WO2016112803A1 - 一种复合型导叶可调式液力变矩器以及无级变速器 - Google Patents

一种复合型导叶可调式液力变矩器以及无级变速器 Download PDF

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Publication number
WO2016112803A1
WO2016112803A1 PCT/CN2016/070212 CN2016070212W WO2016112803A1 WO 2016112803 A1 WO2016112803 A1 WO 2016112803A1 CN 2016070212 W CN2016070212 W CN 2016070212W WO 2016112803 A1 WO2016112803 A1 WO 2016112803A1
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input
gear
output
coupled
carrier
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PCT/CN2016/070212
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English (en)
French (fr)
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吴志强
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吴志强
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Priority to CN201680004297.6A priority Critical patent/CN108027032A/zh
Publication of WO2016112803A1 publication Critical patent/WO2016112803A1/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

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  • the invention belongs to the field of torque converter and shifting, and more particularly to a composite vane adjustable 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 guide vane adjustable hydraulic torque converter and a continuously variable transmission which have the advantages of simple extension, convenient operation, low cost, energy saving and high efficiency.
  • a composite vane adjustable hydraulic torque converter comprising an input shaft (1), an output shaft (3), an input gear (4), an overrunning clutch (5), and a vane adjustable hydraulic torque converter (6) ), the output gear pair (7), between the input shaft (1) and the output shaft (3) is provided with a planetary gear (20), a fixed planet carrier (21), an input pinion (22), an output gear (23), connecting the carrier (24), input ring gear (25), input gear (26), output carrier (27), input small ring gear (28), input large ring gear (29), input pinion (22) and the input gear (71) of the output gear pair (7) is coupled to the input shaft (1), and the input pinion (22) passes through the planetary gear (20) on the fixed carrier (21) and the fixed carrier (21) ), the output large gear (23) works together, the fixed carrier (21) and the input end (51) of the overrunning clutch (5) are coupled with the fixed component, and the output large gear (23) and the vane adjustable hydraulic torque converter
  • the input end (61) of (6) is coupled, and the output end
  • the gear (4) is coupled to the input large ring gear (29), and the input large ring gear (29) is output through the planet
  • the planetary gear (20) on the frame (27) cooperates with the output carrier (27) and the input small ring gear (28), the output carrier (27) is coupled with the output shaft (3), and the output gear pair (7) is output.
  • the output gear (72) is coupled to the input gear (26), and the input gear (26) cooperates with the coupling planet carrier (24) and the input ring gear (25) through the planetary gear (20) coupled to the carrier (24), input
  • the ring gear (25) is coupled to the input large ring gear (29), and the coupled planet carrier (24) is coupled to the input small ring gear (28).
  • a continuously variable transmission of a composite vane adjustable torque converter comprising an input shaft (1), an output shaft (3), a coupling output gear pair (4), a coupling input gear pair (5), an overrunning clutch ( 6), guide vane adjustable torque converter (7), output gear pair (8), between the input shaft (1) and the output shaft (3) is provided with a planetary gear (20), a fixed planet carrier (21), input gear (22), output ring gear (23), input ring gear (24), input large gear (25), output carrier (26), coupling pinion (27), connecting planet carrier (28 ), connecting the large gear (29), the input planet carrier (30), the input small ring gear (31), the output large ring gear (32), and the planetary gear (20) and the input gear through which the fixed carrier (21) is fixed (22)
  • the output ring gear (23) cooperates, the fixed carrier (21) and the input end (61) of the overrunning clutch (6) are coupled with the fixed component, the input gear (22) and the input input gear pair (5)
  • the output gear (52) is coupled, and the
  • Output gear (82) of gear pair (8) and guide vane adjustable hydraulic force The torque converter (7) an input terminal (71) coupled vanes adjustable hydraulic torque converter
  • the output end (72) of (7) is coupled to the input large gear (25), the coupling large gear (29), and the output end (62) of the overrunning clutch (6), and the output ring gear (23) and the input ring gear (24)
  • the input ring gear (24) cooperates with the input bull gear (25) and the output planet carrier (26) through the planetary gears (20) on the output carrier (26), and outputs the planet carrier (26) and the coupling pinion ( 27)
  • the coupling pinion (27) cooperates with the coupling planet carrier (28) and the coupling gear (29) through the planetary gear (20) coupled to the planet carrier (28), and connects the planet carrier (28) and the coupling output.
