WO2017005187A1 - Composite variable speed hydraulic coupler and starter - Google Patents
Composite variable speed hydraulic coupler and starter Download PDFInfo
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- WO2017005187A1 WO2017005187A1 PCT/CN2016/088751 CN2016088751W WO2017005187A1 WO 2017005187 A1 WO2017005187 A1 WO 2017005187A1 CN 2016088751 W CN2016088751 W CN 2016088751W WO 2017005187 A1 WO2017005187 A1 WO 2017005187A1
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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
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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
Definitions
- the invention belongs to the field of fluid coupling and starting, and more particularly to a compound speed regulating fluid coupling and a 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 speed regulating 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.
- Composite speed regulating fluid coupling and starter comprising input shaft (1), variable speed fluid coupling (3), second one-way clutch (4), output shaft (5), hanging Gear mechanism (6), input gear pair (7), output gear (8), electromagnetic clutch (9), output gear pair (10), first one-way clutch (11), starter gear pair (12), starting a gear pair (13) and an overrunning clutch (14), wherein the input shaft (1) and the output shaft (5) are provided with a planetary gear (20), an input small ring gear (21), and an output carrier (22).
- 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 input small ring gear (21)
- the input end (111) of the first one-way clutch (11) and the output gear (122) of the starter gear pair (12) are coupled, the output end (112) of the first one-way clutch (11) and the output gear pair
- the input gear (101) of (10) is coupled, and the output gear (102) and output of the output gear pair (10) are connected.
- the gear pair (7) input gear (71) is coupled, and the output gear (122) of the starter gear pair (12) cooperates with the input gear (121) of the starter gear pair (12) to input the small ring gear (21)
- the planetary gear (20) on the output carrier (22) cooperates with the output carrier (22) and the input large ring gear (23) to output the input end of the carrier (22) and the empty gear mechanism (6).
- the planetary gear (20) on the planet carrier (27) cooperates with the fixed carrier (27) and the output ring gear (28), and the output ring gear (28) is coupled with the input carrier (24), and the input carrier (24) )
- the planetary gear (20) thereon cooperates with the fixed ring gear (25) and the output gear (26), and the fixed ring gear (25) is coupled with the fixed carrier (27) to fix the carrier (27) and fix it.
- a compound speed regulating fluid coupling comprises an input shaft (1), a variable speed fluid coupling (3), a one-way clutch (4), an output shaft (5), an input gear pair (6), Output gear pair (7), overrunning clutch (8), the input shaft (1) Between the output shaft (5), a planetary gear (20), an input large gear (21), an output coupling carrier (22), an input pinion (23), an output gear (24), an input gear (25), Fixed planet carrier (26), output planet carrier (27), input large ring gear (28), input small ring gear (29), input shaft (1) and input large gear (21) and overrunning clutch (8) input The end (81) is coupled, the input end (81) of the overrunning clutch (8) is coupled with the input small ring gear (29), and the input end (31) of the variable speed fluid coupling (3) and the overrunning clutch (8) The output end (82) and the output end (42) of the one-way clutch (4) are coupled, the input end (41) of the one-way clutch (4) is coupled with the output gear (24), and the variable speed
- the output coupling carrier (22) is coupled to the input gear (71) of the output gear pair (7), and the output gear (72) of the output gear pair (7) and the input gear of the input gear pair (6) are 61) Coupling, input gear pair (6) output gear (62) and input gear (2 5) and the input large ring gear (28) is coupled, and the input gear (25) cooperates with the output gear (24) and the fixed planet carrier (26) through the planetary gear (20) on the fixed planet carrier (26) to fix the planet.
- the frame (26) is fixed to the fixing component, and the input large ring gear (28) cooperates with the output carrier (27) and the input small ring gear (29) through the planetary gears (20) on the output carrier (27).
- the output planet carrier (27) is coupled to the output shaft (5).
- 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.
- variable speed fluid coupling can be replaced by a radial turbine 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 variable speed 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 speed regulating fluid coupling and a starter include an input shaft 1 , a variable speed fluid coupling 3 , a second one-way clutch 4 , an output shaft 5 , and an idle gear Mechanism 6, input gear pair 7, output gear 8, electromagnetic clutch 9, output gear pair 10, first one-way clutch 11, starter gear pair 12, start gear pair 13, overrunning clutch 14, said input shaft 1 and A planetary gear 20, an input small ring gear 21, an output carrier 22, an input large ring gear 23, an input carrier 24, a fixed ring gear 25, an output gear 26, a fixed carrier 27, and an output ring gear are disposed between the output shafts 5.
- the input ring gear 29, the input shaft 1 is coupled with 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 input small ring gear 21, the first one-way clutch 11
- the input end 111 and the output gear 122 of the starter gear pair 12 are coupled, the output end 112 of the first one-way clutch 11 is coupled to the input gear 101 of the output gear pair 10, and the output gear 102 and the input gear pair 7 of the output gear pair 10 are input.
