WO2017005184A1 - 一种复合式限矩型水介质液力偶合器以及起动器 - Google Patents

一种复合式限矩型水介质液力偶合器以及起动器 Download PDF

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Publication number
WO2017005184A1
WO2017005184A1 PCT/CN2016/088748 CN2016088748W WO2017005184A1 WO 2017005184 A1 WO2017005184 A1 WO 2017005184A1 CN 2016088748 W CN2016088748 W CN 2016088748W WO 2017005184 A1 WO2017005184 A1 WO 2017005184A1
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WIPO (PCT)
Prior art keywords
input
gear
output
carrier
ring gear
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PCT/CN2016/088748
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English (en)
French (fr)
Inventor
吴志强
Original Assignee
吴志强
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Publication date
Application filed by 吴志强 filed Critical 吴志强
Priority to CN201680039172.7A priority Critical patent/CN108496029A/zh
Publication of WO2017005184A1 publication Critical patent/WO2017005184A1/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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • 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 invention belongs to the field of fluid coupling and starting, and more particularly to a composite torque limiting hydraulic 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 compound torque limiting type hydraulic medium fluid coupling device and a starter which are prolonged in service life, simple in structure, convenient in operation, low in cost, energy-saving and high-efficiency.
  • Composite torque-limiting hydraulic medium fluid coupling and starter comprising input shaft (1), torque-limiting hydraulic medium coupling (3), second one-way clutch (4), output shaft (5) ), empty gear mechanism (6), coupling frame (7), coupling shaft (8), output gear pair (9), first one-way clutch (10), electromagnetic clutch (11), starter gear pair (12 ), a starting gear pair (13), an overrunning clutch (14), between the input shaft (1) and the output shaft (5), a planetary gear (20), an input pinion (21), and an output carrier ( 22), input large gear (23), output small ring gear (24), input planet carrier (25), fixed ring gear (26), output ring gear (27), input ring gear (28), fixed planet carrier ( 29)
  • the input shaft (1) is coupled to the output gear (132) of the start gear pair (13) and the input end (141) of the overrunning clutch (14), the output end (142) of the overrunning clutch (14) and the first single
  • the output end (72) of the gear mechanism (7) is coupled to the output shaft (5), the coupling frame (7) is coupled to the input ring gear (28), and the input ring gear (28) is passed through the planet gears on the fixed planet carrier (29). (20) working in cooperation with the output ring gear (27) and the fixed carrier (29), the output ring gear (27) is coupled to the input carrier (25), and the planetary gear (20) through which the carrier (25) passes is input.
  • the output small ring gear (24) is coupled with the input end (41) of the second one-way clutch (4), and the second one-way clutch (4)
  • the output end (102) is coupled to the input end (31) of the torque-limiting aqueous medium fluid coupling (3), and the output end (32) of the torque-limiting aqueous medium hydraulic coupling (3) and the input large gear (23)
  • the coupling, the fixed planet carrier (29) is coupled to the fixed ring gear (26), and the fixed planet carrier (29) is coupled to the fixed element.
  • Composite torque limiting hydraulic medium fluid coupling comprising input shaft (1), input gear pair (3), output shaft (4), coupling shaft (5), one-way clutch (6), limited moment type Aqueous medium fluid coupling (7), coupling gear (8), overrunning clutch (9)
  • the output gear pair (10) is provided with a planetary gear (20), an input small ring gear (21), and an output large ring gear (22) between the input shaft (1) and the output shaft (4).
  • the shaft (1) is coupled to the input carrier (23) and the input gear (101) of the output gear pair (10), and the output gear (102) of the output gear pair (10) and the coupling shaft (5) and the overrunning clutch (9)
  • the input end (91) is coupled, the output end (92) of the overrunning clutch (9) and the output end (62) of the one-way clutch (6) and the input end of the torque-limiting aqueous medium fluid coupling (7) (71)
  • the coupling end (72) of the torque-type hydraulic medium coupling (7) is coupled with the coupling gear (8), the coupling gear (8) meshes with the input small ring gear (21), and the input small ring gear (21)
  • the planetary gear (20) on the input carrier (23) cooperates with the output large ring gear (22) and the input carrier (23) to output the input of the large ring gear (22) and the input gear pair (3).
  • the gear (31) is coupled, the output gear (32) of the input gear pair (3), and the input large ring gear (25) and the input tooth (28) Coupling, the input large ring gear (25) cooperates with the fixed planet carrier (24) and the output gear (26) through the planetary gear (20) on the fixed planet carrier (24) to fix the planet carrier (24) and
  • the fixed component is fixed
  • the output gear (26) is coupled to the input end (61) of the one-way clutch (6)
  • the input ring gear (28) is passed through the planetary gear (20) on the output carrier (27) and the output carrier ( 27)
  • the input gears (29) cooperate with each other, and the output carrier (27) is coupled with the output shaft (4).
  • 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 torque-limiting hydraulic medium fluid coupling can be replaced by an impeller type 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, reduces the manufacturing cost, and only needs to face after the engine is started.
  • the motor is braked and separated to stop the drive.
