WO2016112800A1 - 一种复合型综合式液力变矩器以及无级变速器 - Google Patents

一种复合型综合式液力变矩器以及无级变速器 Download PDF

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Publication number
WO2016112800A1
WO2016112800A1 PCT/CN2016/070209 CN2016070209W WO2016112800A1 WO 2016112800 A1 WO2016112800 A1 WO 2016112800A1 CN 2016070209 W CN2016070209 W CN 2016070209W WO 2016112800 A1 WO2016112800 A1 WO 2016112800A1
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Prior art keywords
gear
input
output
carrier
coupled
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PCT/CN2016/070209
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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 CN201680004310.8A priority Critical patent/CN107250615A/zh
Publication of WO2016112800A1 publication Critical patent/WO2016112800A1/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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • 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 torque converters and shifting, and more particularly to a composite integrated 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 integrated hydraulic torque converter and a continuously variable transmission which prolong the service life of the engine, has a simple structure, convenient operation, low cost, energy saving and high efficiency.
  • a composite integrated integrated torque converter includes an input shaft (1), an output shaft (3), an integrated hydraulic torque converter (4), an overrunning clutch (5), an input gear (6), An input gear pair (7), a coupling input gear pair (8), an output gear pair (9), a planetary gear (20) and a fixed planet carrier are arranged between the input shaft (1) and the output shaft (3) 21), input pinion (22), output large ring gear (23), input gear (24), input planet carrier (25), output gear (26), output planet carrier (27), input pinion (22) And an input gear (91) of the output gear pair (9) 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), and the output
  • the large ring gear (23) cooperates, the fixed carrier (21) and the input end (51) of the overrunning clutch (5) are coupled with the fixed element, the output large ring gear (23) and the input carrier (25) and the input gear ( 6) Coupling, the input planet carrier (25) cooperates with the
  • a continuously variable transmission of a composite integrated torque converter comprising an input shaft (1), an output shaft (3), an integrated torque converter (4), an overrunning clutch (5), and an input input gear ( 6) an input gear (7), an input gear pair (8), an output gear (9), an output gear pair (10), and a planetary gear is arranged between the input shaft (1) and the output shaft (3) ( 20), fixed planet carrier (21), input ring gear (22), output ring gear (23), input pinion (24), coupled output planet carrier (25), input large gear (26), coupled planet carrier ( 27), the coupling ring gear (28), the coupling gear (29), the output planet carrier (30), the input small ring gear (31), the input large ring gear (32), and the input ring gear (22) through the fixed planet carrier ( 21)
  • the upper planetary gear (20) cooperates with the fixed carrier (21) and the output ring gear (23), and the output gear (9) is coupled with the output ring gear (23) and the input pinion (24), and the input pinion gear (24) Cooperating with the
  • 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 integrated 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 integrated integrated torque converter includes an input shaft 1, an output shaft 3, an integrated torque converter 4, an overrunning clutch 5, an input gear 6, and an input gear pair. 7.
  • the input gear pair 8 and the output gear pair 9 are connected, and the planetary gear 20, the fixed carrier 21, the input pinion 22, the output large ring gear 23, and the input gear 24 are disposed between the input shaft 1 and the output shaft 3.
  • the input carrier 25, the output gear 26, the output carrier 27, the input pinion 22 and the input gear 91 of the output gear pair 9 are coupled to the input shaft 1, and the input pinion 22 is fixed by the planetary gear 20 fixed on the carrier 21.
  • the carrier 21 and the output large ring gear 23 cooperate, and the input end 51 of the fixed carrier 21 and the overrunning clutch 5 are coupled to the fixed element, the output large ring gear 23 and the input carrier 25 are coupled to the input gear 6, and the input carrier 25 passes.
  • the planetary gear 20 thereon cooperates with the input gear 24 and the output gear 26, and the output gear 26 is coupled to the input gear 81 of the input input gear pair 8, and the output gear 82 of the input input gear 8 is coupled to the planetary gear on the output carrier 27.