- the gear 71 is coupled to the output gear of the starter gear pair 12 122 cooperates with the input gear 121 of the starter gear pair 12, and the input small ring gear 21 cooperates with the output carrier 22 and the input large ring gear 23 through the planetary gear 20 on the output carrier 22, and outputs the planet carrier 22 and
- the input end 61 of the empty gear mechanism 6 and the input ring gear 29 are coupled, the output end 62 of the neutral gear mechanism 6 is coupled to the output shaft 5, the input ring gear 29 is meshed with the output gear 8, and the input gear 8 is input to the electromagnetic clutch 9.
- the end 91 is coupled, the output end 92 of the electromagnetic clutch 9 and the input gear pair 13 are coupled to the input gear 131, and the input ring gear 29 cooperates with the fixed carrier 27 and the output ring gear 28 through the planetary gear 20 on the fixed carrier 27.
- the output ring gear 28 is coupled to the input carrier 24, and the input carrier 24 cooperates with the fixed ring gear 25 and the output gear 26 through the planetary gear 20 thereon, and the fixed ring gear 25 is coupled with the fixed carrier 27 to fix the carrier 27 Coupling with the fixed element, the output gear 26 is coupled to the input 41 of the second one-way clutch 4, the output 42 of the second one-way clutch 4, and the output gear 72 of the input gear pair 7 and the variable speed fluid coupling 3 Input 31 Then, the output speed of the hydraulic coupling 3 input end 32 and the ring gear 23 is coupled.
- the idle gear mechanism 6 Before the engine is started, the idle gear mechanism 6 is disengaged and the electromagnetic clutch 9 is engaged.
- the input power of the starter is transmitted to the overrunning clutch 14 through the starter gear pair 12, and the overrunning clutch 14 is split into two paths, one pass and the same to the input small teeth.
- the other side of the ring 21 is transmitted to the input large ring gear 23 through the first one-way clutch 11, the output gear pair 10, the input gear pair 7, and the variable speed type fluid coupling 3, and the input small ring gear 21 and the input large ring gear 23
- the planetary gears 20 that are transmitted to the respective powers through the output carrier 22 are merged to the output carrier 22, and the output carrier 22 is transmitted to the input shaft through the input ring gear 29, the output gear 8, the electromagnetic clutch 9, and the start gear pair 13. 1, then transferred to the engine crankshaft, resulting from The engine is started when the power is sufficient to overcome the engine starting resistance.
- the idle gear mechanism 6 After the engine is started, the idle gear mechanism 6 is engaged, the electromagnetic clutch 9 is disengaged, the input shaft 1 transmits the power transmitted thereto by the engine to the overrunning clutch 14, and the overrunning clutch 14 is divided into two paths, one pass and the same to the input small teeth.
- the other side of the ring 21 is transmitted to the input large ring gear 23 through the first one-way clutch 11, the output gear pair 10, the input gear pair 7, and the variable speed type fluid coupling 3, and the input small ring gear 21 and the input large ring gear 23
- the planetary gears 20 that are transmitted to the respective powers through the output carrier 22 are merged to the output carrier 22, and the output carrier 22 is split into two paths, one way being transmitted to the output shaft 5 of the present invention through the idle gear mechanism 6; Passing all the way to the input ring gear 29, the input ring gear 29 is transmitted to the output ring gear 28 via the planet gears 20 on the fixed planet carrier 27, the output ring gear 28 is transferred to the input planet carrier 24, through which the input planet carrier 24 passes.
- the planetary gear 20 is transmitted to the output gear 26, and the output gear 26 is transmitted to the input large ring gear 23 through the second one-way clutch 4 and the variable speed type fluid coupling 3, and the input small ring gear 21 and the input large ring gear 23 Passed to each
- the self-power is converge on the output carrier 22 through the planetary gears 20 on the output carrier 22, and the output carrier 22 continuously repeats the shifting between the respective components, wherein the output of the variable speed fluid coupling 3
- the rotational speed continuously shifts steplessly as the input power and the running resistance change, so that the output rotational speed of the output carrier 22 also constantly changes, and is transmitted to the output shaft 5 of the present invention through the neutral gear mechanism 6, thereby realizing The power of the engine is externally output through the output shaft 5.
- the torque input to the large ring 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 is transmitted to the input large ring gear 23,
- the torque on the output planet carrier 22 and the output shaft 5 is larger, and vice versa, so that the composite speed-regulating fluid coupling and the starter that can change the torque and speed according to the driving resistance of the present invention are realized. .
- the idle gear mechanism 6 is disengaged, the electromagnetic clutch 9 is engaged, and the engine speed is zero.
- the starter is started, the input power of the starter is transmitted to the overrunning clutch 14 through the starter gear pair 12, beyond The clutch 14 is further divided into two paths, one pass through to the input small ring gear 21, and the other path is transmitted to the input through the first one-way clutch 11, the output gear pair 10, the input gear pair 7, and the variable speed fluid coupling 3.