  • the present invention is a composite torque limiting type hydraulic medium 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 torque-limiting hydraulic medium fluid coupling and starter includes an input shaft 1 , a torque-limiting hydraulic medium fluid coupling 3 , a second one-way clutch 4 , and an output shaft 5 .
  • empty gear mechanism 6 coupling frame 7, coupling shaft 8, output gear pair 9, first one-way clutch 10, electromagnetic clutch 11, starter gear pair 12, starting gear pair 13, overrunning clutch 14, the input
  • a planetary gear 20 an input pinion 21, an output carrier 22, an input bull gear 23, an output small ring gear 24, an input carrier 25, a fixed ring gear 26, an output ring gear 27,
  • the input ring gear 28 and the fixed carrier 29 are coupled to the output gear 132 of the starter gear pair 13 and the input end 141 of the overrunning clutch 14, the output end 142 of the overrunning clutch 14 and the input end 101 of the first one-way clutch 10
  • the output gear 122 of the starter gear pair 12 is coupled, the output gear 122 of the starter gear pair 12 and the input gear 121 of the starter gear pair 12 cooperate with each other
  • the input end 61, the output gear 92 of the output gear pair 9 and the input end 111 of the electromagnetic clutch 11 are coupled, the output gear 112 of the electromagnetic clutch 11 is coupled to the input gear 131 of the start gear pair 13, and the output end 72 of the idle gear mechanism 7 is
  • the output shaft 5 is coupled, and the coupling frame 7 is coupled to the input ring gear 28.
  • the input ring gear 28 cooperates with the output ring gear 27 and the fixed carrier 29 through the planetary gear 20 on the fixed planet carrier 29, and outputs the ring gear 27 and the input planet.
  • the frame 25 is coupled, the input planet carrier 25 cooperates with the output ring gear 24 fixed ring gear 26 through the planetary gear 20 thereon, and the output small ring gear 24 is coupled with the input end 41 of the second one-way clutch 4, the second single The output end 42 of the clutch 4 and the output end 102 of the first one-way clutch 10 are coupled to the input end 31 of the torque-limiting aqueous medium fluid coupling 3, and the output end 32 of the torque-limiting aqueous medium fluid coupling 3 is Input large gear 23 connection Fixing the carrier 29 is coupled with the fixed ring gear 26, planet carrier 29 is fixed to the fixed coupling element.
  • the idle gear mechanism 6 Before the engine is started, the idle gear mechanism 6 is disengaged and the electromagnetic clutch 11 is engaged.
  • the input power of the starter is transmitted to the first one-way clutch 10 via the starter gear pair 12, and the first one-way clutch 10 diverts the power transmitted thereto into Two paths are transmitted to the input pinion 21 all the way, and the other path is transmitted to the input bull gear 23 through the torque-limiting aqueous medium fluid coupling 3, and the input pinion 21 and the input large gear 23 transmit the respective power to the output carrier.
  • the planetary gears 20 on the 22 are merged with the output carrier 22, and the output carrier 22 is transmitted to the input shaft 1 through the output gear pair 9, the coupling shaft 8, the electromagnetic clutch 11 and the start gear pair 13, and then transmitted to the engine crankshaft to generate The driving force is enough to overcome the engine When starting resistance, the engine starts.
  • the idle gear mechanism 6 After the engine is started, the idle gear mechanism 6 is engaged, the electromagnetic clutch 11 is disengaged, and the input shaft 1 transmits the power transmitted thereto by the engine to the first one-way clutch 10 through the overrunning clutch 14, and the first one-way clutch 10 is further divided into Two paths are transmitted to the input pinion 21 all the way, and the other path is transmitted to the input bull gear 23 through the torque-limiting aqueous medium fluid coupling 3, and the input pinion 21 and the input large gear 23 transmit the respective power to the output carrier.
  • the planet gears 20 on the 22 merge with the output planet carrier 22, and the output planet carrier 22 is split into two paths, one pass through the output gear pair 9, the coupling shaft 8 and the idle gear mechanism 6 to the output shaft 5 of the present invention;
  • the coupling ring 7 is transmitted to the input ring gear 28, and the input ring gear 28 is transmitted to the output ring gear 27 through the planetary gears 20 on the fixed carrier 29, and the output ring gear 27 is transmitted to the input carrier 25, and the input carrier 25 passes.
  • the planetary gear 20 thereon is transmitted to the output small ring gear 24, and the output small ring gear 24 is transmitted to the input bull gear 23 through the second one-way clutch 4 and the torque-limiting aqueous medium fluid coupling 3, and the input pinion gear 21 is input.
  • the input bull gear 23 converges the planetary gears 20 that are transmitted to the respective powers through the output carrier 22 to the output carrier 22, and the output carrier 22 continuously repeats the shifting of the shifting between the respective components, wherein the torque limiting type
  • the output rotational speed of the hydraulic medium fluid coupling 3 continuously shifts steplessly with changes in input power and running resistance, so that the output rotational speed of the output carrier 22 also constantly changes, and passes through the output gear pair 9, the coupling shaft. 8 and the idle gear mechanism 6 are 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 bull gear 23, the output carrier 22, 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 large gear 23 and the output planet.
