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WO2017005177A1 - 一种复合型箱体式液力偶合器以及起动器 - Google Patents

一种复合型箱体式液力偶合器以及起动器 Download PDF

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Publication number
WO2017005177A1
WO2017005177A1 PCT/CN2016/088741 CN2016088741W WO2017005177A1 WO 2017005177 A1 WO2017005177 A1 WO 2017005177A1 CN 2016088741 W CN2016088741 W CN 2016088741W WO 2017005177 A1 WO2017005177 A1 WO 2017005177A1
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Prior art keywords
gear
input
output
carrier
coupled
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PCT/CN2016/088741
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English (en)
French (fr)
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吴志强
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Individual
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Individual
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Priority to CN201680039168.0A priority Critical patent/CN108243617A/zh
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
    • F16H47/08—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion

Definitions

  • the present invention is in the field of fluid couplings and starting, and more particularly, it is a composite tank type fluid coupling and starter for various ground vehicles, ships, railway locomotives, and machine tools.
  • the fluid coupling is designed according to the principles of hydrostatics, etc. It can transmit little power and is not efficient; in addition, the cost is high.
  • the invention overcomes the deficiencies of the prior art, and provides a composite box type fluid coupling and a starter which prolong the service life of the engine, has a simple structure, is convenient to operate, has low cost, is energy-saving and high-efficiency.
  • a composite tank type fluid coupling and starter comprising an input shaft (1), an input gear (3), an input gear pair (4), an output shaft (5), an empty gear mechanism (6), a box Body fluid coupling (7), fixed one-way clutch (8), starter gear pair (9), overrunning clutch (10), starting gear pair (11), electromagnetic clutch (12), coupling shaft (13)
  • the input shaft (1) and the output shaft (5) are provided with a planetary gear (20), an input carrier (21), an input gear (22), an output large ring gear (23), and an input ring gear ( 24), fixed carrier (25), output ring gear (26), coupled input planet carrier (27), fixed gear (28), output gear (29), input shaft (1) and start gear pair (11)
  • the output gear (112) and the input end (101) of the overrunning clutch (10) are coupled, the output end (102) of the overrunning clutch (10) and the input gear (22) and the output gear (92) of the starter gear pair (9)
  • the output gear (92) of the starter gear pair (9) cooperates with the input gear (91) of the starter
  • the planetary gear (20) coupled to the input carrier (27) cooperates with the fixed gear (28) and the output gear (29) to fix the carrier (25), the fixed gear (28) and the fixed one-way clutch ( 8)
  • the input end (81) is coupled to the stationary element
  • the output gear (29) is coupled to the input end (71) of the tank-type fluid coupling (7)
  • the end (82) and the input planet carrier (21) is coupled.
  • a composite tank type fluid coupling comprising an input shaft (1), a one-way clutch (3), a tank type fluid coupling (4), an output shaft (5), an input gear pair (6), The output gear pair (7) and the output gear pair (8) are coupled, and a planetary gear (20), an input small ring gear (21), and an input large tooth are disposed between the input shaft (1) and the output shaft (5).
  • a ring 22
  • an output planet carrier 23
  • an output gear 24
  • a fixed planet carrier 25
  • an input gear 26
  • an input planet carrier 27
  • an input pinion 28
  • the output ring gear (29) is coupled to the input small ring gear (21) and the input gear (81) of the output gear pair (8), and the output gear (82) of the output gear pair (8) is small with the input.
  • the gear (28) is coupled, and the input small ring gear (21) cooperates with the input large ring gear (22) and the output planet carrier (23) through the planetary gear (20) on the output carrier (23), and outputs the planet carrier ( 23) coupled to the input gear (71) of the coupled output gear pair (7), coupled to the output gear (72) of the output gear pair (7) and the input gear (27) and the input gear of the input gear pair (6) (61)
  • the coupling gear (62) of the input gear pair (6) is coupled to the input gear (26), and the input gear (26) is fixed by the planetary gear (20) and the output gear (24) fixed on the carrier (25).
  • the planet carrier (25) cooperates with each other, the fixed carrier (25) and the input end (31) of the one-way clutch (3) are fixed to the fixed component, and the output gear (24) and the box type fluid coupling (4)
  • the input end (41) is coupled
  • the output end (42) of the tank type fluid coupling (4) is coupled with the output end (32) of the one-way clutch (3) and the input large ring gear (22), and the input carrier (27)
  • the planetary gear (20) and the input through it Wheel (28), an output ring gear (29) cooperate with each other, the output ring gear (29) and the output shaft (5) is coupled.
  • 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 tank type fluid coupling can be replaced by a double pump wheel hydraulic torque converter.
  • the air-locking mechanism can select a clutch instead.
  • the present invention When the present invention is applied to a vehicle, it is possible to automatically change the output torque and the speed change depending on the magnitude of the resistance that the vehicle is subjected to while traveling.