  • the output 42 of the torque converter 4 is coupled, and the input 41 of the integrated torque converter 4 is coupled to the output gear 92 of the output gear pair 9.
  • the input gear 24 and the input carrier 25 pass the power transmitted thereto through the planetary gears 20 on the input carrier 25 to the output gear 26, and the output gear 26 is transmitted to the input gear 81 of the input input gear pair 8, and the input gear pair is coupled.
  • the output gear 82 of the input gear 82 of the input gear pair 8 and the output gear carrier 72 of the input gear pair 7 are again transmitted to the power output planet carrier 27 via the planetary gears 20 on the output carrier 27.
  • the two power flows will change according to the change of the rotational speed distribution between the two.
  • the rotational speed of the input gear 24 and the output gear 72 of the input gear pair 7 is zero, the input carrier 25.
  • the output gear 82 of the input input gear pair 8 is reduced in speed.
  • the rotational speeds of the output gear 26 and the output carrier 27 are also followed.
  • the rise that is, when the rotational speed of the input gear 24 and the output gear 72 of the input gear pair 7 changes, the rotational speeds of the output gear 26, the output carrier 27, and the output shaft 3 also change.
  • the input power is split into two paths through the input shaft 1, and the first path is transmitted to the integrated torque converter 4 via the output gear pair 9, and the integrated torque converter 4 is divided into two paths, one way to
  • the input gear 24 is passed through the input gear 71 of the input gear pair 7 to the output gear 72 of the input gear pair 7; the second path is passed through the input pinion 22, and the power is transmitted through the planetary gear 20 on the fixed carrier 21.
  • the output large ring gear 23 is transmitted to the input carrier 25 through the input gear 6, and the input gear 24 and the input carrier 25 are connected to the power transmitted thereto through the planetary gears 20 on the input carrier 25.
  • the output gear 26 is coupled to the output gear 82 of the input input gear pair 8 via the input gear 81 coupled to the input gear pair 8, the output gear 72 of the input gear pair 7, the output gear 82 of the input input gear pair 8, and the output planet
  • the planetary gears 20 on the frame 27 converge 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 integrated torque converter 4 when the rotational speed of the input shaft 1 is constant, the torque on the output gear 26, 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 output gear 26 and the output carrier 27 And the torque on the output shaft 3 is larger, and conversely, the smaller, in the process, the integrated torque converter 4 also acts as a torque converter, so that the present invention can be changed depending on the running resistance of the vehicle. Compound integrated torque converter with 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 Pass to lose
  • the pinion gear 22 is transmitted to the output large ring gear 23 through the planetary gear 20 on the fixed carrier 21, and the output large ring gear 23 is transmitted to the input carrier 25 through the input gear 6, wherein, since there is no Power or relatively little power flows into the input gear 24, the output gear 72 of the input gear pair 7, and the input end 51 of the overrunning clutch 5 is coupled to the fixed element to act as a limit steering to output the input gear 24 and the input gear pair 7.
  • the steering of the gear 72 cannot be reversed to the input steering, and the rotational speed is zero.
  • the power transmitted to the input carrier 25 is transmitted to the output gear 26 through the planetary gear 20 on the input carrier 25, and the output gear 26 is output.
  • the input gear 81 coupled to the input gear pair 8 is transmitted to the output gear 82 of the input input gear pair 8, and the output gear 82 of the input input gear pair 8 is coupled to the power convergence transmitted thereto via the planetary gear 20 on the output carrier 27.
  • the output carrier 27 is transmitted to the output shaft 3, and when the torque transmitted to the output shaft 3 is transmitted to the driving wheel through the transmission system, the traction force is sufficient to overcome the starting resistance of the vehicle.
  • the car starts and accelerates, and the rotational speed of the output end 42 of the integrated torque converter 4 also gradually increases, and the rotational speed of the input gear 24 and the output gear 72 of the input gear pair 7 are gradually increased.