- the large ring gear 23, the input small ring gear 21, the input large ring gear 23, and the planetary gears 20 transmitted to the respective powers passing through the output carrier 22 are merged to the output carrier 22, and the output carrier 22 is passed through the input ring gear 29,
- the output gear 8, the electromagnetic clutch 9 and the starter gear pair 13 are 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 unchanged, that is, the speed and torque of the input shaft 1 are constant.
- the idle gear mechanism 6 is engaged, the electromagnetic clutch 9 is separated, and the input shaft 1 is
- the power transmitted to the engine is transmitted to the overrunning clutch 14, and the overrunning clutch 14 is split into two paths, one pass through to the input small ring gear 21, and the other pass through the first one-way clutch 11, the output gear pair 10, and the input gear pair. 7 and the variable speed type fluid coupling 3 are transmitted to the input large ring gear 23, the input small ring gear 21, the input large ring gear 23, and the planetary gears 20 transmitted to the respective powers passing through the output carrier 22 are merged to the output carrier.
- the output planet carrier 22 is split into two paths, one is transmitted to the output shaft 5 of the present invention through the air-gear mechanism 6; the other is transmitted to the input ring gear 29, and the input ring gear 29 is passed through the fixed carrier 27.
- the planetary gear 20 is transmitted to the output ring gear 28, the output ring gear 28 is transmitted to the input carrier 24, the input carrier 24 is transmitted to the output gear 26 through the planetary gear 20 thereon, and the output gear 26 is passed through the second single
- the clutch 4 and the variable speed fluid coupling 3 are transmitted to the input large ring gear 23, the input small ring gear 21, and the input large ring gear 23 converge the planetary gears 20 transmitted to the respective powers through the output carrier 22 to the output planet.
- the frame 22 and the output carrier 22 continuously perform repeated cycles of shifting between the respective components, wherein the output speed of the variable speed fluid coupling 3 is not
- the ground speed is steplessly shifted as the running resistance changes, so that the output rotational speed of the output carrier 22 is also constantly changed, and is transmitted to the output shaft 5 of the present invention through the neutral gear mechanism 6, thereby causing the output shaft 5
- the torque decreases as the speed increases.
- Embodiment 2 is a diagrammatic representation of Embodiment 1:
- a composite speed regulating fluid coupling includes an input shaft 1, a variable speed fluid coupling 3, a one-way clutch 4, an output shaft 5, an input gear pair 6, and an output gear pair. 7.
- Overrunning clutch 8 between the input shaft 1 and the output shaft 5, a planetary gear 20, an input large gear 21, an output coupling carrier 22, an input pinion 23, an output gear 24, an input gear 25, and a fixed planet are provided.
- the frame 26, the output carrier 27, the input large ring gear 28, the input small ring gear 29, the input shaft 1 is coupled to the input large gear 21 and the input end 81 of the overrunning clutch 8, the input end 81 of the overrunning clutch 8 and the input small ring gear 29, the input end 31 of the variable speed hydraulic coupling 3 is coupled with the output end 82 of the overrunning clutch 8 and the output end 42 of the one-way clutch 4, and the input end 41 of the one-way clutch 4 is coupled with the output gear 24 to adjust the speed
- the output end 32 of the type fluid coupling 3 is coupled to the input pinion 23, and the input pinion 23 cooperates with the output coupling carrier 22 and the input large gear 21 through the planetary gear 20 on the output coupling carrier 22, and outputs the coupled planet.
- the frame 22 is coupled to the input gear 71 of the output gear pair 7
- the output gear 72 of the output gear pair 7 is coupled to the input gear 61 of the input gear pair 6,
- the output gear 62 of the input gear pair 6 is coupled to the input gear 25 and the input large ring gear 28, and the input gear 25 is passed through the fixed carrier 26.
- the planetary gear 20 cooperates with the output gear 24 and the fixed carrier 26 to fix the fixed carrier 26 and the fixed component.
- the input large ring gear 28 passes through the planetary gear 20 on the output carrier 27 and the output carrier 27, and the input small teeth.
- the rings 29 cooperate with each other and the output carrier 27 is coupled to the output shaft 5.
- the input large gear 21 and the input pinion 23 converge the planetary gears 20 transmitted to the respective powers through the output coupling carrier 22 to the output coupling carrier 22, since the variable speed fluid coupling 3 is coupled to the input pinion 23, Therefore, the rotational speed of the input pinion 23 can be constantly changed as the rotational speed of the variable speed fluid coupling 3 changes, so that the rotational speed of the output coupled carrier 22 also changes.
- the input power is split into two paths through the input shaft 1, one is transmitted to the input large gear 21, the other is divided into two through the overrunning clutch 8, and one is transmitted to the input pinion 23 through the variable speed fluid coupling 3, and the other path is passed. It is transmitted to the input small ring gear 29, and the input large gear 21 and the input pinion 23 converge the planetary gears 20 transmitted to the respective powers through the output coupling carrier 22 to the output coupling carrier 22, and the output coupling planet carrier 22 passes through the output.
