WO2017005178A1 - 一种复合型外壳带侧辅室的液力偶合器以及起动器 - Google Patents

一种复合型外壳带侧辅室的液力偶合器以及起动器 Download PDF

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Publication number
WO2017005178A1
WO2017005178A1 PCT/CN2016/088742 CN2016088742W WO2017005178A1 WO 2017005178 A1 WO2017005178 A1 WO 2017005178A1 CN 2016088742 W CN2016088742 W CN 2016088742W WO 2017005178 A1 WO2017005178 A1 WO 2017005178A1
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Prior art keywords
gear
input
output
carrier
shaft
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PCT/CN2016/088742
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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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Application filed by 吴志强 filed Critical 吴志强
Priority to CN201680039169.5A priority Critical patent/CN108474461A/zh
Publication of WO2017005178A1 publication Critical patent/WO2017005178A1/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 fluid couplings and starting, and more particularly to a fluid coupling and a starter for a composite outer casing with side auxiliary chambers of 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 fluid coupling and a starter for extending the service life of the engine, having a simple structure, convenient operation, low cost, energy saving and high efficiency, and a composite outer casing with a side auxiliary chamber.
  • the utility model relates to a hydraulic coupling with a side auxiliary chamber and a starter, comprising an input shaft (1), a fixed one-way clutch (3), a fluid coupling (4) with a side auxiliary chamber on the outer casing, and an output shaft ( 5), empty gear mechanism (6), input gear (7), output gear pair (8), coupling shaft (9), starter gear pair (10), electromagnetic clutch (11), input start gear pair (12).
  • the overrunning clutch (13) is provided with a planetary gear (20), an input carrier (21), an input gear (22), and an output gear (23) between the input shaft (1) and the output shaft (5).
  • the gear (26), the output gear (82) of the output gear pair (8), and the input end (111) of the electromagnetic clutch (11) are coupled, and the output end (62) and the output shaft (5) of the idle gear mechanism (6) Coupling, the output end (112) of the electromagnetic clutch (11) is coupled to the input gear (121) of the input starter gear pair (12), and the input large gear (26) is passed through the planetary gear (20) on the output carrier (25).
  • the fixed gear (24) and the output carrier (25) cooperate with each other, the output carrier (25) is coupled with the input gear (7), the input gear (7) is meshed with the input ring gear (29), and the input ring gear (29)
  • the planetary gear (20) on the fixed carrier (27) cooperates with the fixed carrier (27) and the output ring gear (28) to output a fluid coupling of the ring gear (28) and the side auxiliary chamber of the outer casing ( 4)
  • the input end (41) is coupled, and the output end (42) of the fluid coupling (4) with the side auxiliary chamber of the outer casing is coupled with the input gear (22) and the output end (32) of the fixed one-way clutch (3).
  • the input of the fixed one-way clutch (3) ( 31)
  • the fixed gear (24) and the fixed planet carrier (27) are coupled to the fixed element.
  • a compound type housing with a side auxiliary chamber including an input shaft (1), a coupling shaft (3), a one-way clutch (4), a fluid coupling (5) with a side auxiliary chamber, and an output A shaft (6) and an output coupling shaft (7), wherein the input shaft (1) and the output shaft (6) are provided with a planetary gear (20), an output carrier (21), and an input small ring gear (22).
  • the output end (52) of the hydraulic coupling (5) of the side auxiliary chamber is coupled with the output end (42) of the one-way clutch (4) and the input large ring gear (23) through which the input carrier (27) passes.
  • the planetary gear (20) cooperates with the output ring gear (28) and the input gear (29), and the output ring gear (28) is coupled with the output shaft (7).
  • 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 fluid coupling of the outer casing with the side auxiliary chamber may be replaced by a centripetal 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 fluid coupling and a starter for a composite outer casing with side auxiliary chambers of 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 type housing with a side auxiliary chamber and a starter including an input shaft 1, a fixed one-way clutch 3, a fluid coupling 4 with a side auxiliary chamber, and an output shaft 5.
  • a planetary gear 20 an input carrier 21, an input gear 22, an output gear 23, a fixed gear 24, an output carrier 25, an input bull gear 26, a fixed planet carrier 27, an output ring gear 28, and an input ring gear 29 are provided.