  • the invention enables the engine and the starter to operate in the region of the tempering speed, that is, the engine operates in a range of very small pollution discharge speeds, thereby avoiding the engine discharging a large amount of exhaust gas during idle speed and high speed operation, thereby reducing the number of exhaust gases.
  • the emission of exhaust gas is conducive to protecting the environment;
  • the invention can utilize the effect of internal speed difference to buffer and overload protection, which is beneficial to prolonging the service life of the engine and the drive train and the starter.
  • speed up which is beneficial to improve the driving performance of the vehicle;
  • the invention makes the input power uninterrupted, can ensure the vehicle has good acceleration and high average vehicle speed, reduces the wear of the engine, prolongs the overhaul interval mileage, and is beneficial to improving productivity;
  • the invention reduces the transmission mechanism of the current starter machine 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 type tank type fluid coupling and starter for various ground vehicles, ships, railway locomotives, and machine tools.
  • FIG. 1 is a structural view of a first embodiment of the present invention
  • FIG. 2 is a structural diagram of a second embodiment of the present invention.
  • connection between the two elements is indicated by a thick solid line, and the thin solid line indicates that the two elements can be rotated relative to each other.
  • Embodiment 1 is a diagrammatic representation of Embodiment 1:
  • a composite tank type fluid coupling and a starter include an input shaft 1, an input gear 3, an input gear pair 4, an output shaft 5, an idle gear mechanism 6, and a tank type liquid.
  • the output gear 112 of the start gear pair 11 and the input end 101 of the overrunning clutch 10 are coupled, and the output end 102 of the overrunning clutch 10 is coupled to the input gear 22 and the output gear 92 of the starter gear pair 9, the output gear 92 of the starter gear pair 9
  • the input gear 91 of the starter gear pair 9 cooperates with each other.
  • the input gear 22 cooperates with the input carrier 21 and the output large ring gear 23 through the planetary gear 20 on the input carrier 21, and outputs the large ring gear 23 and the input tooth.
  • Ring 24 meshes, coupling shaft 13 Coupling with the input ring gear 24, the input end 121 of the electromagnetic clutch 12, and the input gear 41 of the input gear pair 4, the output gear 42 of the input gear pair 4 is coupled to the input end 61 of the neutral gear mechanism 6, the idle gear mechanism 6
  • the output end 62 is coupled to the output shaft 5, and the output end 122 of the electromagnetic clutch 12 is coupled to the input gear 111 of the start gear pair 11.
  • the input ring gear 24 passes through the planetary gear 20 on the fixed carrier 25 and the fixed carrier 25, and the output ring gear.
  • the output ring gear 26 meshes with the input gear 3
  • the input gear 3 is coupled with the coupling input carrier 27, and the planetary gear 20 coupled to the input carrier 27 cooperates with the fixed gear 28 and the output gear 29 to cooperate with each other.
  • the fixed planet carrier 25, the fixed gear 28 and the input end 81 of the fixed one-way clutch 8 are coupled to a fixed element
  • the output gear 29 is coupled to the input 71 of the tank-type fluid coupling 7, the tank-type fluid coupling 7
  • the output end 72 and the output end 82 of the fixed one-way clutch 8 are coupled to the input carrier 21.
  • the idle gear mechanism 6 Before the engine is started, the idle gear mechanism 6 is disengaged and the electromagnetic clutch 12 is engaged.
  • the input power of the starter is transmitted to the input gear 22 via the starter gear pair 9, and the input gear 22 is transmitted to the output through the planetary gear 20 on the input carrier 21.
  • the ring gear 23, the output large ring gear 23 is transmitted to the input shaft 1 through the input ring gear 24, the coupling shaft 13, the electromagnetic clutch 12 and the start gear pair 11, and is transmitted to the crankshaft of the engine, and the generated driving force is sufficient to overcome the engine starting resistance.
  • the input gear 22 transmits the power transmitted from the engine to the input shaft 1 and the overrunning clutch 12 through the planetary gear 20 input to the carrier 21, and is transmitted to the output.
  • the ring gear 23, the output large ring gear 23 is transmitted to the input ring gear 24, and the input ring gear 24 diverts the power transmitted thereto into two paths, one pass through the coupling shaft 13, the input gear pair 4, and the idle gear mechanism 6 to The output shaft 5 of the present invention; the other path is transmitted to the output ring gear 26 through the planetary gear 20 on the fixed carrier 25, and the output ring gear 26 is transmitted to the coupled input carrier 27 through the input gear 3, coupled to the input carrier 27 and passed
  • the planetary gear 20 on it is transmitted to the transmission
  • the output gear 29, the output gear 29 is transmitted to the input carrier 21 through the tank type fluid coupling 7, the power transmitted to the input carrier 21, and the power transmitted from the engine to the input gear 22 via the input shaft 1 and the overrunning clutch 10,
  • the planetary gear 20 on the input carrier 21 is transmitted to the output large ring gear 23, and the large ring gear 23 is outputted, and the repeated cycle of the shifting is continuously performed between the respective components, wherein the output of the tank type fluid coupling 7 is output.