- the gear pair 7 is transmitted to the input gear pair 6, and the input gear pair 6 is divided into two paths, one way is transmitted to the input large ring gear 28, at this time, the input large ring gear 28 and the input small ring gear 29 are transmitted to their respective powers.
- the planetary gears 20 on the output carrier 27 merge with the output carrier 27, and the output carrier 27 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 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 flow is divided into two paths, one way is transmitted to the input large gear 21, the other way is divided into two by the overrunning clutch 8, one is transmitted to the input pinion 23 through the variable speed fluid coupling 3, and the other is transmitted to the input small ring gear. 29.
- the input bull gear 21 and the input pinion 23 converge the planetary gears 20 that are transmitted to the respective powers through the output coupling carrier 22 to the output coupling carrier 22, and the output coupled carrier 22 is then transmitted to the input through the output gear pair 7.
- the gear pair 6 and the input gear pair 6 are split into two paths, one way to the input large ring gear 28, at which time the input large ring gear 28 and the input small ring gear 29 are transmitted to their respective powers through the output carrier 27.
- the planetary gear 20 merges with the output carrier 27, and the output carrier 27 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 output coupling planet carrier 22 repeats the above process, so that the rotational speed transmitted to the input large ring gear 28 is constantly changing, and the input large ring gear 28 and the input small ring gear 29 are transmitted to their respective powers through the output planet carrier.
- the planet gears 20 on 27 converge on the output planet carrier 27, and the output planet carrier 27 is transmitted to the output shaft 5 of the present invention.
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Abstract
Description
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调速型液力偶合器以及起动器。The invention belongs to the field of fluid coupling and starting, and more particularly to a compound speed regulating fluid coupling and a starter for various ground vehicles, ships, railway locomotives and machine tools.
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。At present, 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.
发明内容Summary of the invention
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，节能高效的复合式调速型液力偶合器以及起动器。The invention overcomes the deficiencies of the prior art, and provides a compound speed regulating 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.
为了实现本发明的目的，本发明采用的技术方案以下：In order to achieve the object of the present invention, the technical solution adopted by the present invention is as follows:
一种复合式调速型液力偶合器以及起动器，包括输入轴(1)、调速型液力偶合器(3)、第二单向离合器(4)、输出轴(5)、空挂档机构(6)、输入齿轮副(7)、输出齿轮(8)、电磁离合器(9)、输出齿轮副(10)、第一单向离合器(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)、输入小齿圈(21)、输出行星架(22)、输入大齿圈(23)、输入行星架(24)、固定齿圈(25)、输出齿轮(26)、固定行星架(27)、输出齿圈(28)、输入齿圈(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)与输入小齿圈(21)、第一单向离合器(11)的输入端(111)以及起动机齿轮副(12)的输出齿轮(122)联接,第一单向离合器(11)的输出端(112)与输出齿轮副(10)的输入齿轮(101)联接,输出齿轮副(10)的输出齿轮(102)与输入齿轮副(7)输入齿轮(71)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，输入小齿圈(21)通过输出行星架(22)上的行星齿轮(20)与输出行星架(22)、输入大齿圈(23)相互配合工作，输出行星架(22)与空挂档机构(6)的输入端(61)以及输入齿圈(29)联接,空挂档机构(6)的输出端(62)与输出轴(5)联接，输入齿圈(29)与输出齿轮(8)啮合，输出齿轮(8)与电磁离合器(9)的输入端(91)联接,电磁离合器(9)的输出端(92)与起动齿轮副(13)输入齿轮(131)的联接,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)与输入行星架(24)联接,输入行星架(24)通过其上的行星齿轮(20)与固定齿圈(25)、输出齿轮(26)相互配合工作，固定齿圈(25)与固定行星架(27)联接,固定行星架(27)与固定元件联接，输出齿轮(26)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)以及输入齿轮副(7)的输出齿轮(72)与调速型液力偶合器(3)的输入端(31)联接，调速型液力偶合器(3)的输出端(32)与输入大齿圈(23)联接。Composite speed regulating fluid coupling and starter, comprising input shaft (1), variable speed fluid coupling (3), second one-way clutch (4), output shaft (5), hanging Gear mechanism (6), input gear pair (7), output gear (8), electromagnetic clutch (9), output gear pair (10), first one-way clutch (11), starter gear pair (12), starting a gear pair (13) and an overrunning clutch (14), wherein the input shaft (1) and the output shaft (5) are provided with a planetary gear (20), an input small ring gear (21), and an output carrier (22). , input large ring gear (23), input planet carrier (24), fixed ring gear (25), output gear (26), fixed planet carrier (27), output ring gear (28), input ring gear (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 input small ring gear (21) The input end (111) of the first one-way clutch (11) and