  • the input shaft 1 is coupled to the output gear 122 of the input starter gear pair 12 and the input end 131 of the overrunning clutch 13, and the output end 132 of the overrunning clutch 13 is coupled to the input carrier 21 and the output gear 102 of the starter gear pair 10, the starter The output gear 102 of the gear pair 10 cooperates with the input gear 101 of the starter gear pair 10, and the input carrier 21 cooperates with the input gear 22 and the output gear 23 via the planetary gear 20 thereon, and the output gear 23 and the output gear vice
  • the input gear 81 of 8 is coupled, and the coupling shaft 9 is coupled to the input end 61 of the neutral shifting mechanism 6, the input bull gear 26, the output gear 82 of the output gear pair 8, and the input end 111 of the electromagnetic clutch 11, the idle gear mechanism 6
  • the output end 62 is coupled to the output shaft 5, and the output end 112 of the electromagnetic clutch 11 is coupled to the input gear 121 of the input starter gear pair 12.
  • the input large gear 26 passes through the planetary gear 20 on the output carrier 25 and the fixed gear 24, and the output carrier 25 cooperates with each other, the output carrier 25 is coupled to the input gear 7, the input gear 7 is meshed with the input ring gear 29, and the input ring gear 29 is fixed to the fixed carrier 27 and the output ring gear 28 by the planetary gear 20 on the fixed carrier 27.
  • the output ring gear 28 is coupled to the input end 41 of the fluid coupling 4 of the outer casing with the side auxiliary chamber, the output end 42 of the fluid coupling 4 with the side auxiliary chamber of the outer casing and the input gear 22 and the fixed one-way clutch 3
  • the output 32 is coupled, the input 31 of the fixed one-way clutch 3, the fixed gear 24 and the fixed planet carrier 27 are coupled to the stationary element.
  • the neutral shifting mechanism 6 is disengaged, and the electromagnetic clutch 11 is engaged.
  • the input power of the starter is transmitted to the input carrier 21 through the starter gear pair 10, and the input carrier 21 is transmitted to the output gear 23 through the planetary gear 20 thereon.
  • the output gear 23 is then transmitted to the input shaft 1 through the output gear pair 8, the coupling shaft 9, the electromagnetic clutch 11 and the input start gear pair 12, and then transmitted to the crankshaft of the engine, and the generated starting power is sufficient to overcome the engine starting resistance when the engine is started. .
  • the air-gear mechanism 6 is engaged, the electromagnetic clutch 11 is disengaged, and the input carrier 21 transmits the power transmitted thereto through the input shaft 1 and the overrunning clutch 13 through the planetary gear 20 thereon, and is transmitted to the output gear 23,
  • the output gear 23 is transmitted to the coupling shaft 9 through the output gear pair 8, and the coupling shaft 9 diverts the power transmitted thereto into two paths, one through the idle gear mechanism 6 to the output shaft 5 of the present invention; the other is transmitted to the input
  • the large gear 26, the input large gear 26 is transmitted to the output carrier 25 through the planetary gear 20 on the output carrier 25, the output carrier 25, the output carrier 25 is transmitted to the input ring gear 29 through the input gear 7, and the input ring gear is input.
  • the output speed of the fluid coupling 4 continuously changes steplessly with changes in input power and running resistance, so that the output rotational speed of the output gear 23 also constantly changes, and through the output gear pair 8, the coupling shaft 9 and The idle gear 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 gear 22, the output gear 23, and the output shaft 5 varies with the change in the rotational speed thereof, and the lower the rotational speed, the transmission to the input gear 22, the output gear 23, and the output.
  • the greater the torque on the shaft 5, and vice versa the smaller the hydraulic torque coupling and the starter of the composite housing with the side and the auxiliary chamber that can change the torque and speed according to the present invention.
  • the idle gear mechanism 6 When the invention is used, before the engine is started, the idle gear mechanism 6 is disengaged, the electromagnetic clutch 11 is engaged, and the engine speed is zero.
  • the starter When the starter is started, the input power of the starter is transmitted to the input carrier 21 through the starter gear pair 10, Wherein, since no power flows into the input gear 22 at this time, and the input end 31 of the fixed one-way clutch 3 is coupled with the fixed component, the steering is restricted to make the input gear 22 unable to rotate opposite to the engine, and the rotational speed is zero.
  • the power transmitted to the input carrier 21 transmits power to the output gear 23 through the planetary gear 20 thereon, and the output gear 23 passes through the output gear pair 8, the coupling shaft 9, the electromagnetic clutch 11, and the input start gear pair 12 It is transmitted to the input shaft 1 and then transmitted to the engine crankshaft.
  • the torque transmitted to the crankshaft of the engine is generated enough to overcome the starting resistance of the engine, the engine starts and accelerates.