  • the torque on the frame 22 and the output shaft 5 is larger, and conversely, the smaller, so as to realize the composite torque-type hydraulic medium coupling and the starter which can change the torque and the speed according to the driving resistance of 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 first one-way clutch through the starter gear pair 12. 10.
  • the first one-way clutch 10 splits the power transmitted thereto into two paths, one way to the input pinion 21, and the other way to the input large gear 23 through the torque-limiting type medium medium fluid coupling 3, and the input pinion 21.
  • the input bull gear 23 converges the planetary gears 20 that are transmitted to the respective powers through the output carrier 22 to the output carrier 22, and the output carrier 22 passes through the output gear pair 9, the coupling shaft 8, the electromagnetic clutch 11, and the start gear.
  • the secondary 13 is transmitted to the input shaft 1 and then transmitted to the crankshaft of the engine, and the generated starting power is sufficient to overcome the engine starting resistance and the engine is started.
  • the input power, input speed and load of the engine are set to be constant, 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 input shaft 1 is
  • the power transmitted to the engine is transmitted to the first one-way clutch 10 through the overrunning clutch 14, and the first one-way clutch 10 is divided into two paths, one for the input pinion 21 and the other for the torque-type hydraulic medium.
  • the coupling 3 is transmitted to the input bull gear 23, the input pinion 21, the input bull gear 23 converges the respective powers to the output carrier 22 through the planetary gears 20 on the output carrier 22, and the output carrier 22 is split into two.
  • the road is transmitted to the output shaft 5 of the present invention through the output gear pair 9, the coupling shaft 8 and the idle gear mechanism 6; the other passage is transmitted to the input ring gear 28 through the coupling frame 7, and the input ring gear 28 is passed through the fixed carrier 29
  • the upper planetary gear 20 is transmitted to the output ring gear 27, and the output ring gear 27 is transmitted to the input carrier 25, and the input carrier 25 is transmitted to the output small ring gear 24 through the planetary gear 20 thereon, and the output is small.
  • the ring 24 is again transmitted to the input bull gear 23 through the second one-way clutch 4 and the torque-limiting aqueous medium fluid coupling 3, and the input pinion 21 and the input bull gear 23 transmit the respective power to the output carrier 22.
  • the planetary gear 20 merges with the output carrier 22, and the output carrier 22 continuously performs repeated cycles of shifting between the components, wherein
  • the output rotational speed of the rectangular-type aqueous medium fluid coupling 3 continuously changes steplessly with the change of the running resistance, so that the output rotational speed of the output carrier 22 also constantly changes, and passes through the output gear pair 9, the coupling shaft 8
  • the idle gear mechanism 6 is transmitted to the output shaft 5 of the present invention such that the torque of the output shaft 5 decreases as the number of revolutions increases.
  • Embodiment 2 is a diagrammatic representation of Embodiment 1:
  • a composite torque-limiting hydraulic medium fluid coupling comprises an input shaft 1, an input gear pair 3, an output shaft 4, a coupling shaft 5, a one-way clutch 6, a torque-limiting aqueous medium liquid.
  • the force coupling 7, the coupling gear 8, the overrunning clutch 9, the output gear pair 10, the planetary gear 20, the input small ring gear 21, the output large ring gear 22, and the input planet are disposed between the input shaft 1 and the output shaft 4.
  • the frame 23, the fixed planet carrier 24, the input large ring gear 25, the output gear 26, the output carrier 27, the input ring gear 28, the input gear 29, and the input shaft 1 are coupled to the input carrier 23 and the input gear 101 of the output gear pair 10
  • the output gear 102 of the output gear pair 10 is coupled to the coupling shaft 5 and the input end 91 of the overrunning clutch 9, the output end 92 of the overrunning clutch 9 and the output end 62 of the one-way clutch 6 and the torque-limiting aqueous medium fluid coupling 7
  • the input end 71 is coupled, the output end 72 of the torque-limiting aqueous medium fluid coupling 7 is coupled to the coupling gear 8, the coupling gear 8 is meshed with the input small ring gear 21, and the input small ring gear 21 is passed through the planet on the input carrier 23.
  • the gear 20 cooperates with the output large ring gear 22 and the input planet carrier 23
  • the output large ring gear 22 is coupled to the input gear 31 of the input gear pair 3, the output gear 32 of the input gear pair 3 and the input large ring gear 25 are coupled to the input ring gear 28, and the input large ring gear 25 is passed through the planet on the fixed carrier 24.
  • the gear 20 cooperates with the fixed carrier 24 and the output gear 26, the fixed carrier 24 is fixed to the fixed component, the output gear 26 is coupled to the input 61 of the one-way clutch 6, and the input ring gear 28 is passed through the output carrier 27.
  • the planetary gear 20 cooperates with the output carrier 27 and the input gear 29, and the output carrier 27 is coupled to the output shaft 4.