  • the torque of the output gear 26, the output carrier 27, and the output shaft 3 is reduced as the number of revolutions increases.
  • Embodiment 2 is a diagrammatic representation of Embodiment 1:
  • a continuously variable transmission of a composite integrated torque converter includes an input shaft 1, an output shaft 3, an integrated torque converter 4, an overrunning clutch 5, and a coupling input gear 6,
  • the input gear 7, the input gear pair 8, the output gear 9, and the output gear pair 10 are provided with a planetary gear 20, a fixed carrier 21, an input ring gear 22, and an output ring gear 23 between the input shaft 1 and the output shaft 3.
  • Ring gear 28 works together,
  • the ring gear 28 is coupled to the input bull gear 26 and the coupling input gear 6, and the output shaft 52 of the coupling input gear 6 and the overrunning clutch 5 is coupled to the output end 42 of the integrated torque converter 4, and the input ring gear 22 and the integrated fluid
  • the input end 41 of the torque converter 4 is coupled to the output gear 102 of the output gear pair 10, the input gear 7 and the input gear 101 of the output gear pair 10 are coupled to the input shaft 1, and the input gears of the carrier 27 and the input gear pair 8 are coupled.
  • the output gear 82 of the input gear pair 8 is coupled with the input small ring gear 31, and the input small ring gear 31 cooperates with the output carrier 30 and the input large ring gear 32 through the planetary gear 20 on the output carrier 30, and the input is large.
  • the ring gear 32 is coupled to the input gear 7, and the coupled output carrier 30 is coupled to the output shaft 3.
  • the input pinion 24 and the input bull gear 26 converge the power transmitted thereto by the planetary gears 20 coupled to the output carrier 25 to the coupled output carrier 25, and the coupled output carrier 25 is coupled to the coupling gear 29 to couple the ring gear 28.
  • the coupling gear 29 converges the power transmitted thereto to the coupling carrier 27 by the planetary gears 20 coupled to the carrier 27.
  • the input power is split into two paths via the input shaft 1, and the first path is transmitted to the input large ring gear via the input gear 7. 32; the second path is split by the output gear pair 10 into two paths, one way is transmitted to the integrated torque converter 4, and then coupled to the input gear 6, transmitted to the coupling ring gear 28 and the input large gear 26, and the other pass
  • the input ring 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 pinion gear 24 through the output gear 9, the input pinion 24, and the input large gear 26
  • the power transmitted thereto is coupled to the coupled output carrier 25 by the planetary gears 20 coupled to the output carrier 25, coupled to the output carrier 25 and transmitted to the coupling gear 29, the coupling ring gear 28, and the coupling gear 29 through the coupling carrier 27.
  • the upper planetary gear 20 converges the power transmitted thereto to the coupled planet carrier 27, the coupled carrier 27 and then the input gear pair 8 is transmitted to the input small ring gear 31, the input small ring gear 31, the input large ring gear 32 through the output
  • the planetary gears 20 on the carrier 30 converge the power transmitted thereto to the output carrier 30, and the output carrier 30 is transmitted to the output shaft 3, thereby realizing the external output of the engine power through the output shaft 3.
  • the integrated torque converter 4 when the rotational speed of the input shaft 1 is constant, the torque on the coupled output carrier 25, the coupled planet carrier 27, 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 output carrier 25, The greater the torque on the connecting planet carrier 27 and the output shaft 3, on the contrary, the smaller, in the process, the integrated torque converter 4 also acts as a torque converter, thereby realizing the driving resistance of the present invention with the vehicle.
  • a continuously variable transmission of a composite integrated 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 Passing to the input ring gear 22, and then transmitting the power to the output ring gear 23 through the planetary gears 20 on the fixed planet carrier 21, and then to the input pinion gear 24 through the output gear 9, wherein there is no or less Power flows into the input bull gear 26, the coupling ring gear 28, and the input end 51 of the overrunning clutch 5 is coupled to the fixed element to limit the steering so that the steering of the input bull gear 26 and the coupling ring gear 28 cannot be reversed from the input steering.