the output gear (122) of the starter gear pair (12) are coupled, the output end (112) of the first one-way clutch (11) and the output gear pair The input gear (101) of (10) is coupled, and the output gear (102) and output of the output gear pair (10) are connected. The gear pair (7) input gear (71) is coupled, and the output gear (122) of the starter gear pair (12) cooperates with the input gear (121) of the starter gear pair (12) to input the small ring gear (21) The planetary gear (20) on the output carrier (22) cooperates with the output carrier (22) and the input large ring gear (23) to output the input end of the carrier (22) and the empty gear mechanism (6). (61) and the input ring gear (29) is coupled, the output end (62) of the idle gear mechanism (6) is coupled with the output shaft (5), the input ring gear (29) is meshed with the output gear (8), and the output gear ( 8) coupled with the input end (91) of the electromagnetic clutch (9), the output end (92) of the electromagnetic clutch (9) and the input gear (131) input gear (131), the input ring gear (29) is fixed The planetary gear (20) on the planet carrier (27) cooperates with the fixed carrier (27) and the output ring gear (28), and the output ring gear (28) is coupled with the input carrier (24), and the input carrier (24) ) The planetary gear (20) thereon cooperates with the fixed ring gear (25) and the output gear (26), and the fixed ring gear (25) is coupled with the fixed carrier (27) to fix the carrier (27) and fix it. Component connection, output gear (26) and second single The input end (41) of the clutch (4) is coupled, the output end (42) of the second one-way clutch (4), and the output gear (72) of the input gear pair (7) and the variable speed fluid coupling (3) The input end (31) is coupled, and the output end (32) of the variable speed fluid coupling (3) is coupled to the input large ring gear (23).
一种复合式调速型液力偶合器，包括输入轴(1)、调速型液力偶合器(3)、单向离合器(4)、输出轴(5)、输入齿轮副(6)、输出齿轮副(7)、超越离合器(8)，所述的输入轴(1) 与输出轴(5)之间设有行星齿轮(20)、输入大齿轮(21)、输出联接行星架(22)、输入小齿轮(23)、输出齿轮(24)、输入齿轮(25)、固定行星架(26)、输出行星架(27)、输入大齿圈(28)、输入小齿圈(29)，输入轴(1)与输入大齿轮(21)以及超越离合器(8)的输入端(81)联接,超越离合器(8)的输入端(81)与输入小齿圈(29)联接,调速型液力偶合器(3)的输入端(31)与超越离合器(8)的输出端(82)以及单向离合器(4)的输出端(42)联接,单向离合器(4)的输入端(41)与输出齿轮(24)联接,调速型液力偶合器(3)的输出端(32)与输入小齿轮(23)联接,输入小齿轮(23)通过输出联接行星架(22)上的行星齿轮(20)与输出联接行星架(22)、输入大齿轮(21)相互配合工作，输出联接行星架(22)与输出齿轮副(7)的输入齿轮(71)联接,输出齿轮副(7)的输出齿轮(72)与输入齿轮副(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(25)以及输入大齿圈(28)联接,输入齿轮(25)通过固定行星架(26)上的行星齿轮(20)与输出齿轮(24)、固定行星架(26)相互配合工作，固定行星架(26)与固定元件固接,输入大齿圈(28)通过输出行星架(27)上的行星齿轮(20)与输出行星架(27)、输入小齿圈(29)相互配合工作，输出行星架(27)与输出轴(5)联接。A compound speed regulating fluid coupling comprises an input shaft (1), a variable speed fluid coupling (3), a one-way clutch (4), an output shaft (5), an input gear pair (6), Output gear pair (7), overrunning clutch (8), the input shaft (1) Between the output shaft (5), a planetary gear (20), an input large gear (21), an output coupling carrier (22), an input pinion (23), an output gear (24), an input gear (25), Fixed planet carrier (26), output planet carrier (27), input large ring gear (28), input small ring gear (29), input shaft (1) and input large gear (21) and overrunning clutch (8) input The end (81) is coupled, the input end (81) of the overrunning clutch (8) is coupled with the input small ring gear (29), and the input end (31) of the variable speed fluid coupling (3) and the overrunning clutch (8) The output end (82) and the output end (42) of the one-way clutch (4) are coupled, the input end (41) of the one-way clutch (4) is coupled with the output gear (24), and the variable speed type fluid coupling (3) The output end (32) is coupled to the input pinion (23), and the input pinion (23) is coupled to the output carrier (22) and the input large gear (21) through the output planetary gear (20) on the carrier (22). Working in cooperation with each other, the output coupling carrier (22) is coupled to the input gear (71) of the output gear pair (7), and the output gear (72) of the output gear pair (7) and the input gear of the input gear pair (6) are 61) Coupling, input gear pair (6) output gear (62) and input gear (2 5) and the input large ring gear (28) is coupled, and the input gear (25) cooperates with the output gear (24) and the fixed planet carrier (26) through the planetary gear (20) on the fixed planet carrier (26) to fix the planet. The frame (26) is fixed to the fixing component, and the input large ring gear (28) cooperates with the output carrier (27) and the input small ring gear (29) through the planetary gears (20) on the output carrier (27). The output planet carrier (27) is coupled to the output shaft (5).