  • the input small ring gear 21 and the input carrier 23 converge the planetary gears 20 transmitted to the respective powers through the input carrier 23 to the output large ring gear 22, because the torque-limiting type aqueous medium fluid coupling 7 passes through the coupling gear 8 and The input small ring gear 21 is coupled, so that the rotational speed of the input small ring gear 21 can be constantly changed with the change of the rotational speed of the torque-limiting aqueous medium fluid coupling 7, so that the rotational speed of the output large ring gear 22 also changes.
  • the input power is split into two paths through the input shaft 1, one is transmitted to the input carrier 23, the other is transmitted to the output gear pair 10 and then split into two paths, one pass through the overrunning clutch 9, the torque-limiting aqueous medium fluid coupling 7 and
  • the coupling gear 8 is transmitted to the input small ring gear 21, the other path is transmitted to the input gear 29 through the coupling shaft 5, the input small ring gear 21, and the input carrier 23 converges the respective powers transmitted through the planetary gears 20 on the input carrier 23.
  • the output large ring gear 22 the output large ring gear 22 is split into two paths through the input gear pair 3, and is transmitted to the input ring gear 28 at one time. At this time, the input ring gear 28 and the input gear 29 are transmitted to the respective power through the output.
  • the planetary gears 20 on the carrier 27 merge with the output carrier 27, and the output carrier 27 is transmitted to the output shaft 4 of the present invention, thereby realizing the external output of the engine power through the output shaft 4.
  • the input small ring gear 21 and the input carrier 23 converge the planetary gears 20 transmitted to the respective powers through the input carrier 23 to the output large ring gear 22, and output the large ring gear 22 and repeat the above process to transmit
  • the rotational speed to the input ring gear 28 is constantly changing, the input ring gear 28 and the input gear 29 converge the respective power transmitted through the planetary gear 20 on the output carrier 27 to the output carrier 27, and the output carrier 27 is transmitted to the present.
  • Invented output shaft 4 thereby achieving power through the output shaft 4 External output.
  • the rotational speed input to the ring gear 28 varies with the input power or the driving resistance of the vehicle.
  • the input power, the input rotational speed and the load of the engine are unchanged, 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 4 is zero, and the input power of the engine passes through the input shaft 1
  • the split is two ways, one way is transmitted to the input planet carrier 23, the other way is transmitted to the output gear pair 10 and then split into two paths, one pass through the overrunning clutch 9, the torque-limiting aqueous medium hydraulic coupling 7 and the coupling gear 8 to the input
  • the small ring gear 21, the other path is transmitted to the input gear 29 through the coupling shaft 5, the input small ring gear 21, the input carrier 23, and the planetary gears 20 transmitted to the respective powers passing through the input carrier 23 are merged to the output large ring gear 22
  • the output large ring gear 22 is split into two paths through the input gear pair 3, and is transmitted to the input ring gear 28 all the way.
  • the input ring gear 28 and the input gear 29 transmit the power to the respective planets passing through the output carrier 27.
  • the gear 20 merges with the output carrier 27, and the output carrier 27 is transmitted to the output shaft 4 of the present invention, thereby realizing the external output of the engine power through the output shaft 4.
  • the planetary gear 20 input to the carrier 23 merges with the output large ring gear 22, and the large ring gear 22 is output to repeat the above process, so that the rotational speed transmitted to the input ring gear 28 is constantly changed, and the input ring gear 28 and the input gear 29 are transmitted.
  • the respective powers are merged through the planetary gears 20 on the output carrier 27 to the output carrier 27, and the output carrier 27 is transmitted to the output shaft 4 of the present invention, and the torque transmitted to the output shaft 4 is transmitted through the transmission system.
  • the vehicle continues to accelerate, and the rotational speed of the output end 72 of the torque-type aqueous medium fluid coupling 7 is gradually increased, and the input small ring gear associated therewith is gradually increased.
  • the rotational speed of 21 is also gradually increased, so that the rotational speeds of the input small ring gear 21, the input ring gear 28, and the output shaft 4 are continuously increased.