  • 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 11 is separated, and the output shaft 5 is rotated.
  • the input power of the engine is transmitted to the input carrier 21 via the input shaft 1 and the overrunning clutch 13, wherein since no power flows into the input gear 22 at this time, and the input end 31 of the fixed one-way clutch 3 is coupled to the fixed element,
  • the function of limiting the steering is such that the input gear 22 cannot rotate opposite to the engine, and the rotational speed is zero.
  • the power transmitted to the input carrier 21 is transmitted to the output gear 23 through the planetary gear 20 thereon.
  • the output gear 23 is transmitted to the coupling shaft 9 through the output gear pair 8, and the coupling shaft 9 diverts the power transmitted thereto into two paths, one through the idle gear mechanism 6 to the output shaft 5 of the present invention, when transmitted to the output shaft
  • the torque on the 5, the traction generated by the drive train to the drive wheel is enough to overcome the starting resistance of the car, the car starts and starts to accelerate; another way It is transmitted to the input bull gear 26 through the input gear 7, and the input bull gear 26 is transmitted to the output carrier 25 through the planetary gear 20 on the output carrier 25, and the output carrier 25 is transmitted to the input ring gear 29 through the input gear 7, and the input ring gear is input.
  • Embodiment 2 is a diagrammatic representation of Embodiment 1:
  • a composite type housing with a side auxiliary chamber including an input shaft 1, a coupling shaft 3, a one-way clutch 4, a fluid coupling 5 with a side auxiliary chamber, and an output shaft 6.
  • the output coupling shaft 7 is provided with a planetary gear 20, an output planet carrier 21, an input small ring gear 22, an input large ring gear 23, a connecting planet carrier 24, and a transmission between the input shaft 1 and the output shaft 6.
  • the gear 25, the fixed gear 26, the input carrier 27, the output ring gear 28, the input gear 29, the input shaft 1 is coupled with the input small ring gear 22 and the coupling shaft 3, and the coupling shaft 3 is coupled with the input gear 29, and the input small ring gear 22 cooperates with the output carrier 21 and the input large ring gear 23 through the planetary gears 20 on the output carrier 21, the output carrier 21 is coupled with the output coupling shaft 7, the output coupling shaft 7 and the coupling carrier 24 and the input carrier 27, the connecting planet carrier 24 cooperates with the output gear 25 and the fixed gear 26 through the planetary gear 20 thereon, the fixed gear 26 and the input end 41 of the one-way clutch 4 are fixed to the fixed component, and the output gear 25 and the outer casing strap
  • the input end 51 of the fluid coupling 5 of the side auxiliary chamber is coupled, and the output end 52 of the fluid coupling 5 with the side auxiliary chamber of the outer casing is coupled with the output end 42 of the one-way clutch 4 and the input large ring gear 23, and the input carrier 27, through the planetary gear
  • the input small ring gear 22 and the input large ring gear 23 converge the power transmitted to the respective planets 20 through the planetary gears 20 on the output carrier 21, due to the fluid coupling 5 and the input large teeth of the outer casing with the outer casing
  • the ring 23 is coupled, so that the rotational speed of the input large ring gear 23 can be constantly changed as the rotational speed of the fluid coupling 5 of the outer casing side auxiliary chamber changes, so that the rotational speed of the output carrier 21 also changes.
  • the input power is split into two paths through the input shaft 1, one is transmitted to the input small ring gear 22, the other is transmitted to the input gear 29 via the coupling shaft 3, and the input small ring gear 22 passes the power transmitted thereto through the output carrier 21.
  • the planetary gear 20 merges with the output carrier 21, and the output carrier 21 is split into two paths, one path is transmitted to the input carrier 27 through the output coupling shaft 7, and at this time, the input carrier 27 and the input gear 29 are transmitted to the respective powers.
  • the planetary gear 20 on the input carrier 27 merges with the output ring gear 28, and the output ring gear 28 is transmitted to the output shaft 6 of the present invention, thereby realizing the external output of the engine power through the output shaft 6.
  • the output gear 25 is transmitted to the input large ring gear 23 through the fluid coupling 5 with the side auxiliary chamber of the outer casing, that is, the input power of the input large ring gear 23 increases accordingly, and the input small ring gear 22 and the input large tooth
  • the ring 23 converges the respective powers through the planetary gears 20 on the output carrier 21 to the output carrier 21, and the output carrier 21 repeats the above process, so that the rotational speed transmitted to the input carrier 27 is constantly changed, and the input carrier 27 and the input gear 29 merge the planetary gear 20 transmitted to the respective power through the input carrier 27 to the output ring gear 28, and the output ring gear 28 is transmitted to the output shaft 6 of the present invention, thereby realizing the passage of the engine power.