  • An input gear (41) of the gear pair (4) is coupled with an output gear (42) coupled to the output gear pair (4) and coupled to the input carrier (30), and the planetary gear (20) through which the carrier (30) passes is input. ) Cooperate with the input small ring gear (31) and the output large ring gear (32), and the output large ring gear (32) is coupled with 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 guide vane adjustable 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, and a thin solid line indicates The two elements can be rotated relative to each other.
  • Embodiment 1 is a diagrammatic representation of Embodiment 1:
  • a composite guide vane adjustable torque converter includes an input shaft 1, an output shaft 3, an input gear 4, an overrunning clutch 5, a vane adjustable torque converter 6, and an output.
  • the gear pair 7 is provided with a planetary gear 20, a fixed carrier 21, an input pinion 22, an output bull gear 23, a coupling carrier 24, an input ring gear 25, and an input gear 26 between the input shaft 1 and the output shaft 3.
  • the output carrier 27, the input small ring gear 28, the input large ring gear 29, the input pinion 22 and the input gear 71 of the output gear pair 7 are coupled to the input shaft 1, and the input pinion 22 is passed through the planetary gear on the fixed carrier 21.
  • the coupling vane adjustable torque converter 6 is coupled to the output end 52 of the overrunning clutch 5 and the input gear 4, the input gear 4 is coupled to the input large ring gear 29, and the input large ring gear 29 is passed through the output carrier Planetary gear 20 on 27 and output planet carrier 27, input small ring gear 28 cooperates, the output carrier 27 is coupled to the output shaft 3, the output gear 72 of the output gear pair 7 is coupled to the input gear 26, and the input gear 26 is coupled to the planet carrier 24 and the input ring gear via the planet gear 20 coupled to the carrier 24.
  • the input ring gear 25 is coupled to the input large ring gear 29, and the coupling carrier 24 is coupled to the input small ring gear 28.
  • the input ring gear 25 and the input gear 26 converge the power transmitted thereto through the planetary gears 20 coupled to the carrier 24 to the coupling carrier 24, and the coupling carrier 24 is transmitted to the input small ring gear 28, and the input small ring gear 28, The input large ring gear 29 then converges the power transmitted thereto through the planetary gears 20 on the output carrier 27 to the output carrier 27.
  • the two power flows will change according to the change of the rotational speed distribution between the two.
  • the input ring gear 25 and the input large ring gear 29 have zero rotational speed
  • the input gear 26 and the input are input.
  • the small ring gear 28 is reduced in speed, and when the input ring gear 25 and the input large ring gear 29 are continuously increased in speed, the rotational speed of the connecting carrier 24 and the output carrier 27 also increases, that is, when When the input ring gear 25 and the rotational speed of the input large ring gear 29 are changed, the rotational speeds of the coupled carrier 24, the output carrier 27, and the output shaft 3 also change.
  • the input power is split into two paths through the input shaft 1, one through the input pinion 22, and then the power is transmitted to the output bull gear 23 through the planetary gear 20 on the fixed carrier 21, and the output large gear 23 is transmitted to the vane.
  • the modulating torque converter 6 is transmitted to the input large ring gear 29 and the input ring gear 25 via the input gear 4; the other path is transmitted to the input gear 26 via the output gear pair 7, the input ring gear 25, the input gear 26 and the
  • the planetary gears 20 coupled to the planet carrier 24 converge the power transmitted thereto to the coupled planet carrier 24, and then to the input small ring gear 28, the input small ring gear 28, the input large ring gear 29 and the output carrier 27
  • the planetary gear 20 converges the power transmitted thereto to the output carrier 27 and then to the output shaft 3, thereby realizing the external output of the engine power through the output shaft 3.