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Abstract

一种复合式限矩型水介质液力偶合器及具有该复合式限矩型水介质液力偶合器的起动器，其中输入轴（1）与起动齿轮副（13）以及超越离合器（14）联接，超越离合器（14）与第一单向离合器（10）以及起动机齿轮副（12）联接，第一单向离合器（10）与输入小齿轮（21）联接，输出行星架（22）与联接架（7）以及输出齿轮副（9）联接，联接轴（8）与空挂档机构（6）、输出齿轮副（9）以及电磁离合器（11）联接，电磁离合器（11）与起动齿轮副（13）联接，空挂档机构（7）与输出轴（5）联接，联接架（7）与输入齿圈（28）联接，输出齿圈（27）与输入行星架（25）联接，输出小齿圈（24）与第二单向离合器（4）联接，第二单向离合器（4）以及第一单向离合器（10）与限矩型水介质液力偶合器（3）联接，限矩型水介质液力偶合器（3）与输入大齿轮（23）联接。

Description

一种复合式限矩型水介质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式限矩型水介质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，节能高效的复合式限矩型水介质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：
一种复合式限矩型水介质液力偶合器以及起动器，包括输入轴(1)、限矩型水介质液力偶合器(3)、第二单向离合器(4)、输出轴(5)、空挂档机构(6)、联接架(7)、联接轴(8)、输出齿轮副(9)、第一单向离合器(10)、电磁离合器(11)、起动机齿轮副(12)、起动齿轮副(13)、超越离合器(14)，所述的输入轴(1)与输出轴(5)之间设有行星齿轮(20)、输入小齿轮(21)、输出行星架(22)、输入大齿轮(23)、输出小齿圈(24)、输入行星架(25)、固定齿圈(26)、输出齿圈(27)、输入齿圈(28)、固定行星架(29),输入轴(1)与起动齿轮副(13)的输出齿轮(132)以及超越离合器(14)的输入端(141)联接,超越离合器(14)的输出端(142)与第一单向离合器(10)的输入端(101)以及起动机齿轮副(12)的输出齿轮(122)联接,起动机齿轮副(12)的输出齿轮(122)与起动机齿轮副(12)的输入齿轮(121)相互配合工作，第一单向离合器(10)的输入端(101)与输入小齿轮(21)联接，输入小齿轮(21)通过输出行星架(22)上的行星齿轮(20)与输出行星架(22)、输入大齿轮(23)相互配合工作，输出行星架(22)与联接架(7)以及输出齿轮副(9)的输入齿轮(91)联接，联接轴(8)与空挂档机构(6)的输入端(61)、输出齿轮副(9)的输出齿轮(92)以及电磁离合器(11)的输入端(111)联接，电磁离合器(11)的输出齿轮(112)与起动齿轮副(13)的输入齿轮(131)联接，空挂档机构(7)的输出端(72)与输出轴(5)联接，联接架(7)与输入齿圈(28)联接，输入齿圈(28)通过固定行星架(29)上的行星齿轮(20)与输出齿圈(27)、固定行星架(29)相互配合工作，输出齿圈(27)与输入行星架(25)联接，输入行星架(25)通过其上的行星齿轮(20)与输出小齿圈(24)固定齿圈(26)相互配合工作，输出小齿圈(24)与第二单向离合器(4)的输入端(41)联接，第二单向离合器(4)的输出端(42)以及第一单向离合器(10)的输出端(102)与限矩型水介质液力偶合器(3)的输入端(31)联接，限矩型水介质液力偶合器(3)的输出端(32)与输入大齿轮(23)联接，固定行星架(29)与固定齿圈(26)联接，固定行星架(29)与固定元件联接。
一种复合式限矩型水介质液力偶合器，包括输入轴(1)、输入齿轮副(3)、输出轴(4)、联接轴(5)、单向离合器(6)、限矩型水介质液力偶合器(7)、联接齿轮(8)、超越离合器 (9)、输出齿轮副(10)，所述的输入轴(1)与输出轴(4)之间设有行星齿轮(20)、输入小齿圈(21)、输出大齿圈(22)、输入行星架(23)、固定行星架(24)、输入大齿圈(25)、输出齿轮(26)、输出行星架(27)、输入齿圈(28)、输入齿轮(29)，输入轴(1)与输入行星架(23)以及输出齿轮副(10)的输入齿轮(101)联接,输出齿轮副(10)的输出齿轮(102)与联接轴(5)以及超越离合器(9)的输入端(91)联接,超越离合器(9)的输出端(92)以及单向离合器(6)的输出端(62)与限矩型水介质液力偶合器(7)的输入端(71)联接,限矩型水介质液力偶合器(7)的输出端(72)与联接齿轮(8)联接,联接齿轮(8)与输入小齿圈(21)啮合,输入小齿圈(21)通过输入行星架(23)上的行星齿轮(20)与输出大齿圈(22)、输入行星架(23)相互配合工作，输出大齿圈(22)与输入齿轮副(3)的输入齿轮(31)联接,输入齿轮副(3)的输出齿轮(32)以及输入大齿圈(25)与输入齿圈(28)联接,输入大齿圈(25)通过固定行星架(24)上的行星齿轮(20)与固定行星架(24)、输出齿轮(26)相互配合工作，固定行星架(24)与固定元件固接,输出齿轮(26)与单向离合器(6)的输入端(61)联接,输入齿圈(28)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(29)相互配合工作，输出行星架(27)与输出轴(4)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。