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。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.
所述调速型液力偶合器可以选择向心涡轮式液力变矩器代替。The variable speed fluid coupling can be replaced by a radial turbine torque converter.
所述空挂档机构可以选择离合器代替。The air-locking mechanism can select a clutch instead.
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。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.
本发明具有以下的优点：The invention has the following advantages:
(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；(1) Most of the power of the present invention is transmitted by the ring gear, the planetary gear, the carrier, and the gear, so that the transmission power and the transmission efficiency are greatly improved, and the structure is simple and easier to maintain;
(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；(2) The torque and shifting of the present invention are automatically performed, enabling efficient transmission, and in addition to starting, the engine and the starter can be operated in an optimum range, compared with other transmissions, in the engine and On the premise that the starter is equivalent, it reduces the manufacturing cost of the engine and the starter;
(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；(3) 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;
(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；(4) 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. In addition, when the running resistance is increased, the vehicle can be automatically decelerated, and vice versa. Speed up, which is beneficial to improve the driving performance of the vehicle;
(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；(5) 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;
(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；(6) When the invention is started, it has the characteristics of automatic torque change and shifting, the input power is uninterrupted, and no impact phenomenon occurs, which can ensure stable engine starting, reduce noise, reduce starting wear of the engine, and prolong the starting motor and Battery life;
(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。(7) 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.
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调速型液力偶合器以及起动器。Further, the present invention is a composite variable speed fluid coupling and starter for various ground vehicles, ships, railway locomotives, and machine tools.
说明书附图1为本发明实施例一的结构图；BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a structural view of a first embodiment of the present invention;
说明书附图2为本发明实施例二的结构图；2 is a structural diagram of a second embodiment of the present invention;
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。In the figures, the 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.
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：The present invention will be further described in detail below in conjunction with the drawings and specific embodiments.
实施例一：Embodiment 1:
如图1中所示，一种复合式调速型液力偶合器以及起动器，包括输入轴1、调速型液力偶合器3、第二单向离合器4、输出轴5、空挂档机构6、输入齿轮副7、输出齿轮8、电磁离合器9、输出齿轮副10、第一单向离合器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、输入小齿圈21、输出行星架22、输入大齿圈23、输入行星架24、固定齿圈25、输出齿轮26、固定行星架27、输出齿圈28、输入齿圈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与输入小齿圈21、第一单向离合器11的输入端111以及起动机齿轮副12的输出齿轮122联接,第一单向离合器11的输出端112与输出齿轮副10的输入齿轮101联接,输出齿轮副10的输出齿轮102与输入齿轮副7输入齿轮71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，输入小齿圈21通过输出行星架22上的行星齿轮20与输出行星架22、输入大齿圈23相互配合工作，输出行星架22与空挂档机构6的输入端61以及输入齿圈29联接,空挂档机构6的输出端62与输出轴5联接，输入齿圈29与输出齿轮8啮合，输出齿轮8与电磁离合器9的输入端91联接,电磁离合器9的输出端92与起动齿轮副13输入齿轮131的联接,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与输入行星架24联接,输入行星架24通过其上的行星齿轮20与固定齿圈25、输出齿轮26相互配合工作，固定齿圈25与固定行星架27联接,固定行星架27与固定元件联接，输出齿轮26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以及输入齿轮副7的输出齿轮72与调速型液力偶合器3的输入端31联接，调速型液力偶合器3的输出端32与输入大齿圈23联接。As shown in FIG. 1 , a composite speed regulating fluid coupling and a starter include an input shaft 1 , a variable speed fluid coupling 3 , a second one-way clutch 4 , an output shaft 5 , and an idle gear Mechanism 6, input gear pair 7, output gear 8, electromagnetic clutch 9, output gear pair 10, first one-way clutch 11, starter gear pair 12, start gear pair 13, overrunning clutch 14, said input shaft 1 and A planetary gear 20, an input small ring gear 21, an output carrier 22, an input large ring gear 23, an input carrier 24, a fixed ring gear 25, an output gear 26, a fixed carrier 27, and an output ring gear are disposed between the output shafts 5. 28, the input ring gear 29, the input shaft 1 is coupled with 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 input small ring gear 21, the first one-way clutch 11 The input end 111 and the output gear 122 of the starter gear pair 12 are coupled, the output end 112 of the first one-way clutch 11 is coupled to the input gear 101 of the output gear pair 10, and the output gear 102 and the input gear pair 7 of the output gear pair 10 are input. The gear 71 is coupled to the output gear of the starter gear pair 12 122 cooperates with the input gear 121 of the starter gear pair 12, and the input small ring gear 21 cooperates with the output carrier 22 and the input large ring gear 23 through the planetary gear 20 on the output carrier 22, and outputs the planet carrier 22 and The input end 61 of the empty gear mechanism 6 and the input ring gear 29 are coupled, the output end 62 of the neutral gear mechanism 6 is coupled to the output shaft 5, the input ring gear 29 is meshed with the output gear 8, and the input gear 8 is input to the electromagnetic clutch 9. The end 91 is coupled, the output end 92 of the electromagnetic clutch 9 and the input gear pair 13 are coupled to the input gear 131, and the input ring gear 29 cooperates with the fixed carrier 27 and the output ring gear 28 through the planetary gear 20 on the fixed carrier 27. The output ring gear 28 is coupled to the input carrier 24, and the input carrier 24 cooperates with the fixed ring gear 25 and the output gear 26 through the planetary gear 20 thereon, and the fixed ring gear 25 is coupled with the fixed carrier 27 to fix the carrier 27 Coupling with the fixed element, the output gear 26 is coupled to the input 41 of the second one-way clutch 4, the output 42 of the second one-way clutch 4, and the output gear 72 of the input gear pair 7 and the variable speed fluid coupling 3 Input 31 Then, the output speed of the hydraulic coupling 3 input end 32 and the ring gear 23 is coupled.