  • the output shaft 6 is output to the outside.
  • the rotational speed input to the carrier 27 varies with the input power or the running resistance of the vehicle, and the lower the resistance, the transmission to the input large ring gear 23 and the output gear 25 And the higher the rotational speed of the input carrier 27, and vice versa, thereby realizing the fluid coupling of the composite outer casing side auxiliary chamber which can change the speed according to the input power or the running resistance of the present invention.
  • the input power, the input rotational speed and the load of the engine are unchanged, that is, the rotational speed and the torque of the input shaft 1 are constant, and before the vehicle starts, the rotational speed of the output shaft 6 is zero, and the input power of the engine passes through the input shaft 1
  • the split is two ways, one is transmitted to the input small ring gear 22, the other is transmitted to the input gear 29 via the coupling shaft 3, and the input small ring gear 22 converges the power transmitted thereto through the planetary gear 20 on the output carrier 21 to the output.
  • the planet carrier 21, the output planet carrier 21 is split into two paths, one pass is transmitted through the output coupling shaft 7 to the input carrier 27, at which time the input carrier 27 and the input gear 29 are transmitted to their respective powers through the input carrier 27.
  • the planetary gear 20 merges with the output ring gear 28, and the output ring gear 28 is transmitted to the output shaft 6 of the present invention, thereby realizing the external output of the engine power through the output shaft 6.
  • the large ring gear 23, that is, the input power of the input large ring gear 23, is increased accordingly, and the input small ring gear 22 and the input large ring gear 23 converge the output to the respective power through the planetary gear 20 on the output carrier 21 to the output.
  • the carrier 21, the output carrier 21 repeats the above process to continuously change the rotational speed transmitted to the input carrier 27, and the input carrier 27 and the input gear 29 transmit the respective powers to the planetary gears 20 passing through the input carrier 27. Converging on the output ring gear 28, the output ring gear 28 is transmitted to the output shaft 6 of the present invention.