所述限矩型水介质液力偶合器可以选择叶轮式液力变矩器代替。
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式限矩型水介质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，一种复合式限矩型水介质液力偶合器以及起动器，包括输入轴1、限矩型水介质液力偶合器3、第二单向离合器4、输出轴5、空挂档机构6、联接架7、联接轴8、输出齿轮副9、第一单向离合器10、电磁离合器11、起动机齿轮副12、起动齿轮副13、超越离合器14，所述的输入轴1与输出轴5之间设有行星齿轮20、输入小齿轮21、输出行星架22、输入大齿轮23、输出小齿圈24、输入行星架25、固定齿圈26、输出齿圈27、输入齿圈28、固定行星架29,输入轴1与起动齿轮副13的输出齿轮132以及超越离合器14的输入端141联接,超越离合器14的输出端142与第一单向离合器10的输入端101以及起动机齿轮副12的输出齿轮122联接,起动机齿轮副12的输出齿轮122与起动机齿轮副12的输入齿轮121相互配合工作，第一单向离合器10的输入端101与输入小齿轮21联接，输入小齿轮21通过输出行星架22上的行星齿轮20与输出行星架22、输入大齿轮23相互配合工作，输出行星架22与联接架7以及输出齿轮副9的输入齿轮91联接，联接轴8与空挂档机构6的输入端61、输出齿轮副9的输出齿轮92以及电磁离合器11的输入端111联接，电磁离合器11的输出齿轮112与起动齿轮副13的输入齿轮131联接，空挂档机构7的输出端72与输出轴5联接，联接架7与输入齿圈28联接，输入齿圈28通过固定行星架29上的行星齿轮20与输出齿圈27、固定行星架29相互配合工作，输出齿圈27与输入行星架25联接，输入行星架25通过其上的行星齿轮20与输出小齿圈24固定齿圈26相互配合工作，输出小齿圈24与第二单向离合器4的输入端41联接，第二单向离合器4的输出端42以及第一单向离合器10的输出端102与限矩型水介质液力偶合器3的输入端31联接，限矩型水介质液力偶合器3的输出端32与输入大齿轮23联接，固定行星架29与固定齿圈26联接，固定行星架29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12传递到第一单向离合器10，第一单向离合器10把传递到此的功率分流为两路，一路传递到输入小齿轮21，另一路通过限矩型水介质液力偶合器3传递到输入大齿轮23，输入小齿轮21、输入大齿轮23把传递到各自的功率通过输出行星架22上的行星齿轮20汇流于输出行星架22，输出行星架22再通过输出齿轮副9、联接轴8、电磁离合器11以及起动齿轮副13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，输入轴1把由发动机传递到此的功率通过超越离合器14，传递到第一单向离合器10，第一单向离合器10再分流为两路，一路传递到输入小齿轮21，另一路通过限矩型水介质液力偶合器3传递到输入大齿轮23，输入小齿轮21、输入大齿轮23把传递到各自的功率通过输出行星架22上的行星齿轮20汇流于输出行星架22，输出行星架22再分流为两路，一路通过输出齿轮副9、联接轴8以及空挂档机构6传递到本发明的输出轴5；另一路通过联接架7传递到输入齿圈28，输入齿圈28再通过固定行星架29上的行星齿轮20传递到输出齿圈27，输出齿圈27再传递到输入行星架25，输入行星架25通过其上的行星齿轮20传递到输出小齿圈24，输出小齿圈24再通过第二单向离合器4以及限矩型水介质液力偶合器3传递到输入大齿轮23，输入小齿轮21、输入大齿轮23把传递到各自的功率通过输出行星架22上的行星齿轮20汇流于输出行星架22，输出行星架22则在各个元件之间不断地进行变速的反复循环，其中，限矩型水介质液力偶合器3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，从而使输出行星架22的输出转速也不断地变化，并且通过输出齿轮副9、联接轴8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，输入大齿轮23、输出行星架22以及输出轴5上的扭矩随其转速的变化而变化，转速越低，传递到输入大齿轮23、输出行星架22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式限矩型水介质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12传递到第一单向离合器10，第一单向离合器10把传递到此的功率分流为两路，一路传递到输入小齿轮21，另一路通过限矩型水介质液力偶合器3传递到输入大齿轮23，输入小齿轮21、输入大齿轮23把传递到各自的功率通过输出行星架22上的行星齿轮20汇流于输出行星架22，输出行星架22再通过输出齿轮副9、联接轴8、电磁离合器11以及起动齿轮副13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，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，输入轴1把由发动机传递到此的功率通过超越离合器14，传递到第一单向离合器