  • the torque on the coupled carrier 24, the output carrier 27, and the output shaft 3 varies with the change in the rotational speed thereof, and the lower the rotational speed, the transmission to the coupled carrier 24, the output planet.
  • a composite vane adjustable torque converter that varies 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
  • the output gear pair 7 is transmitted to the input gear 26, wherein no power or relatively little power flows into the input ring gear 25, the input large ring gear 29, and the input end 51 of the overrunning clutch 5 is coupled to the fixed element, Limiting the effect of the steering, the input ring gear 25, the input large ring gear 29 can not be reversed from the input steering, the rotational speed is zero, at this time, is transmitted to the input gear 26
  • the power is transmitted to the coupled planet carrier 24 by the planet gears 20 coupled to the planet carrier 24, the coupled planet carrier 24 is transferred to the input small ring gear 28, and the input small ring gear 28 is passed through the planets on the output planet carrier 27.
  • the gear 20 transmits power to the output carrier 27 and then to the output shaft 3.
  • the traction force generated is sufficient to overcome the starting resistance of the vehicle, and the vehicle starts.
  • the rotational speed of the output end 62 of the vane adjustable torque converter 6 is also gradually increased, and the rotational speed of the input input ring gear 25 and the input large ring gear 29 is also gradually increased, thereby connecting the planets.
  • the torque of the frame 24, the output carrier 27, 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 vane adjustable torque converter includes an input shaft 1, an output shaft 3, a coupled output gear pair 4, a coupled input gear pair 5, an overrunning clutch 6, Guide vane adjustable torque converter 7, output gear pair 8, between the input shaft 1 and the output shaft 3, a planetary gear 20, a fixed planet carrier 21, an input gear 22, an output ring gear 23, and an input tooth are disposed.
  • the ring 24, the input large gear 25, the output planet carrier 26, the coupling pinion 27, the coupling planet carrier 28, the coupling large gear 29, the input carrier 30, the input small ring gear 31, the output large ring gear 32, and the fixed carrier 21 pass The planetary gear 20 thereon cooperates with the input gear 22 and the output ring gear 23.
  • the fixed end of the fixed carrier 21 and the overrunning clutch 6 is coupled to the fixed component, and the input gear 22 is coupled to the output gear 52 of the input input gear pair 5.
  • the input gear 51 coupled to the input gear pair 5, the input gear 81 of the output gear pair 8 and the input small ring gear 31 are coupled to the input shaft 1, and the output gear 82 of the output gear pair 8 and the vane adjustable torque converter 7
  • Input end 71 is coupled, vane adjustable torque converter 7
  • the output end 72 is coupled to the input bull gear 25, the coupling bull gear 29 and the output 62 of the overrunning clutch 6, the output ring gear 23 is coupled to the input ring gear 24, and the input ring gear 24 is passed through the planet gear 20 and the input on the output carrier 26.
  • the large gear 25 and the output carrier 26 cooperate, the output carrier 26 is coupled with the coupling pinion 27, and the coupling pinion 27 cooperates with the coupling carrier 28 and the coupling gear 29 through the planetary gear 20 coupled to the carrier 28, and is coupled.
  • the carrier 28 is coupled to the input gear 41 coupled to the output gear pair 4, and the output gear 42 of the coupled output gear pair 4 is coupled to the input carrier 30, and the input carrier 30 passes the planetary gear 20 and the input small ring gear 31,
  • the output large ring gear 32 cooperates, and the output large ring gear 32 is coupled to the output shaft 3.
  • the input ring gear 24 and the input large gear 25 converge the power transmitted thereto through the planetary gears 20 on the output carrier 26 to the output carrier 26, and the output carrier 26 is transmitted to the coupling pinion 27, the coupling pinion 27, and the coupling.