  • the rotational speed is zero.
  • the power transmitted to the input pinion 24 is transferred to the coupled output carrier 25 by the planetary gear 20 coupled to the output carrier 25, and coupled to the output carrier 25 to be transmitted to Coupling gear 29, the coupling gear 29 converges the power transmitted thereto by the planetary gears 20 coupled to the carrier 27 to the coupled planet carrier 27, and the coupled carrier 27 is transmitted through the input gear pair 8

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Abstract

一种复合型综合式液力变矩器，其中，输入小齿轮（22）以及输出齿轮副（9）与输入轴（1）联接，输出大齿圈（23）以及输入行星架（25）与输入齿轮（6）联接，输出齿轮（26）与联接输入齿轮副（8）联接，输出行星架（27）与输出轴（3）联接，输入齿轮（24）、输入齿轮副（7）以及超越离合器（5）与综合式液力变矩器（4）联接，综合式液力变矩器（4）与输出齿轮副（9）联接。此外，还提供了一种复合型综合式液力变矩器的无级变速器。

Description

一种复合型综合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综合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，节能高效的复合型综合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：
一种复合型综合式综合式液力变矩器，包括输入轴(1)、输出轴(3)、综合式液力变矩器(4)、超越离合器(5)、输入齿轮(6)、输入齿轮副(7)、联接输入齿轮副(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)、输入小齿轮(22)、输出大齿圈(23)、输入齿轮(24)、输入行星架(25)、输出齿轮(26)、输出行星架(27),输入小齿轮(22)以及输出齿轮副(9)的输入齿轮(91)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)、输出大齿圈(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,输出大齿圈(23)以及输入行星架(25)与输入齿轮(6)联接,输入行星架(25)通过其上的行星齿轮(20)与输入齿轮(24)、输出齿轮(26)配合工作，输出齿轮(26)与联接输入齿轮副(8)的输入齿轮(81)联接,联接输入齿轮副(8)的输出齿轮(82)通过输出行星架(27)上的行星齿轮(20)与输出行星架(27)、输入齿轮副(7)的输出齿轮(72)配合工作，输出行星架(27)与输出轴(3)联接，输入齿轮(24)、输入齿轮副(7)的输入齿轮(71)以及超越离合器(5)的输出端(52)与综合式液力变矩器(4)的输出端(42)联接,综合式液力变矩器(4)的输入端(41)与输出齿轮副(9)的输出齿轮(92)联接。
一种复合型综合式液力变矩器的无级变速器，包括输入轴(1)、输出轴(3)、综合式液力变矩器(4)、超越离合器(5)、联接输入齿轮(6)、输入齿轮(7)、输入齿轮副(8)、输出齿轮(9)、输出齿轮副(10)，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)、输入小齿轮(24)、联接输出行星架(25)、输入大齿轮(26)、联接行星架(27)、联接齿圈(28)、联接齿轮(29)、输出行星架(30)、输入小齿圈(31)、输入大齿圈(32),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，输出齿轮(9)与输出齿圈(23)以及输入小齿轮(24)联接,输入小齿轮(24)通过联接输出行星架(25)上的行星齿轮(20)与联接输出行星架(25)、输入大齿轮(26)配合工作，联接输出行星架(25)与联接齿轮(29)联接,联接齿轮(29)通过联接行星架(27)上的行星齿轮(20)与联接行星架(27)、联接齿圈(28)配合工作， 