10，第一单向离合器10再分流为两路，一路传递到输入小齿轮21，另一路通过限矩型水介质液力偶合器3传递到输入大齿轮23，输入小齿轮21、输入大齿轮23把传递到各自的功率通过输出行星架22上的行星齿轮20汇流于输出行星架22，输出行星架22再分流为两路，一路通过输出齿轮副9、联接轴8以及空挂档机构6传递到本发明的输出轴5；另一路通过联接架7传递到输入齿圈28，输入齿圈28再通过固定行星架29上的行星齿轮20传递到输出齿圈27，输出齿圈27再传递到输入行星架25，输入行星架25通过其上的行星齿轮20传递到输出小齿圈24，输出小齿圈24再通过第二单向离合器4以及限矩型水介质液力偶合器3传递到输入大齿轮23，输入小齿轮21、输入大齿轮23把传递到各自的功率通过输出行星架22上的行星齿轮20汇流于输出行星架22，输出行星架22则在各个元件之间不断地进行变速的反复循环，其中，限 矩型水介质液力偶合器3的输出转速不断地随着行驶阻力的变化而无级地变速，从而使输出行星架22的输出转速也不断地变化，并且通过输出齿轮副9、联接轴8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，一种复合式限矩型水介质液力偶合器，包括输入轴1、输入齿轮副3、输出轴4、联接轴5、单向离合器6、限矩型水介质液力偶合器7、联接齿轮8、超越离合器9、输出齿轮副10，所述的输入轴1与输出轴4之间设有行星齿轮20、输入小齿圈21、输出大齿圈22、输入行星架23、固定行星架24、输入大齿圈25、输出齿轮26、输出行星架27、输入齿圈28、输入齿轮29，输入轴1与输入行星架23以及输出齿轮副10的输入齿轮101联接,输出齿轮副10的输出齿轮102与联接轴5以及超越离合器9的输入端91联接,超越离合器9的输出端92以及单向离合器6的输出端62与限矩型水介质液力偶合器7的输入端71联接,限矩型水介质液力偶合器7的输出端72与联接齿轮8联接,联接齿轮8与输入小齿圈21啮合,输入小齿圈21通过输入行星架23上的行星齿轮20与输出大齿圈22、输入行星架23相互配合工作，输出大齿圈22与输入齿轮副3的输入齿轮31联接,输入齿轮副3的输出齿轮32以及输入大齿圈25与输入齿圈28联接,输入大齿圈25通过固定行星架24上的行星齿轮20与固定行星架24、输出齿轮26相互配合工作，固定行星架24与固定元件固接,输出齿轮26与单向离合器6的输入端61联接,输入齿圈28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29相互配合工作，输出行星架27与输出轴4联接。
输入小齿圈21、输入行星架23把传递到各自的功率通过输入行星架23上的行星齿轮20汇流于输出大齿圈22，由于限矩型水介质液力偶合器7通过联接齿轮8与输入小齿圈21联接,所以输入小齿圈21的转速可以不断地随着限矩型水介质液力偶合器7转速的变化而变化,从而使输出大齿圈22的转速也随之变化。
输入功率经过输入轴1分流为两路，一路传递到输入行星架23，另一路传递到输出齿轮副10再分流为两路，一路经过超越离合器9、限矩型水介质液力偶合器7以及联接齿轮8传递到输入小齿圈21，另一路通过联接轴5传递到输入齿轮29，输入小齿圈21、输入行星架23把传递到各自的功率通过输入行星架23上的行星齿轮20汇流于输出大齿圈22，输出大齿圈22再通过输入齿轮副3分流为两路，一路传递到输入齿圈28，此时，输入齿圈28与输入齿轮29把传递到各自的功率通过输出行星架27上的行星齿轮20汇流于输出行星架27，输出行星架27则传递至本发明的输出轴4,从而实现了把发动机的功率通过输出轴4对外输出。
当发动机的输入功率增大或者输出轴4的阻力减少时，另一路传递到输入大齿圈25的功率随之而增大，输入大齿圈25则通过固定行星架24上的行星齿轮20把功率传递到输出齿轮26，输出齿轮26再通过单向离合器6、限矩型水介质液力偶合器7以及联接齿轮8传递到输入小齿圈21，即输入小齿圈21的输入功率随之而增大，输入小齿圈21、输入行星架23把传递到各自的功率通过输入行星架23上的行星齿轮20汇流于输出大齿圈22，输出大齿圈22再重复上述过程，使传递到输入齿圈28上的转速不断变化，输入齿圈28与输入齿轮29把传递到各自的功率通过输出行星架27上的行星齿轮20汇流于输出行星架27，输出行星架27则传递到本发明的输出轴4,从而实现了把发动机的功率通过输出轴4 对外输出。
对于本发明，当输入轴1的转速不变，输入齿圈28上的转速，则随着车辆行输入功率或者驶阻力的不同而变化，阻力越低，传递到输入齿圈28上的转速就越高，反之，则越低，从而实现本发明能随着车辆输入功率或者行驶阻力的不同而改变速度的复合式限矩型水介质液力偶合器。
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4的转速为零，发动机的输入功率经过输入轴1分流为两路，一路传递到输入行星架23，另一路传递到输出齿轮副10再分流为两路，一路经过超越离合器9、限矩型水介质液力偶合器7以及联接齿轮8传递到输入小齿圈21，另一路通过联接轴5传递到输入齿轮29，输入小齿圈21、输入行星架23把传递到各自的功率通过输入行星架23上的行星齿轮20汇流于输出大齿圈22，输出大齿圈22再通过输入齿轮副3分流为两路，一路传递到输入齿圈28，此时，输入齿圈28与输入齿轮29把传递到各自的功率通过输出行星架27上的行星齿轮20汇流于输出行星架27，输出行星架27则传递至本发明的输出轴4,从而实现了把发动机的功率通过输出轴4对外输出。