  • the bull gear 29 converges the power transmitted thereto to the coupled planet carrier 28 by the planet gears 20 coupled to the planet carrier 28.
  • the two power flows will change according to the change of the rotational speed distribution between the two.
  • the input large gear 25 and the rotational speed of the coupling large gear 29 are zero, the input ring gear 24 is connected.
  • the pinion gear 27 is reduced in speed and the torque is increased.
  • the rotational speed of the input large gear 25 and the connecting large gear 29 is continuously increased, the rotational speed of the output carrier 26 and the coupled carrier 28 also increases, that is, when the input is large.
  • the rotational speed of the gear 25 and the coupling large gear 29 changes, the rotational speeds of the output carrier 26, the coupled carrier 28, and the output shaft 3 also change.
  • the input power is divided into three paths via the input shaft 1, and the first path is outputted to the input large gear 25 and the coupled large gear 29 via the output gear pair 8 and the vane adjustable torque converter 7; the second path is coupled
  • the input gear pair 5 is transmitted to the input gear 22, and the input gear 22 transmits power to the output ring gear 23 through the planetary gears 20 on the fixed carrier 21, and then to the input ring gear 24, the input ring gear 24, and the input large gear 25
  • the power transmitted thereto is converged to the output carrier 26 via the planetary gears 20 on the output carrier 26, the output carrier 26 is transferred to the coupling pinion 27, the coupling pinion 27, and the coupling gear 29 are coupled to the carrier 28.
  • the planetary gear 20 converges the power transmitted thereto to the coupled planet carrier 28, and the coupled planet carrier 28 is coupled to the input planet carrier 30 through the coupled output gear pair 4;
  • the input small ring gear 31, the input planet carrier 30, the input small ring gear 31 and the power transmitted thereto through the planetary gears 20 on the input carrier 30 merge into the output large ring gear 32, and the output large ring gear 32 is transmitted again.
  • the torque on the output carrier 26, the coupled carrier 28, and the output shaft 3 varies with the change in the rotational speed thereof, and the lower the rotational speed, the transmission to the output carrier 26, the coupling of the planet
  • the guide vane adjustable torque converter 7 also acts as a torque converter, thereby achieving the driving resistance of the present invention with the vehicle.
  • a continuously variable transmission of a composite vane-adjustable torque converter that varies 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
  • the input gear pair 5 is coupled to the input gear 22, and the power is transmitted to the output ring gear 23 through the planetary gear 20 on the fixed carrier 21, and the output ring gear 23 is transmitted to the input ring gear 24, wherein No or relatively little power flows into the input bull gear 25, the coupling bull gear 29, and the input end 61 of the overrunning clutch 6 is coupled to the fixed element to limit the steering, so that the steering of the input bull gear 25 and the coupling large gear 29 cannot be The input steering is reversed, and the rotational speed is zero.
  • the power transmitted to the input ring gear 24 is transmitted to the output carrier 26 through the planetary gear 20 on the output carrier 26, and the output carrier 26 is re-circulated.
  • the coupling pinion 27 converges the power transmitted thereto by the planet gears 20 coupled to the planet carrier 28 to the coupling planet carrier 28, and the coupling planet carrier 28 is coupled
  • the gear pair 4 is transmitted to the input carrier 30, the input carrier 30, the input small ring gear 31 and the power transmitted thereto through the planetary gear 20 of the input carrier 30 are merged to the output large ring gear 32, and the output ring gear is output.
  • the traction force generated by the transmission system to the driving wheel is sufficient to overcome the starting resistance of the vehicle, the car starts and starts to accelerate, and the vane adjustable hydraulic force changes.
  • the rotational speed of the output end 72 of the torque device 7 is also gradually increased, and the rotational speeds of the input large gear 25 and the coupled large gear 29 are also gradually increased, thereby causing the output carrier 26, the coupling carrier 28 and the output shaft 3 to be connected.
  • the torque decreases as the speed increases.