  • the rotational speed continuously shifts steplessly as the input power and the running resistance change, so that the output rotational speed of the output large ring gear 23 also constantly changes, and through the input ring gear 24, the coupling shaft 13, the input gear pair 4, and the air
  • the gear shifting mechanism 6 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 torque on the input carrier 21, the output large ring gear 23, and the output shaft 5 varies with the change of the rotational speed thereof, and the lower the rotational speed, the transmission to the input carrier 21 and the output.
  • the idle gear mechanism 6 is disengaged, the electromagnetic clutch 12 is engaged, and the engine speed is zero.
  • the starter is started, the input power of the starter is transmitted to the input gear 22 through the starter gear pair 9, wherein Since no power flows into the input carrier 21 at this time, and the input end 81 of the fixed one-way clutch 8 is coupled to the fixed component, the steering is restricted, so that the input carrier 21 cannot rotate opposite to the engine, and the rotational speed is zero.
  • the power transmitted to the input gear 22 is transmitted to the output large ring gear 23 through the planetary gear 20 input to the carrier 21, and the large ring gear 23 is output through the input ring gear 24, the coupling shaft 13, and the electromagnetic clutch. 12 and the starter gear pair 11 is transmitted to the input shaft 1 and then to the engine crankshaft.
  • 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 12 is separated, and the output shaft 5 is rotated.
  • the input power of the engine is transmitted to the input gear 22 via the input shaft 1 and the overrunning clutch 10, wherein since no power flows into the input carrier 21 at this time, and the input end 81 of the fixed one-way clutch 8 is coupled to the fixed member,
  • the function of restricting the steering is such that the input carrier 21 cannot rotate opposite to the engine, and the rotational speed is zero.
  • the power transmitted to the input gear 22 is transmitted to the output through the planetary gear 20 input to the carrier 21.
  • the large ring gear 23, the output large ring gear 23 is transmitted to the input ring gear 24, and the input ring gear 24 diverts the power transmitted thereto into two paths, one pass through the coupling shaft 13, the input gear pair 4, and the idle gear mechanism 6.
  • the other path is transmitted to the output ring gear 26 through the planetary gear 20 on the fixed carrier 25, and the output ring gear 26 is transmitted to the joint through the input gear 3.
  • the input carrier 27 is coupled to the input carrier 27 and transmitted to the output gear 29 through the planetary gear 20 thereon.
  • the output gear 29 is transmitted to the input carrier 21 through the tank type fluid coupling 7 and transmitted to the input carrier 21.
  • the power and the power transmitted from the engine through the input shaft 1 and the overrunning clutch 10 to the input gear 22 are transmitted to the output large ring gear 23 through the planetary gear 20 on the input carrier 21, and the large ring gear 23 is output between the respective components.
  • the repeated cycle of the shifting is continuously performed, wherein the output rotational speed of the tank type fluid coupling 7 is continuously steplessly changed in accordance with the change in the running resistance, so that the output rotational speed of the output large ring gear 23 is also constantly changed.
  • the input ring gear 24, the coupling shaft 13, the input gear pair 4, and the idle gear mechanism 6 are transmitted to the output shaft 5 of the present invention, so that the torque of the output shaft 5 is reduced as the number of revolutions increases.
  • Embodiment 2 is a diagrammatic representation of Embodiment 1:
  • a composite tank type fluid coupling includes an input shaft 1, a one-way clutch 3, a tank type fluid coupling 4, an output shaft 5, an input gear pair 6, and a coupling output gear.
  • Sub 7 , output gear pair 8, the input shaft 1 and the input A planetary gear 20, an input small ring gear 21, an input large ring gear 22, an output carrier 23, an output gear 24, a fixed carrier 25, an input gear 26, an input carrier 27, and an input pinion 28 are disposed between the output shafts 5.
  • the output ring gear 29 is coupled to the input small gear ring 21 and the input gear 81 of the output gear pair 8.
  • the output gear 82 of the output gear pair 8 is coupled to the input pinion 28, and the input small ring gear 21 is passed through the output carrier.
  • the planetary gear 20 on the 23 cooperates with the input large ring gear 22 and the output carrier 23, the output carrier 23 is coupled with the input gear 71 of the coupled output gear pair 7, and the output gear 72 of the output gear pair 7 is coupled to the input carrier. 27 and the input gear 61 of the input gear pair 6 are coupled, the output gear 62 of the input gear pair 6 is coupled to the input gear 26, and the input gear 26 is matched with the output gear 24 and the fixed carrier 25 by the planetary gear 20 on the fixed carrier 25.
  • the fixed carrier 25 and the input end 31 of the one-way clutch 3 are fixed to the fixed element, and the output gear 24 is coupled to the input 41 of the tank type fluid coupling 4, the output of the tank type fluid coupling 4 42 and one-way clutch Output 3 and an input terminal 32 coupled to the ring gear 22, input planet carrier 27 through the planetary gear 20 on the input pinion 28, output gear 29 cooperate with each other, the output gear 29 and the output shaft 5 is coupled.