发动机起动前，分离空挂档机构6，接合电磁离合器9，起动机的输入功率经过起动机齿轮副12传递到超越离合器14，超越离合器14再分流为两路，一路传通过递到输入小齿圈21，另一路通过第一单向离合器11、输出齿轮副10、输入齿轮副7以及调速型液力偶合器3传递到输入大齿圈23，输入小齿圈21、输入大齿圈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再通过输入齿圈29、输出齿轮8、电磁离合器9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。Before the engine is started, the idle gear mechanism 6 is disengaged and the electromagnetic clutch 9 is engaged. The input power of the starter is transmitted to the overrunning clutch 14 through the starter gear pair 12, and the overrunning clutch 14 is split into two paths, one pass and the same to the input small teeth. The other side of the ring 21 is transmitted to the input large ring gear 23 through the first one-way clutch 11, the output gear pair 10, the input gear pair 7, and the variable speed type fluid coupling 3, and the input small ring gear 21 and the input large ring gear 23 The planetary gears 20 that are transmitted to the respective powers through the output carrier 22 are merged to the output carrier 22, and the output carrier 22 is transmitted to the input shaft through the input ring gear 29, the output gear 8, the electromagnetic clutch 9, and the start gear pair 13. 1, then transferred to the engine crankshaft, resulting from The engine is started when the power is sufficient to overcome the engine starting resistance.
发动机起动后，接合空挂档机构6，分离电磁离合器9，输入轴1把由发动机传递到此的功率传递到超越离合器14，超越离合器14再分流为两路，一路传通过递到输入小齿圈21，另一路通过第一单向离合器11、输出齿轮副10、输入齿轮副7以及调速型液力偶合器3传递到输入大齿圈23，输入小齿圈21、输入大齿圈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，一路通过空挂档机构6传递到本发明的输出轴5；另一路传递到传递到输入齿圈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再传递到输入行星架24，输入行星架24通过其上的行星齿轮20传递到输出齿轮26，输出齿轮26再通过第二单向离合器4以及调速型液力偶合器3传递到输入大齿圈23，输入小齿圈21、输入大齿圈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，调速型液力偶合器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。After the engine is started, the idle gear mechanism 6 is engaged, the electromagnetic clutch 9 is disengaged, the input shaft 1 transmits the power transmitted thereto by the engine to the overrunning clutch 14, and the overrunning clutch 14 is divided into two paths, one pass and the same to the input small teeth. The other side of the ring 21 is transmitted to the input large ring gear 23 through the first one-way clutch 11, the output gear pair 10, the input gear pair 7, and the variable speed type fluid coupling 3, and the input small ring gear 21 and the input large ring gear 23 The planetary gears 20 that are transmitted to the respective powers through the output carrier 22 are merged to the output carrier 22, and the output carrier 22 is split into two paths, one way being transmitted to the output shaft 5 of the present invention through the idle gear mechanism 6; Passing all the way to the input ring gear 29, the input ring gear 29 is transmitted to the output ring gear 28 via the planet gears 20 on the fixed planet carrier 27, the output ring gear 28 is transferred to the input planet carrier 24, through which the input planet carrier 24 passes. The planetary gear 20 is transmitted to the output gear 26, and the output gear 26 is transmitted to the input large ring gear 23 through the second one-way clutch 4 and the variable speed type fluid coupling 3, and the input small ring gear 21 and the input large ring gear 23 Passed to each The self-power is converge on the output carrier 22 through the planetary gears 20 on the output carrier 22, and the output carrier 22 continuously repeats the shifting between the respective components, wherein the output of the variable speed fluid coupling 3 The rotational speed continuously shifts steplessly as the input power and the running resistance change, so that the output rotational speed of the output carrier 22 also constantly changes, and is transmitted to the output shaft 5 of the present invention through the neutral gear mechanism 6, thereby realizing The power of the engine is externally output through the output shaft 5.