Abstract

一种复合型导叶可调式液力变矩器，其中，输入小齿轮（22）以及输出齿轮副（7）与输入轴（1）联接，输出大齿轮（23）与导叶可调式液力变矩器（6）联接，导叶可调式液力变矩器（6）与超越离合器（5）以及输入齿轮（4）联接，输入齿轮（4）与输入大齿圈（29）联接，输出行星架（27）与输出轴（3）联接，输出齿轮副（7）与输入齿轮（26）联接，输入齿圈（25）与输入大齿圈（29）联接，联接行星架（24）与输入小齿圈（28）联接。此外，还提供了一种复合型导叶可调式液力变矩器的无级变速器。

Description

一种复合型导叶可调式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导叶可调式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，节能高效的复合型导叶可调式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：
一种复合型导叶可调式液力变矩器，包括输入轴(1)、输出轴(3)、输入齿轮(4)、超越离合器(5)、导叶可调式液力变矩器(6)、输出齿轮副(7)，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)、输入小齿轮(22)、输出大齿轮(23)、联接行星架(24)、输入齿圈(25)、输入齿轮(26)、输出行星架(27)、输入小齿圈(28)、输入大齿圈(29),输入小齿轮(22)以及输出齿轮副(7)的输入齿轮(71)与输入轴(1)联接,输入小齿轮(22)通过固定行星架(21)上的行星齿轮(20)与固定行星架(21)、输出大齿轮(23)配合工作，固定行星架(21)以及超越离合器(5)的输入端(51)与固定元件联接,输出大齿轮(23)与导叶可调式液力变矩器(6)的输入端(61)联接,导叶可调式液力变矩器(6)的输出端(62)与超越离合器(5)的输出端(52)以及输入齿轮(4)联接,输入齿轮(4)与输入大齿圈(29)联接,输入大齿圈(29)通过输出行星架(27)上的行星齿轮(20)与输出行星架(27)、输入小齿圈(28)配合工作，输出行星架(27)与输出轴(3)联接,输出齿轮副(7)的输出齿轮(72)与输入齿轮(26)联接,输入齿轮(26)通过联接行星架(24)上的行星齿轮(20)与联接行星架(24)、输入齿圈(25)配合工作，输入齿圈(25)与输入大齿圈(29)联接,联接行星架(24)与输入小齿圈(28)联接。
一种复合型导叶可调式液力变矩器的无级变速器，包括输入轴(1)、输出轴(3)、联接输出齿轮副(4)、联接输入齿轮副(5)、超越离合器(6)、导叶可调式液力变矩器(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)、固定行星架(21)、输入齿轮(22)、输出齿圈(23)、输入齿圈(24)、输入大齿轮(25)、输出行星架(26)、联接小齿轮(27)、联接行星架(28)、联接大齿轮(29)、输入行星架(30)、输入小齿圈(31)、输出大齿圈(32),固定行星架(21)通过其上的行星齿轮(20)与输入齿轮(22)、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,输入齿轮(22)与联接输入齿轮副(5)的输出齿轮(52)联接,联接输入齿轮副(5)的输入齿轮(51)、输出齿轮副(8)的输入齿轮(81)以及输入小齿圈(31)与输入轴(1)联接,输出齿轮副(8)的输出齿轮(82)与导叶可调式液力变矩器(7)的输入端(71)联接,导叶可调式液力变矩器 (7)的输出端(72)与输入大齿轮(25)、联接大齿轮(29)以及超越离合器(6)的输出端(62)联接,输出齿圈(23)与输入齿圈(24)联接,输入齿圈(24)通过输出行星架(26)上的行星齿轮(20)与输入大齿轮(25)、输出行星架(26)配合工作，输出行星架(26)与联接小齿轮(27)联接,联接小齿轮(27)通过联接行星架(28)上的行星齿轮(20)与联接行星架(28)、联接大齿轮(29)配合工作，联接行星架(28)与联接输出齿轮副(4)的输入齿轮(41)与联接,联接输出齿轮副(4)的输出齿轮(42)与输入行星架(30)联接,输入行星架(30)通过其上的行星齿轮(20)与输入小齿圈(31)、输出大齿圈(32)配合工作，输出大齿圈(32)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导叶可调式液力变矩器以及无级变速器。