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Abstract

一种复合型外壳带侧辅室的液力偶合器以及具有该外壳带侧辅室的液力偶合器的起动器，其中输入轴（1）与输入起动齿轮副（12）以及超越离合器（13）联接，超越离合器（13）与输入行星架（21）以及起动机齿轮副（10）联接，输出齿轮（23）与输出齿轮副（8）联接，联接轴（9）与空挂档机构（6）、输入大齿轮（26）、输出齿轮副（8）以及电磁离合器（11）联接，空挂档机构（6）与输出轴（5）联接，电磁离合器（11）与输入起动齿轮副（12）联接，输出行星架（25）与输入齿轮（7）联接，输入齿轮（7）与输入齿圈（29）啮合，输出齿圈（28）与外壳带侧辅室的液力偶合器（4）联接，外壳带侧辅室的液力偶合器（4）与输入齿轮（22）以及固定单向离合器（3）联接。

Description

一种复合型外壳带侧辅室的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外壳带侧辅室的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，节能高效的复合型外壳带侧辅室的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：
一种复合型外壳带侧辅室的液力偶合器以及起动器，包括输入轴(1)、固定单向离合器(3)、外壳带侧辅室的液力偶合器(4)、输出轴(5)、空挂档机构(6)、输入齿轮(7)、输出齿轮副(8)、联接轴(9)、起动机齿轮副(10)、电磁离合器(11)、输入起动齿轮副(12)、超越离合器(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)、输出齿轮(23)、固定齿轮(24)、输出行星架(25)、输入大齿轮(26)、固定行星架(27)、输出齿圈(28)、输入齿圈(29),输入轴(1)与输入起动齿轮副(12)的输出齿轮(122)以及超越离合器(13)的输入端(131)联接,超越离合器(13)的输出端(132)与输入行星架(21)以及起动机齿轮副(10)的输出齿轮(102)联接,起动机齿轮副(10)的输出齿轮(102)与起动机齿轮副(10)的输入齿轮(101)相互配合工作，输入行星架(21)通过其上的行星齿轮(20)与输入齿轮(22)、输出齿轮(23)相互配合工作，输出齿轮(23)与输出齿轮副(8)的输入齿轮(81)联接，联接轴(9)与空挂档机构(6)的输入端(61)、输入大齿轮(26)、输出齿轮副(8)的输出齿轮(82)以及电磁离合器(11)的输入端(111)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(11)的输出端(112)与输入起动齿轮副(12)的输入齿轮(121)联接，输入大齿轮(26)通过输出行星架(25)上的行星齿轮(20)与固定齿轮(24)、输出行星架(25)相互配合工作，输出行星架(25)与输入齿轮(7)联接，输入齿轮(7)与输入齿圈(29)啮合，输入齿圈(29)通过固定行星架(27)上的行星齿轮(20)与固定行星架(27)、输出齿圈(28)相互配合工作，输出齿圈(28)与外壳带侧辅室的液力偶合器(4)的输入端(41)联接,外壳带侧辅室的液力偶合器(4)的输出端(42)与输入齿轮(22)以及固定单向离合器(3)的输出端(32)联接，固定单向离合器(3)的输入端(31)、固定齿轮(24)以及固定行星架(27)与固定元件联接。
一种复合型外壳带侧辅室的液力偶合器，包括输入轴(1)、联接轴(3)、单向离合器(4)、外壳带侧辅室的液力偶合器(5)、输出轴(6)、输出联接轴(7)，所述的输入轴(1)与输出轴(6)之间设有行星齿轮(20)、输出行星架(21)、输入小齿圈(22)、输入大齿圈(23)、联接行星架(24)、输出齿轮(25)、固定齿轮(26)、输入行星架(27)、输出齿圈(28)、输入齿 轮(29)，输入轴(1)与输入小齿圈(22)以及联接轴(3)联接,联接轴(3)与输入齿轮(29)联接,输入小齿圈(22)通过输出行星架(21)上的行星齿轮(20)与输出行星架(21)、输入大齿圈(23)相互配合工作，输出行星架(21)与输出联接轴(7)联接,输出联接轴(7)与联接行星架(24)以及输入行星架(27)联接,联接行星架(24)通过其上的行星齿轮(20)与输出齿轮(25)、固定齿轮(26)相互配合工作，固定齿轮(26)以及单向离合器(4)的输入端(41)与固定元件固接,输出齿轮(25)与外壳带侧辅室的液力偶合器(5)的输入端(51)联接,外壳带侧辅室的液力偶合器(5)的输出端(52)与单向离合器(4)的输出端(42)以及输入大齿圈(23)联接,输入行星架(27)通过其上的行星齿轮(20)与输出齿圈(28)、输入齿轮(29)相互配合工作，输出齿圈(28)与输出轴(7)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。
所述外壳带侧辅室的液力偶合器可以选择向心式液力变矩器代替。
所述空挂档机构可以选择离合器代替。
本发明应用于车辆时，能够根据车辆行驶时受到阻力的大小，自动地改变输出扭矩以及速度的变化。
本发明具有以下的优点：
(1)本发明大部份功率由齿圈、行星齿轮、行星架、齿轮传递，因而传动功率和传动效率都极大地提高,而且结构简单，更易于维修；