  • the input small ring gear 21 and the input large ring gear 22 converge the respective power transmitted through the planetary gears 20 on the output carrier 23 to the output carrier 23, since the box type fluid coupling 4 is coupled to the input large ring gear 22. Therefore, the rotational speed of the input large ring gear 22 can be constantly changed in accordance with the change in the rotational speed of the tank type fluid coupling 4, so that the rotational speed of the output carrier 23 also changes.
  • the input power is split into two paths through the input shaft 1, one is transmitted to the input small ring gear 21, the other is transmitted to the input pinion 28 via the output gear pair 8, and the input small ring gear 21 passes the power transmitted thereto through the output carrier 23.
  • the upper planetary gear 20 merges with the output carrier 23, and the output carrier 23 is split into two paths by coupling the output gear pair 7, and is transmitted to the input carrier 27 at one time. At this time, the input carrier 27 and the input pinion 28 transmit The respective powers are converge to the output ring gear 29 through the planetary gears 20 on the input carrier 27, and the output ring gear 29 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 power of the other path transmitted to the input gear 26 through the input gear pair 6 increases, and the input gear 26 passes through the planetary gear 20 on the fixed carrier 25.
  • the power is transmitted to the output gear 24, and the output gear 24 is transmitted to the input large ring gear 22 through the tank type fluid coupling 4, that is, the input power of the input large ring gear 22 is increased, and the small ring gear 21 is input.
  • the input large ring gear 22 converges the planetary gears 20 transmitted to the respective powers through the output carrier 23 to the output carrier 23, and the output carrier 23 repeats the above process to continuously change the rotational speed transmitted to the input carrier 27.
  • the input carrier 27 and the input pinion 28 converge the planetary gear 20 transmitted to the respective power through the input carrier 27 to the output ring gear 29, and the output ring gear 29 is transmitted to the output shaft 5 of the present invention, thereby realizing The power of the engine is externally output through the output shaft 5.
  • the rotational speed input to the carrier 27 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 carrier 27.
  • 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
  • the split is two paths, one is transmitted to the input small ring gear 21, the other is transmitted to the input pinion 28 via the output gear pair 8, and the input small ring gear 21 converges the power transmitted thereto through the planetary gears 20 on the output carrier 23.
  • the output planet carrier 23 is split into two paths by coupling the output gear pair 7, one way to the input planet carrier 27, at this time, the input planet carrier 27 and the input pinion 28 merge the planetary gear 20 transmitted to the respective power through the input carrier 27 to the output ring gear 29, and the output ring gear 29 is transmitted to the output shaft 5 of the present invention, thereby realizing the power of the engine. It is output to the outside through the output shaft 5.
  • the vehicle starts to accelerate.
  • the resistance of the output shaft 5 decreases, the other passes through the input gear.
  • the power delivered by the secondary 6 to the input gear 26 is increased, the input gear 26 transmits power to the output gear 24 via the planet gears 20 on the fixed planet carrier 25, and the output gear 24 passes through the tank-type fluid coupling 4
  • the input power to the input large ring gear 22, i.e., the input large ring gear 22, increases, and the input small ring gear 21, the input large ring gear 22, transmits the respective power through the planetary gear 20 on the output carrier 23.
  • the output carrier 23 repeats the above process, so that the rotational speed transmitted to the input carrier 27 is constantly changing, and the input carrier 27 and the input pinion 28 transmit the respective powers through the input carrier 27.
  • the planetary gear 20 merges with the output ring gear 29, and the output ring gear 29 is transmitted to the output shaft 5 of the present invention.