附图说明
说明书图1为本发明实施例一的结构图；说明书图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，一种复合型导叶可调式液力变矩器，包括输入轴1、输出轴3、输入齿轮4、超越离合器5、导叶可调式液力变矩器6、输出齿轮副7，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、输入小齿轮22、输出大齿轮23、联接行星架24、输入齿圈25、输入齿轮26、输出行星架27、输入小齿圈28、输入大齿圈29,输入小齿轮22以及输出齿轮副7的输入齿轮71与输入轴1联接,输入小齿轮22通过固定行星架21上的行星齿轮20与固定行星架21、输出大齿轮23配合工作，固定行星架21以及超越离合器5的输入端51与固定元件联接,输出大齿轮23与导叶可调式液力变矩器6的输入端61联接,导叶可调式液力变矩器6的输出端62与超越离合器5的输出端52以及输入齿轮4联接,输入齿轮4与输入大齿圈29联接,输入大齿圈29通过输出行星架27上的行星齿轮20与输出行星架27、输入小齿圈28配合工作，输出行星架27与输出轴3联接,输出齿轮副7的输出齿轮72与输入齿轮26联接,输入齿轮26通过联接行星架24上的行星齿轮20与联接行星架24、输入齿圈25配合工作，输入齿圈25与输入大齿圈29联接,联接行星架24与输入小齿圈28联接。
输入齿圈25、输入齿轮26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联接行星架24,联接行星架24再传递到输入小齿圈28,输入小齿圈28、输入大齿圈29再通过输出行星架27上的行星齿轮20把传递到此的功率汇流于输出行星架27。
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，当输入齿圈25、输入大齿圈29的转速为零时，输入齿轮26、输入小齿圈28则降速增矩，当输入齿圈25、输入大齿圈29的转速不断升高时，联接行星架24、输出行星架27的转速也随之升高，也就是说，当输入齿圈25、输入大齿圈29的转速发生变化时，联接行星架24、输出行星架27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，一路经输入小齿轮22，再通过固定行星架21上的行星齿轮20把功率传递到输出大齿轮23，输出大齿轮23再传递到导叶可调式液力变矩器6，再经输入齿轮4，传递到输入大齿圈29以及输入齿圈25；另一路经输出齿轮副7传递到输入齿轮26，输入齿圈25、输入齿轮26再通过联接行星架24上的行星齿轮20把传递到此的功率汇流于联接行星架24，再传递到输入小齿圈28，输入小齿圈28、输入大齿圈29再通过输出行星架27上的行星齿轮20把传递到此的功率汇流于输出行星架27,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24、输出行星架27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24、输出行星架27以及输出轴3上的扭矩就越大，反之，则越小，在此过程中，导叶可调式液力变矩器6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导叶可调式液力变矩器。
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以及输出齿轮副7，传递到输入齿轮26，其中，由于此时没有功率或比较少的功率流入输入齿圈25、输入大齿圈29，并且超越离合器5的输入端51与固定元件联接,起限制转向的作用，输入齿圈25、输入大齿圈29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26 