联接齿圈(28)与输入大齿轮(26)以及联接输入齿轮(6)联接,联接输入齿轮(6)以及超越离合器(5)的输出端(52)与综合式液力变矩器(4)的输出端(42)联接,输入齿圈(22)以及综合式液力变矩器(4)的输入端(41)与输出齿轮副(10)的输出齿轮(102)联接，输入齿轮(7)以及输出齿轮副(10)的输入齿轮(101)与输入轴(1)联接,联接行星架(27)与输入齿轮副(8)的输入齿轮(81)联接,输入齿轮副(8)的输出齿轮(82)与输入小齿圈(31)联接,输入小齿圈(31)通过输出行星架(30)上的行星齿轮(20)与输出行星架(30)、输入大齿圈(32)配合工作，输入大齿圈(32)与输入齿轮(7),联接输出行星架(30)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综合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，一种复合型综合式综合式液力变矩器，包括输入轴1、输出轴3、综合式液力变矩器4、超越离合器5、输入齿轮6、输入齿轮副7、联接输入齿轮副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、输入小齿轮22、输出大齿圈23、输入齿轮24、输入行星架25、输出齿轮26、输出行星架27,输入小齿轮22以及输出齿轮副9的输入齿轮91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、输出大齿圈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,输出大齿圈23以及输入行星架25与输入齿轮6联接,输入行星架25通过其上的行星齿轮20与输入齿轮24、输出齿轮26配合工作，输出齿轮26与联接输入齿轮副8的输入齿轮81联接,联接输入齿轮副8的输出齿轮82通过输出行星架27上的行星齿轮20与输出行星架27、输入齿轮副7的输出齿轮72配合工作，输出行星架27与输出轴3联接，输入齿轮24、输入齿轮副7的输入齿轮71以及超越离合器5的输出端52与综合式液力变矩器4的输出端42联接,综合式液力变矩器4的输入端41与输出齿轮副9的输出齿轮92联接。
输入齿轮24、输入行星架25通过输入行星架25上的行星齿轮20把传递到此的功率汇流于输出齿轮26,输出齿轮26再传递到联接输入齿轮副8的输入齿轮81,联接输入齿轮副8的输出齿轮82、输入齿轮副7的输出齿轮72再通过输出行星架27上的行星齿轮20把传递到此的功率输出行星架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，当输入齿轮24、输入齿轮副7的输出齿轮72的转速为零时，输入行星架25、联接输入齿轮副8的输出齿轮82则降速增矩，当输入齿轮24、输入齿轮副7的输出齿轮72的转速不断升高时，输出齿轮26、输出行星架27的转速也随之升高，也就是说，当输入齿轮24、输入齿轮副7的输出齿轮72的转速发生变化时，输出齿轮26、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，第一路经输出齿轮副9，传递到综合式液力变矩器4，综合式液力变矩器4再分流为两路，一路传递到输入齿轮24，另一路经输入齿轮副7的输入齿轮71,传递到输入齿轮副7的输出齿轮72；第二路经输入小齿轮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圈23，输出大齿圈23通过输入齿轮6,传递到输入行星架25，输入齿轮24、输入行星架25通过输入行星架25上的行星齿轮20把传递到此的功率汇流于输出齿轮26，再经联接输入齿轮副8的输入齿轮81，传递到联接输入齿轮副8的输出齿轮82,输入齿轮副7的输出齿轮72、联接输入齿轮副8的输出齿轮82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，输出齿轮26、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，传递到输出齿轮26、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，综合式液力变矩器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综合式液力变矩器。
