(21)上的行星齿轮(20)与固定行星架(21)、输出齿圈(23)配合工作，固定行星架(21)以及超越离合器(6)的输入端(61)与固定元件联接,输出齿圈(23)与输入齿轮(25)联接,输入齿轮(25)通过联接行星架(24)上的行星齿轮(20)与联接行星架(24)、输出大齿圈(26)配合工作，输入齿轮(8)与输出大齿圈(26)以及输入行星架(31)联接,输入行星架(31)通过其上的行星齿轮(20)与输出齿轮(30)、输入小齿轮(32)配合工作，输入小齿轮(32)、超越离合器(6)的输出端(62)以及联接齿轮副(7)的输出齿轮(72)与输入齿轮副(5)的输出齿轮(52)联接,联接齿轮副(7)的输入齿轮(71)与联接行星架(24)联接,输入齿轮副(5)的输入齿轮(51)与双涡轮液力变矩器(4)的输出端(42)联接,输出齿轮(30)与输入大齿圈(29)联接,输入大齿圈(29)通过输出行星架(28)上的行星齿轮(20)与输入大齿轮(27)、输出行星架(28)配合工作，输入大齿轮(27)与输出齿轮副(9)的输出齿轮(92)联接,输出行星架(28)与输出轴(3)联接。
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