的功率，则通过联接行星架24上的行星齿轮20把功率传递到联接行星架24，联接行星架24再传递到输入小齿圈28，输入小齿圈28再通过输出行星架27上的行星齿轮20把功率传递到输出行星架27，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，导叶可调式液力变矩器6的输出端62的转速也逐渐增加，与之相联的输入齿圈25、输入大齿圈29的转速也随之逐渐增加，从而使联接行星架24、输出行星架27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，一种复合型导叶可调式液力变矩器的无级变速器，包括输入轴1、输出轴3、联接输出齿轮副4、联接输入齿轮副5、超越离合器6、导叶可调式液力变矩器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、固定行星架21、输入齿轮22、输出齿圈23、输入齿圈24、输入大齿轮25、输出行星架26、联接小齿轮27、联接行星架28、联接大齿轮29、输入行星架30、输入小齿圈31、输出大齿圈32,固定行星架21通过其上的行星齿轮20与输入齿轮22、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,输入齿轮22与联接输入齿轮副5的输出齿轮52联接,联接输入齿轮副5的输入齿轮51、输出齿轮副8的输入齿轮81以及输入小齿圈31与输入轴1联接,输出齿轮副8的输出齿轮82与导叶可调式液力变矩器7的输入端71联接,导叶可调式液力变矩器7的输出端72与输入大齿轮25、联接大齿轮29以及超越离合器6的输出端62联接,输出齿圈23与输入齿圈24联接,输入齿圈24通过输出行星架26上的行星齿轮20与输入大齿轮25、输出行星架26配合工作，输出行星架26与联接小齿轮27联接,联接小齿轮27通过联接行星架28上的行星齿轮20与联接行星架28、联接大齿轮29配合工作，联接行星架28与联接输出齿轮副4的输入齿轮41与联接,联接输出齿轮副4的输出齿轮42与输入行星架30联接,输入行星架30通过其上的行星齿轮20与输入小齿圈31、输出大齿圈32配合工作，输出大齿圈32与输出轴3联接。
输入齿圈24、输入大齿轮25通过输出行星架26上的行星齿轮20把传递到此的功率汇流于输出行星架26,输出行星架26再传递到联接小齿轮27,联接小齿轮27、联接大齿轮29通过联接行星架28上的行星齿轮20把传递到此的功率汇流于联接行星架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，当输入大齿轮25、联接大齿轮29的转速为零时，输入齿圈24、联接小齿轮27则降速增矩，当输入大齿轮25、联接大齿轮29的转速不断升高时，输出行星架26、联接行星架28的转速也随之升高，也就是说，当输入大齿轮25、联接大齿轮29的转速发生变化时，输出行星架26、联接行星架28以及输出轴3的转速也随之变化。
输入功率经输入轴1把功率分流为三路，第一路经输出齿轮副8以及导叶可调式液力变矩器7，传递到输入大齿轮25以及联接大齿轮29；第二路经联接输入齿轮副5传递到输入齿轮22，输入齿轮22再通过固定行星架21上的行星齿轮20把功率传递到输出齿圈23，再传递到输入齿圈24,输入齿圈24、输入大齿轮25通过输出行星架26上的行星齿轮20把传递到此的功率汇流于输出行星架26,输出行星架26再传递到联接小齿轮27,联接小齿轮27、联接大齿轮29通过联接行星架28上的行星齿轮20把传递到此的功率汇流于联接行星架28,联接行星架28再通过联接输出齿轮副4，传递到输入行星架30；第三路传 递到输入小齿圈31，输入行星架30、输入小齿圈31再通过输入行星架30上的行星齿轮20把传递到此的功率汇流于输出大齿圈32，输出大齿圈32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，输出行星架26、联接行星架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，传递到输出行星架26、联接行星架28以及输出轴3上的扭矩就越大，反之，则越小，在此过程中，导叶可调式液力变矩器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导叶可调式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以及联接输入齿轮副5，传递到输入齿轮22，再通过固定行星架21上的行星齿轮20把功率传递到输出齿圈23，输出齿圈23再传递到输入齿圈24,其中，由于此时没有或比较少的功率流入输入大齿轮25、联接大齿轮29，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，使输入大齿轮25、