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Abstract

一种复合型箱体式液力偶合器及具有该箱体式液力偶合器的起动器，其中输入轴（1）与起动齿轮副（11）以及超越离合器（10）联接，超越离合器（10）与输入齿轮（22）以及起动机齿轮副（9）联接，输出大齿圈（23）与输入齿圈（24）啮合，联接轴（13）与输入齿圈（24）、电磁离合器（12）以及输入齿轮副（4）联接，输入齿轮副（4）与空挂档机构（6）联接，空挂档机构（6）与输出轴（5）联接，电磁离合器（12）与起动齿轮副（11）联接，输出齿圈（26）与输入齿轮（3）啮合，输入齿轮（3）与联接输入行星架（27）联接，输出齿轮（29）与箱体式液力偶合器（7）联接，箱体式液力偶合器（7）以及固定单向离合器（8）与输入行星架（21）联接。

Description

一种复合型箱体式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箱体式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，节能高效的复合型箱体式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：
一种复合型箱体式液力偶合器以及起动器，包括输入轴(1)、输入齿轮(3)、输入齿轮副(4)、输出轴(5)、空挂档机构(6)、箱体式液力偶合器(7)、固定单向离合器(8)、起动机齿轮副(9)、超越离合器(10)、起动齿轮副(11)、电磁离合器(12)、联接轴(13)，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)、输入齿轮(22)、输出大齿圈(23)、输入齿圈(24)、固定行星架(25)、输出齿圈(26)、联接输入行星架(27)、固定齿轮(28)、输出齿轮(29),输入轴(1)与起动齿轮副(11)的输出齿轮(112)以及超越离合器(10)的输入端(101)联接,超越离合器(10)的输出端(102)与输入齿轮(22)以及起动机齿轮副(9)的输出齿轮(92)联接,起动机齿轮副(9)的输出齿轮(92)与起动机齿轮副(9)的输入齿轮(91)相互配合工作，输入齿轮(22)通过输入行星架(21)上的行星齿轮(20)与输入行星架(21)、输出大齿圈(23)相互配合工作，输出大齿圈(23)与输入齿圈(24)啮合，联接轴(13)与输入齿圈(24)、电磁离合器(12)的输入端(121)以及输入齿轮副(4)的输入齿轮(41)联接，输入齿轮副(4)的输出齿轮(42)与空挂档机构(6)的输入端(61)联接，空挂档机构(6)的输出端(62)与输出轴(5)联接，电磁离合器(12)的输出端(122)与起动齿轮副(11)的输入齿轮(111)联接，输入齿圈(24)通过固定行星架(25)上的行星齿轮(20)与固定行星架(25)、输出齿圈(26)相互配合工作，输出齿圈(26)与输入齿轮(3)啮合，输入齿轮(3)与联接输入行星架(27)联接，联接输入行星架(27)通过其上的行星齿轮(20)与固定齿轮(28)、输出齿轮(29)相互配合工作，固定行星架(25)、固定齿轮(28)以及固定单向离合器(8)的输入端(81)与固定元件联接，输出齿轮(29)与箱体式液力偶合器(7)的输入端(71)联接,箱体式液力偶合器(7)的输出端(72)以及固定单向离合器(8)的输出端(82)与输入行星架(21)联接。
一种复合型箱体式液力偶合器，包括输入轴(1)、单向离合器(3)、箱体式液力偶合器(4)、输出轴(5)、输入齿轮副(6)、联接输出齿轮副(7)、输出齿轮副(8)，所述的输入轴(1)与输出轴(5)之间设有行星齿轮(20)、输入小齿圈(21)、输入大齿圈(22)、输出行星架(23)、输出齿轮(24)、固定行星架(25)、输入齿轮(26)、输入行星架(27)、输入小齿轮(28)、 输出齿圈(29)，输入轴(1)与输入小齿圈(21)以及输出齿轮副(8)的输入齿轮(81)联接,输出齿轮副(8)的输出齿轮(82)与输入小齿轮(28)联接,输入小齿圈(21)通过输出行星架(23)上的行星齿轮(20)与输入大齿圈(22)、输出行星架(23)相互配合工作，输出行星架(23)与联接输出齿轮副(7)的输入齿轮(71)联接,联接输出齿轮副(7)的输出齿轮(72)与输入行星架(27)以及输入齿轮副(6)的输入齿轮(61)联接,输入齿轮副(6)的输出齿轮(62)与输入齿轮(26)联接,输入齿轮(26)通过固定行星架(25)上的行星齿轮(20)与输出齿轮(24)、固定行星架(25)相互配合工作，固定行星架(25)以及单向离合器(3)的输入端(31)与固定元件固接,输出齿轮(24)与箱体式液力偶合器(4)的输入端(41)联接,箱体式液力偶合器(4)的输出端(42)与单向离合器(3)的输出端(32)以及输入大齿圈(22)联接,输入行星架(27)通过其上的行星齿轮(20)与输入小齿轮(28)、输出齿圈(29)相互配合工作，输出齿圈(29)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。
所述箱体式液力偶合器可以选择双泵轮液力变矩器代替。
所述空挂档机构可以选择离合器代替。
本发明应用于车辆时，能够根据车辆行驶时受到阻力的大小，自动地改变输出扭矩以及速度的变化。
本发明具有以下的优点：