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，传递到输 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圈23，输出大齿圈23则通过输入齿轮6,传递到输入行星架25，其中，由于此时没有功率或比较少的功率流入输入齿轮24、输入齿轮副7的输出齿轮72，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，使输入齿轮24、输入齿轮副7的输出齿轮72的转向不能与输入的转向相反，转速为零，此时，传递到输入行星架25的功率，则通过输入行星架25上的行星齿轮20把功率传递到输出齿轮26，输出齿轮26再经联接输入齿轮副8的输入齿轮81，传递到联接输入齿轮副8的输出齿轮82,联接输入齿轮副8的输出齿轮82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,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，综合式液力变矩器4的输出端42的转速也逐渐增加，与之相联的输入齿轮24、输入齿轮副7的输出齿轮72的转速也随之逐渐增加，从而使输出齿轮26、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，一种复合型综合式液力变矩器的无级变速器，包括输入轴1、输出轴3、综合式液力变矩器4、超越离合器5、联接输入齿轮6、输入齿轮7、输入齿轮副8、输出齿轮9、输出齿轮副10，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、输入小齿轮24、联接输出行星架25、输入大齿轮26、联接行星架27、联接齿圈28、联接齿轮29、输出行星架30、输入小齿圈31、输入大齿圈32,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，输出齿轮9与输出齿圈23以及输入小齿轮24联接,输入小齿轮24通过联接输出行星架25上的行星齿轮20与联接输出行星架25、输入大齿轮26配合工作，联接输出行星架25与联接齿轮29联接,联接齿轮29通过联接行星架27上的行星齿轮20与联接行星架27、联接齿圈28配合工作，联接齿圈28与输入大齿轮26以及联接输入齿轮6联接,联接输入齿轮6以及超越离合器5的输出端52与综合式液力变矩器4的输出端42联接,输入齿圈22以及综合式液力变矩器4的输入端41与输出齿轮副10的输出齿轮102联接，输入齿轮7以及输出齿轮副10的输入齿轮101与输入轴1联接,联接行星架27与输入齿轮副8的输入齿轮81联接,输入齿轮副8的输出齿轮82与输入小齿圈31联接,输入小齿圈31通过输出行星架30上的行星齿轮20与输出行星架30、输入大齿圈32配合工作，输入大齿圈32与输入齿轮7,联接输出行星架30与输出轴3联接。
输入小齿轮24、输入大齿轮26通过联接输出行星架25上的行星齿轮20把传递到此的功率汇流于联接输出行星架25,联接输出行星架25再传递到联接齿轮29,联接齿圈28、联接齿轮29通过联接行星架27上的行星齿轮20把传递到此的功率汇流于联接行星架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，当输入大齿轮26、联接齿圈28的转速为零时，联接输入小齿轮24、联接齿轮29则降速增矩，当输入大齿轮26、联接齿圈28的转速不断升高时，联接输出行星架25、联接行星架27的转速也随之升高，也就是说，当输入大齿轮26、联接齿圈28的转速发生变化时，联接输出行星架25、联接行星架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，第一路经输入齿轮7传递到输入大齿圈 32；第二路经输出齿轮副10再分流为两路，一路传递到综合式液力变矩器4，再经联接输入齿轮6,传递到联接齿圈28以及输入大齿轮26，另一路传递到输入齿圈22，输入齿圈22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，再通过输出齿轮9传递到输入小齿轮24,输入小齿轮24、输入大齿轮26通过联接输出行星架25上的行星齿轮20把传递到此的功率汇流于联接输出行星架25,联接输出行星架25再传递到联接齿轮29,联接齿圈28、联接齿轮29通过联接行星架27上的行星齿轮20把传递到此的功率汇流于联接行星架27,联接行星架27再通过输入齿轮副8,传递到输入小齿圈31,输入小齿圈31、输入大齿圈32通过输出行星架30上的行星齿轮20把传递到此的功率汇流于输出行星架30，输出行星架30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，联接输出行星架25、联接行星架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，传递到联接输出行星架25、联接行星架27以及输出轴3上的扭矩就越大，反之，则越小，在此过程中，综合式液力变矩器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综合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