当传递到输出轴4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4的阻力减少时，另一路传递到输入大齿圈25的功率随之而增大，输入大齿圈25则通过固定行星架24上的行星齿轮20把功率传递到输出齿轮26，输出齿轮26再通过单向离合器6、限矩型水介质液力偶合器7以及联接齿轮8传递到输入小齿圈21，即输入小齿圈21的输入功率随之而增大，输入小齿圈21、输入行星架23把传递到各自的功率通过输入行星架23上的行星齿轮20汇流于输出大齿圈22，输出大齿圈22再重复上述过程，使传递到输入齿圈28上的转速不断变化，输入齿圈28与输入齿轮29把传递到各自的功率通过输出行星架27上的行星齿轮20汇流于输出行星架27，输出行星架27则传递到本发明的输出轴4,当传递到输出轴4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，限矩型水介质液力偶合器7的输出端72的转速也逐渐升高，与之相关联的输入小齿圈21的转速也随之逐渐升高，从而使输入小齿圈21、输入齿圈28以及输出轴4上的转速随之增加而不断地升高。

Claims (2)

  1. 一种复合式限矩型水介质液力偶合器以及起动器，包括输入轴(1)、限矩型水介质液力偶合器(3)、第二单向离合器(4)、输出轴(5)、空挂档机构(6)、联接架(7)、联接轴(8)、输出齿轮副(9)、第一单向离合器(10)、电磁离合器(11)、起动机齿轮副(12)、起动齿轮副(13)、超越离合器(14)，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)、输入小齿轮(21)、输出行星架(22)、输入大齿轮(23)、输出小齿圈(24)、输入行星架(25)、固定齿圈(26)、输出齿圈(27)、输入齿圈(28)、固定行星架(29),输入轴(1)与起动齿轮副(13)的输出齿轮(132)以及超越离合器(14)的输入端(141)联接,超越离合器(14)的输出端(142)与第一单向离合器(10)的输入端(101)以及起动机齿轮副(12)的输出齿轮(122)联接,起动机齿轮副(12)的输出齿轮(122)与起动机齿轮副(12)的输入齿轮(121)相互配合工作，第一单向离合器(10)的输入端(101)与输入小齿轮(21)联接，输入小齿轮(21)通过输出行星架(22)上的行星齿轮(20)与输出行星架(22)、输入大齿轮(23)相互配合工作，输出行星架(22)与联接架(7)以及输出齿轮副(9)的输入齿轮(91)联接，联接轴(8)与空挂档机构(6)的输入端(61)、输出齿轮副(9)的输出齿轮(92)以及电磁离合器(11)的输入端(111)联接，电磁离合器(11)的输出齿轮(112)与起动齿轮副(13)的输入齿轮(131)联接，空挂档机构(7)的输出端(72)与输出轴(5)联接，联接架(7)与输入齿圈(28)联接，输入齿圈(28)通过固定行星架(29)上的行星齿轮(20)与输出齿圈(27)、固定行星架(29)相互配合工作，输出齿圈(27)与输入行星架(25)联接，输入行星架(25)通过其上的行星齿轮(20)与输出小齿圈(24)固定齿圈(26)相互配合工作，输出小齿圈(24)与第二单向离合器(4)的输入端(41)联接，第二单向离合器(4)的输出端(42)以及第一单向离合器(10)的输出端(102)与限矩型水介质液力偶合器(3)的输入端(31)联接，限矩型水介质液力偶合器(3)的输出端(32)与输入大齿轮(23)联接，固定行星架(29)与固定齿圈(26)联接，固定行星架(29)与固定元件联接。
  2. 一种复合式限矩型水介质液力偶合器，包括输入轴(1)、输入齿轮副(3)、输出轴(4)、联接轴(5)、单向离合器(6)、限矩型水介质液力偶合器(7)、联接齿轮(8)、超越离合器(9)、输出齿轮副(10)，其特征在于：所述的输入轴(1)与输出轴(4)之间设有行星齿轮(20)、输入小齿圈(21)、输出大齿圈(22)、输入行星架(23)、固定行星架(24)、输入大齿圈(25)、输出齿轮(26)、输出行星架(27)、输入齿圈(28)、输入齿轮(29)，输入轴(1)与输入行星架(23)以及输出齿轮副(10)的输入齿轮(101)联接,输出齿轮副(10)的输出齿轮(102)与联接轴(5)以及超越离合器(9)的输入端(91)联接,超越离合器(9)的输出端(92)以及单向离合器(6)的输出端(62)与限矩型水介质液力偶合器(7)的输入端(71)联接,限矩型水介质液力偶合器(7)的输出端(72)与联接齿轮(8)联接,联接齿轮(8)与输入小齿圈(21)啮合,输入小齿圈(21)通过输入行星架(23)上的行星齿轮(20)与输出大齿圈(22)、输入行星架(23)相互配合工作，输出大齿圈(22)与输入齿轮副(3)的输入齿轮(31)联接,输入齿轮副(3)的输出齿轮(32)以及输入大齿圈(25)与输入齿圈(28)联接,输入大齿圈(25)通过固定行星架(24)上的行星齿轮(20)与固定行星架(24)、输出齿轮(26)相互配合工作，固定行星架(24)与固定元件固接,输出齿轮(26)与单向离合器(6)的输入端(61)联接,输入齿圈(28)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(29)相互配合工作，输出行星架(27)与输出轴(4)联接。
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