(1)本发明大部份功率由齿圈、行星齿轮、行星架、齿轮传递，因而传动功率和传动效率都极大地提高,而且结构简单，更易于维修；
(2)本发明的变矩和变速是自动完成的，能实现高效率的传动，并且除了起步以外，都能使发动机和起动机在最佳范围内工作，与其它变速器相比，在发动机和起动机等效的前提下，它降低了发动机和起动机的制造成本；
(3)本发明使发动机和起动机处于经过济转速区域内运转，也就是使发动机在非常小污染排放的转速范围内工作，避免了发动机在怠速和高速运行时，排放大量废气，从而减少了废气的排放，有利于保护环境；
(4)本发明能利用内部转速差起缓冲和过载保护的作用，有利于延长发动机和传动系以及起动机的使用寿命，另外，当行驶阻力增大，则能使车辆自动降速，反之则升速，有利于提高车辆的行驶性能；
(5)本发明使输入功率不间断，可保证车辆有良好的加速性和较高的平均车速，使发动机的磨损减少，延长了大修间隔里程，有利于提高生产率；
(6)本发明起动时，具有自动变矩和变速的性能，输入功率不间断，不会发生冲击现象，可保证发动机起动平稳、减少噪音，使发动机的起动磨损减少，并延长了起动电机以及蓄电池的使用寿命；
(7)本发明减少了现今起动机的传动机构，降低了制造成本，发动机起动后，只需对起动电机采取制动以及分离的措施，使其停止传动。
另外，本发明是是一种用于各种地面车辆、船舶、铁道机车以及机床的复合型箱体式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，一种复合型箱体式液力偶合器以及起动器，包括输入轴1、输入齿轮3、输入齿轮副4、输出轴5、空挂档机构6、箱体式液力偶合器7、固定单向离合器8、起动机齿轮副9、超越离合器10、起动齿轮副11、电磁离合器12、联接轴13，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、输入齿轮22、输出大齿圈23、输入齿圈24、固定行星架25、输出齿圈26、联接输入行星架27、固定齿轮28、输出齿轮29,输入轴1与起动齿轮副11的输出齿轮112以及超越离合器10的输入端101联接,超越离合器10的输出端102与输入齿轮22以及起动机齿轮副9的输出齿轮92联接,起动机齿轮副9的输出齿轮92与起动机齿轮副9的输入齿轮91相互配合工作，输入齿轮22通过输入行星架21上的行星齿轮20与输入行星架21、输出大齿圈23相互配合工作，输出大齿圈23与输入齿圈24啮合，联接轴13与输入齿圈24、电磁离合器12的输入端121以及输入齿轮副4的输入齿轮41联接，输入齿轮副4的输出齿轮42与空挂档机构6的输入端61联接，空挂档机构6的输出端62与输出轴5联接，电磁离合器12的输出端122与起动齿轮副11的输入齿轮111联接，输入齿圈24通过固定行星架25上的行星齿轮20与固定行星架25、输出齿圈26相互配合工作，输出齿圈26与输入齿轮3啮合，输入齿轮3与联接输入行星架27联接，联接输入行星架27通过其上的行星齿轮20与固定齿轮28、输出齿轮29相互配合工作，固定行星架25、固定齿轮28以及固定单向离合器8的输入端81与固定元件联接，输出齿轮29与箱体式液力偶合器7的输入端71联接,箱体式液力偶合器7的输出端72以及固定单向离合器8的输出端82与输入行星架21联接。
发动机起动前，分离空挂档机构6，接合电磁离合器12，起动机的输入功率经过起动机齿轮副9传递到输入齿轮22，输入齿轮22通过输入行星架21上的行星齿轮20传递到输出大齿圈23，输出大齿圈23再通过输入齿圈24、联接轴13、电磁离合器12以及起动齿轮副11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12，输入齿轮22通过输入行星架21上的行星齿轮20把由发动机经过输入轴1以及超越离合器12传递到此的功率，传递到输出大齿圈23，输出大齿圈23再传递到输入齿圈24，输入齿圈24把传递到此的功率分流为两路，一路经过联接轴13、输入齿轮副4以及空挂档机构6传递到本发明的输出轴5；另一路通过固定行星架25上的行星齿轮20传递到输出齿圈26，输出齿圈26再通过输入齿轮3传递到联接输入行星架27，联接输入行星架27再通过其上的行星齿轮20传递到输 出齿轮29，输出齿轮29通过箱体式液力偶合器7传递到输入行星架21，传递到输入行星架21的功率以及由发动机经过输入轴1以及超越离合器10传递到输入齿轮22的功率，则通过输入行星架21上的行星齿轮20传递到输出大齿圈23，输出大齿圈23再在各个元件之间不断地进行变速的反复循环，其中，箱体式液力偶合器7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，从而使输出大齿圈23的输出转速也不断地变化，并且通过输入齿圈24、联接轴13、输入齿轮副4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、输出大齿圈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、输出大齿圈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箱体式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12，发动机的转速为零，当起动机启动，起动机的输入功率经过起动机齿轮副9传递到输入齿轮22,其中，由于此时没有功率流入输入行星架21，并且固定单向离合器8的输入端81与固定元件联接，起限制转向的作用，使输入行星架21不能与发动机相反的转向转动，转速为零，此时，传递到输入齿轮22的功率，则通过输入行星架21上的行星齿轮20把功率传递到输出大齿圈23，输出大齿圈23再通过输入齿圈24、联接轴13、电磁离合器12以及起动齿轮副11传递到输入轴1，再传递到发动机曲轴上，当传递到发动机的曲轴上的扭矩，产生的起动力足以克服发动机的起动阻力时，发动机则起动并开始加速。