(2)本发明的变矩和变速是自动完成的，能实现高效率的传动，并且除了起步以外，都能使发动机和起动机在最佳范围内工作，与其它变速器相比，在发动机和起动机等效的前提下，它降低了发动机和起动机的制造成本；
(3)本发明使发动机和起动机处于经过济转速区域内运转，也就是使发动机在非常小污染排放的转速范围内工作，避免了发动机在怠速和高速运行时，排放大量废气，从而减少了废气的排放，有利于保护环境；
(4)本发明能利用内部转速差起缓冲和过载保护的作用，有利于延长发动机和传动系以及起动机的使用寿命，另外，当行驶阻力增大，则能使车辆自动降速，反之则升速，有利于提高车辆的行驶性能；
(5)本发明使输入功率不间断，可保证车辆有良好的加速性和较高的平均车速，使发动机的磨损减少，延长了大修间隔里程，有利于提高生产率；
(6)本发明起动时，具有自动变矩和变速的性能，输入功率不间断，不会发生冲击现象，可保证发动机起动平稳、减少噪音，使发动机的起动磨损减少，并延长了起动电机以及蓄电池的使用寿命；
(7)本发明减少了现今起动机的传动机构，降低了制造成本，发动机起动后，只需对起动电机采取制动以及分离的措施，使其停止传动。
另外，本发明是是一种用于各种地面车辆、船舶、铁道机车以及机床的复合型外壳带侧辅室的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，一种复合型外壳带侧辅室的液力偶合器以及起动器，包括输入轴1、固定单向离合器3、外壳带侧辅室的液力偶合器4、输出轴5、空挂档机构6、输入齿轮7、输出齿轮副8、联接轴9、起动机齿轮副10、电磁离合器11、输入起动齿轮副12、超越离合器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、输出齿轮23、固定齿轮24、输出行星架25、输入大齿轮26、固定行星架27、输出齿圈28、输入齿圈29,输入轴1与输入起动齿轮副12的输出齿轮122以及超越离合器13的输入端131联接,超越离合器13的输出端132与输入行星架21以及起动机齿轮副10的输出齿轮102联接,起动机齿轮副10的输出齿轮102与起动机齿轮副10的输入齿轮101相互配合工作，输入行星架21通过其上的行星齿轮20与输入齿轮22、输出齿轮23相互配合工作，输出齿轮23与输出齿轮副8的输入齿轮81联接，联接轴9与空挂档机构6的输入端61、输入大齿轮26、输出齿轮副8的输出齿轮82以及电磁离合器11的输入端111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11的输出端112与输入起动齿轮副12的输入齿轮121联接，输入大齿轮26通过输出行星架25上的行星齿轮20与固定齿轮24、输出行星架25相互配合工作，输出行星架25与输入齿轮7联接，输入齿轮7与输入齿圈29啮合，输入齿圈29通过固定行星架27上的行星齿轮20与固定行星架27、输出齿圈28相互配合工作，输出齿圈28与外壳带侧辅室的液力偶合器4的输入端41联接,外壳带侧辅室的液力偶合器4的输出端42与输入齿轮22以及固定单向离合器3的输出端32联接，固定单向离合器3的输入端31、固定齿轮24以及固定行星架27与固定元件联接。
发动机起动前，分离空挂档机构6，接合电磁离合器11，起动机的输入功率经过起动机齿轮副10传递到输入行星架21，输入行星架21通过其上的行星齿轮20传递到输出齿轮23，输出齿轮23再通过输出齿轮副8、联接轴9、电磁离合器11以及输入起动齿轮副12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11，输入行星架21通过其上的行星齿轮20把由发动机经过输入轴1以及超越离合器13传递到此的功率，传递到输出齿轮23，输出齿轮23则通过输出齿轮副8传递到联接轴9，联接轴9把传递到此的功率分流为两路，一路经过空挂档机构6传递到本发明的输出轴5；另一路传递到输入大齿轮26，输入大齿轮26再通过输出行星架25上的行星齿轮20传递到输出行星架25，输出行星架25，输出行星架25再通过输入齿轮7传递到输入齿圈29，输入齿圈29再通过固定行星架27上的行星齿轮20传递到输出齿圈28，输出齿圈28则通过外壳带侧辅室的液力偶合器4传递到输入齿轮22，传递到输入齿轮22的功率以及由发动机经过输入轴1以及超越离合器13传 递到输入行星架21的功率，则通过输入行星架21上的行星齿轮20传递到输出齿轮23，输出齿轮23再在各个元件之间不断地进行变速的反复循环，其中，外壳带侧辅室的液力偶合器4的输出转速不断地随着输入功率、行驶阻力的变化而无级地变速，从而使输出齿轮23的输出转速也不断地变化，并且通过输出齿轮副8、联接轴9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，输入齿轮22、输出齿轮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，传递到输入齿轮22、输出齿轮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外壳带侧辅室的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11，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10传递到输入行星架21,其中，由于此时没有功率流入输入齿轮22，并且固定单向离合器3的输