，传递到输入齿圈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，再通过输出齿轮9传递到输入小齿轮24,其中，由于此时没有或比较少的功率流入输入大齿轮26、联接齿圈28，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，使输入大齿轮26、联接齿圈28的转向不能与输入的转向相反，转速为零，此时，传递到输入小齿轮24的功率，则通过联接输出行星架25上的行星齿轮20把传递到此的功率汇流于联接输出行星架25,联接输出行星架25再传递到联接齿轮29,联接齿轮29通过联接行星架27上的行星齿轮20把传递到此的功率汇流于联接行星架27,联接行星架27再通过输入齿轮副8传递到输入小齿圈31,输入小齿圈31、输入大齿圈32通过输出行星架30上的行星齿轮20把传递到此的功率汇流于输出行星架30，输出行星架30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，综合式液力变矩器4输出端42的转速也逐渐增加，与之相联的输入大齿轮26、联接齿圈28的转速也随之逐渐增加，从而使联接输出行星架25、联接行星架27以及输出轴3的扭矩随着转速的增加而减少。

Claims (2)

  1. 一种复合型综合式综合式液力变矩器，包括输入轴(1)、输出轴(3)、综合式液力变矩器(4)、超越离合器(5)、输入齿轮(6)、输入齿轮副(7)、联接输入齿轮副(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)、输入小齿轮(22)、输出大齿圈(23)、输入齿轮(24)、输入行星架(25)、输出齿轮(26)、输出行星架(27),输入小齿轮(22)以及输出齿轮副(9)的输入齿轮(91)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)、输出大齿圈(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,输出大齿圈(23)以及输入行星架(25)与输入齿轮(6)联接,输入行星架(25)通过其上的行星齿轮(20)与输入齿轮(24)、输出齿轮(26)配合工作，输出齿轮(26)与联接输入齿轮副(8)的输入齿轮(81)联接,联接输入齿轮副(8)的输出齿轮(82)通过输出行星架(27)上的行星齿轮(20)与输出行星架(27)、输入齿轮副(7)的输出齿轮(72)配合工作，输出行星架(27)与输出轴(3)联接，输入齿轮(24)、输入齿轮副(7)的输入齿轮(71)以及超越离合器(5)的输出端(52)与综合式液力变矩器(4)的输出端(42)联接,综合式液力变矩器(4)的输入端(41)与输出齿轮副(9)的输出齿轮(92)联接。
  2. 一种复合型综合式液力变矩器的无级变速器，包括输入轴(1)、输出轴(3)、综合式液力变矩器(4)、超越离合器(5)、联接输入齿轮(6)、输入齿轮(7)、输入齿轮副(8)、输出齿轮(9)、输出齿轮副(10)，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)、输入小齿轮(24)、联接输出行星架(25)、输入大齿轮(26)、联接行星架(27)、联接齿圈(28)、联接齿轮(29)、输出行星架(30)、输入小齿圈(31)、输入大齿圈(32),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，输出齿轮(9)与输出齿圈(23)以及输入小齿轮(24)联接,输入小齿轮(24)通过联接输出行星架(25)上的行星齿轮(20)与联接输出行星架(25)、输入大齿轮(26)配合工作，联接输出行星架(25)与联接齿轮(29)联接,联接齿轮(29)通过联接行星架(27)上的行星齿轮(20)与联接行星架(27)、联接齿圈(28)配合工作，联接齿圈(28)与输入大齿轮(26)以及联接输入齿轮(6)联接,联接输入齿轮(6)以及超越离合器(5)的输出端(52)与综合式液力变矩器(4)的输出端(42)联接,输入齿圈(22)以及综合式液力变矩器(4)的输入端(41)与输出齿轮副(10)的输出齿轮(102)联接，输入齿轮(7)以及输出齿轮副(10)的输入齿轮(101)与输入轴(1)联接,联接行星架(27)与输入齿轮副(8)的输入齿轮(81)联接,输入齿轮副(8)的输出齿轮(82)与输入小齿圈(31)联接,输入小齿圈(31)通过输出行星架(30)上的行星齿轮(20)与输出行星架(30)、输入大齿圈(32)配合工作，输入大齿圈(32)与输入齿轮(7),联接输出行星架(30)与输出轴(3)联接。
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