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12，输出轴5的转速为零，发动机的输入功率经过输入轴1以及超越离合器10，传递到输入齿轮22，其中，由于此时没有功率流入输入行星架21，并且固定单向离合器8的输入端81与固定元件联接，起限制转向的作用，使输入行星架21不能与发动机相反的转向转动，转速为零，此时，传递到输入齿轮22的功率，则通过输入行星架21上的行星齿轮20把功率传递到输出大齿圈23，输出大齿圈23再传递到输入齿圈24，输入齿圈24把传递到此的功率分流为两路，一路经过联接轴13、输入齿轮副4以及空挂档机构6传递到本发明的输出轴5；另一路通过固定行星架25上的行星齿轮20传递到输出齿圈26，输出齿圈26再通过输入齿轮3传递到联接输入行星架27，联接输入行星架27再通过其上的行星齿轮20传递到输出齿轮29，输出齿轮29通过箱体式液力偶合器7传递到输入行星架21，传递到输入行星架21的功率以及由发动机经过输入轴1以及超越离合器10传递到输入齿轮22的功率，则通过输入行星架21上的行星齿轮20传递到输出大齿圈23，输出大齿圈23再在各个元件之间不断地进行变速的反复循环，其中，箱体式液力偶合器7的输出转速不断地随着行驶阻力的变化而无级地变速，从而使输出大齿圈23的输出转速也不断地变化，并且通过输入齿圈24、联接轴13、输入齿轮副4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，一种复合型箱体式液力偶合器，包括输入轴1、单向离合器3、箱体式液力偶合器4、输出轴5、输入齿轮副6、联接输出齿轮副7、输出齿轮副8，所述的输入轴1与输 出轴5之间设有行星齿轮20、输入小齿圈21、输入大齿圈22、输出行星架23、输出齿轮24、固定行星架25、输入齿轮26、输入行星架27、输入小齿轮28、输出齿圈29，输入轴1与输入小齿圈21以及输出齿轮副8的输入齿轮81联接,输出齿轮副8的输出齿轮82与输入小齿轮28联接,输入小齿圈21通过输出行星架23上的行星齿轮20与输入大齿圈22、输出行星架23相互配合工作，输出行星架23与联接输出齿轮副7的输入齿轮71联接,联接输出齿轮副7的输出齿轮72与输入行星架27以及输入齿轮副6的输入齿轮61联接,输入齿轮副6的输出齿轮62与输入齿轮26联接,输入齿轮26通过固定行星架25上的行星齿轮20与输出齿轮24、固定行星架25相互配合工作，固定行星架25以及单向离合器3的输入端31与固定元件固接,输出齿轮24与箱体式液力偶合器4的输入端41联接,箱体式液力偶合器4的输出端42与单向离合器3的输出端32以及输入大齿圈22联接,输入行星架27通过其上的行星齿轮20与输入小齿轮28、输出齿圈29相互配合工作，输出齿圈29与输出轴5联接。
输入小齿圈21、输入大齿圈22把传递到各自的功率通过输出行星架23上的行星齿轮20汇流于输出行星架23，由于箱体式液力偶合器4与输入大齿圈22联接,所以输入大齿圈22的转速可以不断地随着箱体式液力偶合器4转速的变化而变化,从而使输出行星架23的转速也随之变化。
输入功率经过输入轴1分流为两路，一路传递到输入小齿圈21，另一路经过输出齿轮副8传递到输入小齿轮28，输入小齿圈21把传递到此的功率通过输出行星架23上的行星齿轮20汇流于输出行星架23，输出行星架23通过联接输出齿轮副7再分流为两路，一路传递到输入行星架27，此时，输入行星架27与输入小齿轮28把传递到各自的功率通过输入行星架27上的行星齿轮20汇流于输出齿圈29，输出齿圈29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，另一路通过输入齿轮副6传递到输入齿轮26的功率随之而增大，输入齿轮26则通过固定行星架25上的行星齿轮20把功率传递到输出齿轮24，输出齿轮24再通过箱体式液力偶合器4传递到输入大齿圈22，即输入大齿圈22的输入功率随之而增大，输入小齿圈21、输入大齿圈22把传递到各自的功率通过输出行星架23上的行星齿轮20汇流于输出行星架23，输出行星架23再重复上述过程，使传递到输入行星架27上的转速不断变化，输入行星架27与输入小齿轮28把传递到各自的功率通过输入行星架27上的行星齿轮20汇流于输出齿圈29，输出齿圈29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，输入行星架27上的转速，则随着车辆输入功率或者行驶阻力的不同而变化，阻力越低，传递到输入行星架27上的转速就越高，反之，则越低，从而实现本发明能随车辆输入功率或者行驶阻力的不同而改变速度的复合型箱体式液力偶合器。