入端31与固定元件联接，起限制转向的作用，使输入齿轮22不能与发动机相反的转向转动，转速为零，此时，传递到输入行星架21的功率，则通过其上的行星齿轮20把功率传递到输出齿轮23，输出齿轮23再通过输出齿轮副8、联接轴9、电磁离合器11以及输入起动齿轮副12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11，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13，传递到输入行星架21，其中，由于此时没有功率流入输入齿轮22，并且固定单向离合器3的输入端31与固定元件联接，起限制转向的作用，使输入齿轮22不能与发动机相反的转向转动，转速为零，此时，传递到输入行星架21的功率，则通过其上的行星齿轮20把功率传递到输出齿轮23，输出齿轮23则通过输出齿轮副8传递到联接轴9，联接轴9把传递到此的功率分流为两路，一路经过空挂档机构6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；另一路通过输入齿轮7传递到输入大齿轮26，输入大齿轮26通过输出行星架25上的行星齿轮20传递到输出行星架25，输出行星架25通过输入齿轮7传递到输入齿圈29，输入齿圈29通过固定行星架27上的行星齿轮20传递到输出齿圈28，输出齿圈28再通过外壳带侧辅室的液力偶合器4传递到输入齿轮22，传递到输入齿轮22的功率以及由发动机经过输入轴1以及超越离合器13传递到输入行星架21的功率，则通过输入行星架21上的行星齿轮20传递到输出齿轮23，输出齿轮23再在各个元件之间不断地进行变速的反复循环，其中，外壳带侧辅室的液力偶合器4的输出转速不断地随着行驶阻力的变化而无级地变速，从而使输入齿轮23的输出转速也不断地变化，并且通过输出齿轮副8、联接轴9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，一种复合型外壳带侧辅室的液力偶合器，包括输入轴1、联接轴3、单向离合器4、外壳带侧辅室的液力偶合器5、输出轴6、输出联接轴7，所述的输入轴1与输出轴6之间设有行星齿轮20、输出行星架21、输入小齿圈22、输入大齿圈23、联接行星架24、输 出齿轮25、固定齿轮26、输入行星架27、输出齿圈28、输入齿轮29，输入轴1与输入小齿圈22以及联接轴3联接,联接轴3与输入齿轮29联接,输入小齿圈22通过输出行星架21上的行星齿轮20与输出行星架21、输入大齿圈23相互配合工作，输出行星架21与输出联接轴7联接,输出联接轴7与联接行星架24以及输入行星架27联接,联接行星架24通过其上的行星齿轮20与输出齿轮25、固定齿轮26相互配合工作，固定齿轮26以及单向离合器4的输入端41与固定元件固接,输出齿轮25与外壳带侧辅室的液力偶合器5的输入端51联接,外壳带侧辅室的液力偶合器5的输出端52与单向离合器4的输出端42以及输入大齿圈23联接,输入行星架27通过其上的行星齿轮20与输出齿圈28、输入齿轮29相互配合工作，输出齿圈28与输出轴6联接。
输入小齿圈22、输入大齿圈23把传递到各自的功率通过输出行星架21上的行星齿轮20汇流于输出行星架21，由于外壳带侧辅室的液力偶合器5与输入大齿圈23联接,所以输入大齿圈23的转速可以不断地随着外壳带侧辅室的液力偶合器5转速的变化而变化,从而使输出行星架21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22，另一路经过联接轴3传递到输入齿轮29，输入小齿圈22把传递到此的功率通过输出行星架21上的行星齿轮20汇流于输出行星架21，输出行星架21再分流为两路，一路通过输出联接轴7传递到输入行星架27，此时，输入行星架27与输入齿轮29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28，输出齿圈28则传递至本发明的输出轴6,从而实现了把发动机的功率通过输出轴6对外输出。
当发动机的输入功率增大或者输出轴6的阻力减少时，另一路传递到联接行星架24的功率随之而增大，联接行星架24则通过其上的行星齿轮20把功率传递到输出齿轮25，输出齿轮25再通过外壳带侧辅室的液力偶合器5传递到输入大齿圈23，即输入大齿圈23的输入功率随之而增大，输入小齿圈22、输入大齿圈23把传递到各自的功率通过输出行星架21上的行星齿轮20汇流于输出行星架21，输出行星架21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与输入齿轮29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28，输出齿圈28则传递到本发明的输出轴6,从而实现了把发动机的功率通过输出轴6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，传递到输入大齿圈23、输出齿轮25以及输入行星架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外壳带侧辅室的液力偶合器。