联接大齿轮29的转向不能与输入的转向相反，转速为零，此时，传递到输入齿圈24的功率，则通过输出行星架26上的行星齿轮20把传递到此的功率汇流于输出行星架26,输出行星架26再传递到联接小齿轮27,联接小齿轮27则通过联接行星架28上的行星齿轮20把传递到此的功率汇流于联接行星架28,联接行星架28再通过联接输出齿轮副4，传递到输入行星架30,输入行星架30、输入小齿圈31再通过输入行星架30的行星齿轮20把传递到此的功率汇流于输出大齿圈32，输出大齿圈32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，导叶可调式液力变矩器7输出端72的转速也逐渐增加，与之相联的输入大齿轮25、联接大齿轮29的转速也随之逐渐增加，从而使输出行星架26、联接行星架28以及输出轴3的扭矩随着转速的增加而减少。

Claims (2)

  1. 一种复合型导叶可调式液力变矩器，包括输入轴(1)、输出轴(3)、输入齿轮(4)、超越离合器(5)、导叶可调式液力变矩器(6)、输出齿轮副(7)，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)、输入小齿轮(22)、输出大齿轮(23)、联接行星架(24)、输入齿圈(25)、输入齿轮(26)、输出行星架(27)、输入小齿圈(28)、输入大齿圈(29),输入小齿轮(22)以及输出齿轮副(7)的输入齿轮(71)与输入轴(1)联接,输入小齿轮(22)通过固定行星架(21)上的行星齿轮(20)与固定行星架(21)、输出大齿轮(23)配合工作，固定行星架(21)以及超越离合器(5)的输入端(51)与固定元件联接,输出大齿轮(23)与导叶可调式液力变矩器(6)的输入端(61)联接,导叶可调式液力变矩器(6)的输出端(62)与超越离合器(5)的输出端(52)以及输入齿轮(4)联接,输入齿轮(4)与输入大齿圈(29)联接,输入大齿圈(29)通过输出行星架(27)上的行星齿轮(20)与输出行星架(27)、输入小齿圈(28)配合工作，输出行星架(27)与输出轴(3)联接,输出齿轮副(7)的输出齿轮(72)与输入齿轮(26)联接,输入齿轮(26)通过联接行星架(24)上的行星齿轮(20)与联接行星架(24)、输入齿圈(25)配合工作，输入齿圈(25)与输入大齿圈(29)联接,联接行星架(24)与输入小齿圈(28)联接。
  2. 一种复合型导叶可调式液力变矩器的无级变速器，包括输入轴(1)、输出轴(3)、联接输出齿轮副(4)、联接输入齿轮副(5)、超越离合器(6)、导叶可调式液力变矩器(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)、固定行星架(21)、输入齿轮(22)、输出齿圈(23)、输入齿圈(24)、输入大齿轮(25)、输出行星架(26)、联接小齿轮(27)、联接行星架(28)、联接大齿轮(29)、输入行星架(30)、输入小齿圈(31)、输出大齿圈(32),固定行星架(21)通过其上的行星齿轮(20)与输入齿轮(22)、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,输入齿轮(22)与联接输入齿轮副(5)的输出齿轮(52)联接,联接输入齿轮副(5)的输入齿轮(51)、输出齿轮副(8)的输入齿轮(81)以及输入小齿圈(31)与输入轴(1)联接,输出齿轮副(8)的输出齿轮(82)与导叶可调式液力变矩器(7)的输入端(71)联接,导叶可调式液力变矩器(7)的输出端(72)与输入大齿轮(25)、联接大齿轮(29)以及超越离合器(6)的输出端(62)联接,输出齿圈(23)与输入齿圈(24)联接,输入齿圈(24)通过输出行星架(26)上的行星齿轮(20)与输入大齿轮(25)、输出行星架(26)配合工作，输出行星架(26)与联接小齿轮(27)联接,联接小齿轮(27)通过联接行星架(28)上的行星齿轮(20)与联接行星架(28)、联接大齿轮(29)配合工作，联接行星架(28)与联接输出齿轮副(4)的输入齿轮(41)与联接,联接输出齿轮副(4)的输出齿轮(42)与输入行星架(30)联接,输入行星架(30)通过其上的行星齿轮(20)与输入小齿圈(31)、输出大齿圈(32)配合工作，输出大齿圈(32)与输出轴(3)联接。
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