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21，另一路经过输出齿轮副8传递到输入小齿轮28，输入小齿圈21把传递到此的功率通过输出行星架23上的行星齿轮20汇流于输出行星架23，输出行星架23通过联接输出齿轮副7再分流为两路，一路传递到输入行星架27，此时，输入行星架 27与输入小齿轮28把传递到各自的功率通过输入行星架27上的行星齿轮20汇流于输出齿圈29，输出齿圈29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，另一路通过输入齿轮副6传递到输入齿轮26的功率随之而增大，输入齿轮26则通过固定行星架25上的行星齿轮20把功率传递到输出齿轮24，输出齿轮24再通过箱体式液力偶合器4传递到输入大齿圈22，即输入大齿圈22的输入功率随之而增大，输入小齿圈21、输入大齿圈22把传递到各自的功率通过输出行星架23上的行星齿轮20汇流于输出行星架23，输出行星架23再重复上述过程，使传递到输入行星架27上的转速不断变化，输入行星架27与输入小齿轮28把传递到各自的功率通过输入行星架27上的行星齿轮20汇流于输出齿圈29，输出齿圈29则传递到本发明的输出轴5,当传递到输出轴5上的扭矩，经过传动系统传动到驱动轮上产生的牵引力足以进一步克服汽车行阻力时,汽车则继续加速，箱体式液力偶合器4的输出端42的转速也逐渐升高，与之相联的输入大齿圈22的转速也随之逐渐升高，从而使输出行星架23、输入行星架27以及输出轴5上的转速随之不断地升高。

Claims (2)

  1. 种复合型箱体式液力偶合器以及起动器，包括输入轴(1)、输入齿轮(3)、输入齿轮副(4)、输出轴(5)、空挂档机构(6)、箱体式液力偶合器(7)、固定单向离合器(8)、起动机齿轮副(9)、超越离合器(10)、起动齿轮副(11)、电磁离合器(12)、联接轴(13)，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)、输入齿轮(22)、输出大齿圈(23)、输入齿圈(24)、固定行星架(25)、输出齿圈(26)、联接输入行星架(27)、固定齿轮(28)、输出齿轮(29),输入轴(1)与起动齿轮副(11)的输出齿轮(112)以及超越离合器(10)的输入端(101)联接,超越离合器(10)的输出端(102)与输入齿轮(22)以及起动机齿轮副(9)的输出齿轮(92)联接,起动机齿轮副(9)的输出齿轮(92)与起动机齿轮副(9)的输入齿轮(91)相互配合工作，输入齿轮(22)通过输入行星架(21)上的行星齿轮(20)与输入行星架(21)、输出大齿圈(23)相互配合工作，输出大齿圈(23)与输入齿圈(24)啮合，联接轴(13)与输入齿圈(24)、电磁离合器(12)的输入端(121)以及输入齿轮副(4)的输入齿轮(41)联接，输入齿轮副(4)的输出齿轮(42)与空挂档机构(6)的输入端(61)联接，空挂档机构(6)的输出端(62)与输出轴(5)联接，电磁离合器(12)的输出端(122)与起动齿轮副(11)的输入齿轮(111)联接，输入齿圈(24)通过固定行星架(25)上的行星齿轮(20)与固定行星架(25)、输出齿圈(26)相互配合工作，输出齿圈(26)与输入齿轮(3)啮合，输入齿轮(3)与联接输入行星架(27)联接，联接输入行星架(27)通过其上的行星齿轮(20)与固定齿轮(28)、输出齿轮(29)相互配合工作，固定行星架(25)、固定齿轮(28)以及固定单向离合器(8)的输入端(81)与固定元件联接，输出齿轮(29)与箱体式液力偶合器(7)的输入端(71)联接,箱体式液力偶合器(7)的输出端(72)以及固定单向离合器(8)的输出端(82)与输入行星架(21)联接。
  2. 一种复合型箱体式液力偶合器，包括输入轴(1)、单向离合器(3)、箱体式液力偶合器(4)、输出轴(5)、输入齿轮副(6)、联接输出齿轮副(7)、输出齿轮副(8)，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)、输入小齿圈(21)、输入大齿圈(22)、输出行星架(23)、输出齿轮(24)、固定行星架(25)、输入齿轮(26)、输入行星架(27)、输入小齿轮(28)、输出齿圈(29)，输入轴(1)与输入小齿圈(21)以及输出齿轮副(8)的输入齿轮(81)联接,输出齿轮副(8)的输出齿轮(82)与输入小齿轮(28)联接,输入小齿圈(21)通过输出行星架(23)上的行星齿轮(20)与输入大齿圈(22)、输出行星架(23)相互配合工作，输出行星架(23)与联接输出齿轮副(7)的输入齿轮(71)联接,联接输出齿轮副(7)的输出齿轮(72)与输入行星架(27)以及输入齿轮副(6)的输入齿轮(61)联接,输入齿轮副(6)的输出齿轮(62)与输入齿轮(26)联接,输入齿轮(26)通过固定行星架(25)上的行星齿轮(20)与输出齿轮(24)、固定行星架(25)相互配合工作，固定行星架(25)以及单向离合器(3)的输入端(31)与固定元件固接,输出齿轮(24)与箱体式液力偶合器(4)的输入端(41)联接,箱体式液力偶合器(4)的输出端(42)与单向离合器(3)的输出端(32)以及输入大齿圈(22)联接,输入行星架(27)通过其上的行星齿轮(20)与输入小齿轮(28)、输出齿圈(29)相互配合工作，输出齿圈(29)与输出轴(5)联接。
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