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6的转速为零，发动机的输入功率经过输入轴1分流为两路，一路传递到输入小齿圈22，另一路经过联接轴3传递到输入齿轮29，输入小齿圈22把传递到此的功率通过输出行星架21上的行星齿轮20汇流于输出行星架21，输出行星架21再分流为两路，一路通过输出联接轴7传递到输入行星架27，此时，输入行星架27与输入齿轮29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28，输出齿圈28则传递至本发明的输出轴6,从而实现了把发动机的功率通过输出轴6对外输出。
当传递到输出轴6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6的阻力减少时，另一路传递到联接行星架24的功率随之而增大，联接行星架24则通过其上的行星齿轮20把功率传递到输出齿轮25，输出齿轮25再通过外壳带侧辅室的液力偶合器5传递到输入大齿圈23，即输入大齿圈23的输入功率随之而增大，输入小齿圈22、输入大齿圈23把传递到各自的功率通过输出行星架21上的行星齿轮20汇流于输出行星架21，输出行星架21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与输入齿轮29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28，输出齿圈28则传递到本发明的输出轴6,当传递到输出轴6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，外壳带侧辅室的液力偶合器5的输出端52的转速也逐渐升高，与之相联的输入大齿圈23的转速也随之逐渐升高，从而使输出行星架21、输入行星架27以及输出轴6上的转速随之增加而不断地升高。

Claims (2)

  1. 一种复合型外壳带侧辅室的液力偶合器以及起动器，包括输入轴(1)、固定单向离合器(3)、外壳带侧辅室的液力偶合器(4)、输出轴(5)、空挂档机构(6)、输入齿轮(7)、输出齿轮副(8)、联接轴(9)、起动机齿轮副(10)、电磁离合器(11)、输入起动齿轮副(12)、超越离合器(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)、输出齿轮(23)、固定齿轮(24)、输出行星架(25)、输入大齿轮(26)、固定行星架(27)、输出齿圈(28)、输入齿圈(29),输入轴(1)与输入起动齿轮副(12)的输出齿轮(122)以及超越离合器(13)的输入端(131)联接,超越离合器(13)的输出端(132)与输入行星架(21)以及起动机齿轮副(10)的输出齿轮(102)联接,起动机齿轮副(10)的输出齿轮(102)与起动机齿轮副(10)的输入齿轮(101)相互配合工作，输入行星架(21)通过其上的行星齿轮(20)与输入齿轮(22)、输出齿轮(23)相互配合工作，输出齿轮(23)与输出齿轮副(8)的输入齿轮(81)联接，联接轴(9)与空挂档机构(6)的输入端(61)、输入大齿轮(26)、输出齿轮副(8)的输出齿轮(82)以及电磁离合器(11)的输入端(111)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(11)的输出端(112)与输入起动齿轮副(12)的输入齿轮(121)联接，输入大齿轮(26)通过输出行星架(25)上的行星齿轮(20)与固定齿轮(24)、输出行星架(25)相互配合工作，输出行星架(25)与输入齿轮(7)联接，输入齿轮(7)与输入齿圈(29)啮合，输入齿圈(29)通过固定行星架(27)上的行星齿轮(20)与固定行星架(27)、输出齿圈(28)相互配合工作，输出齿圈(28)与外壳带侧辅室的液力偶合器(4)的输入端(41)联接,外壳带侧辅室的液力偶合器(4)的输出端(42)与输入齿轮(22)以及固定单向离合器(3)的输出端(32)联接，固定单向离合器(3)的输入端(31)、固定齿轮(24)以及固定行星架(27)与固定元件联接。
  2. 一种复合型外壳带侧辅室的液力偶合器，包括输入轴(1)、联接轴(3)、单向离合器(4)、外壳带侧辅室的液力偶合器(5)、输出轴(6)、输出联接轴(7)，其特征在于：所述的输入轴(1)与输出轴(6)之间设有行星齿轮(20)、输出行星架(21)、输入小齿圈(22)、输入大齿圈(23)、联接行星架(24)、输出齿轮(25)、固定齿轮(26)、输入行星架(27)、输出齿圈(28)、输入齿轮(29)，输入轴(1)与输入小齿圈(22)以及联接轴(3)联接,联接轴(3)与输入齿轮(29)联接,输入小齿圈(22)通过输出行星架(21)上的行星齿轮(20)与输出行星架(21)、输入大齿圈(23)相互配合工作，输出行星架(21)与输出联接轴(7)联接,输出联接轴(7)与联接行星架(24)以及输入行星架(27)联接,联接行星架(24)通过其上的行星齿轮(20)与输出齿轮(25)、固定齿轮(26)相互配合工作，固定齿轮(26)以及单向离合器(4)的输入端(41)与固定元件固接,输出齿轮(25)与外壳带侧辅室的液力偶合器(5)的输入端(51)联接,外壳带侧辅室的液力偶合器(5)的输出端(52)与单向离合器(4)的输出端(42)以及输入大齿圈(23)联接,输入行星架(27)通过其上的行星齿轮(20)与输出齿圈(28)、输入齿轮(29)相互配合工作，输出齿圈(28)与输出轴(7)联接。
PCT/CN2016/088742 2015-07-07 2016-07-06 一种复合型外壳带侧辅室的液力偶合器以及起动器 WO2017005178A1 (zh)

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