对于本发明，当输入轴1的转速不变，输入大齿圈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，传递到输入大齿圈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调速型液力偶合器以及起动器。For the present invention, when the rotational speed of the input shaft 1 is constant, the torque input to the large ring 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 is transmitted to the input large ring gear 23, The torque on the output planet carrier 22 and the output shaft 5 is larger, and vice versa, so that the composite speed-regulating fluid coupling and the starter that can change the torque and speed according to the driving resistance of the present invention are realized. .
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9，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传递到超越离合器14，超越离合器14再分流为两路，一路传通过递到输入小齿圈21，另一路通过第一单向离合器11、输出齿轮副10、输入齿轮副7以及调速型液力偶合器3传递到输入大齿圈23，输入小齿圈21、输入大齿圈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再通过输入齿圈29、输出齿轮8、电磁离合器9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。When the invention is used, before the engine is started, the idle gear mechanism 6 is disengaged, the electromagnetic clutch 9 is engaged, and the engine speed is zero. When the starter is started, the input power of the starter is transmitted to the overrunning clutch 14 through the starter gear pair 12, beyond The clutch 14 is further divided into two paths, one pass through to the input small ring gear 21, and the other path is transmitted to the input through the first one-way clutch 11, the output gear pair 10, the input gear pair 7, and the variable speed fluid coupling 3. The large ring gear 23, the input small ring gear 21, the input large ring gear 23, and the planetary gears 20 transmitted to the respective powers passing through the output carrier 22 are merged to the output carrier 22, and the output carrier 22 is passed through the input ring gear 29, The output gear 8, the electromagnetic clutch 9 and the starter gear pair 13 are 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.
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9，输入轴1把由发动机传递到此的功率传递到超越离合器14，超越离合器14再分流为两路，一路传通过递到输入小齿圈21，另一路通过第一单向离合器11、输出齿轮副10、输入齿轮副7以及调速型液力偶合器3传递到输入大齿圈23，输入小齿圈21、输入大齿圈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，一路通过空挂档机构6传递到本发明的输出轴5；另一路传递到传递到输入齿圈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再传递到输入行星架24，输入行星架24通过其上的行星齿轮20传递到输出齿轮26，输出齿轮26再通过第二单向离合器4以及调速型液力偶合器3传递到输入大齿圈23，输入小齿圈21、输入大齿圈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，调速型液力偶合器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。After the engine is started, 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. Before the vehicle starts, the idle gear mechanism 6 is engaged, the electromagnetic clutch 9 is separated, and the input shaft 1 is The power transmitted to the engine is transmitted to the overrunning clutch 14, and the overrunning clutch 14 is split into two paths, one pass through to the input small ring gear 21, and the other pass through the first one-way clutch 11, the output gear pair 10, and the input gear pair. 7 and the variable speed type fluid coupling 3 are transmitted to the input large ring gear 23, the input small ring gear 21, the input large ring gear 23, and the planetary gears 20 transmitted to the respective powers passing through the output carrier 22 are merged to the output carrier. 22, the output planet carrier 22 is split into two paths, one is transmitted to the output shaft 5 of the present invention through the air-gear mechanism 6; the other is transmitted to the input ring gear 29, and the input ring gear 29 is passed through the fixed carrier 27. The planetary gear 20 is transmitted to the output ring gear 28, the output ring gear 28 is transmitted to the input carrier 24, the input carrier 24 is transmitted to the output gear 26 through the planetary gear 20 thereon, and the output gear 26 is passed through the second single The clutch 4 and the variable speed fluid coupling 3 are transmitted to the input large ring gear 23, the input small ring gear 21, and the input large ring gear 23 converge the planetary gears 20 transmitted to the respective powers through the output carrier 22 to the output planet. The frame 22 and the output carrier 22 continuously perform repeated cycles of shifting between the respective components, wherein the output speed of the variable speed fluid coupling 3 is not The ground speed is steplessly shifted as the running resistance changes, so that the output rotational speed of the output carrier 22 is also constantly changed, and is transmitted to the output shaft 5 of the present invention through the neutral gear mechanism 6, thereby causing the output shaft 5 The torque decreases as the speed increases.
实施例二：Embodiment 2:
如图2中所示，一种复合式调速型液力偶合器，包括输入轴1、调速型液力偶合器3、单向离合器4、输出轴5、输入齿轮副6、输出齿轮副7、超越离合器8，所述的输入轴1与输出轴5之间设有行星齿轮20、输入大齿轮21、输出联接行星架22、输入小齿轮23、输出齿轮24、输入齿轮25、固定行星架26、输出行星架27、输入大齿圈28、输入小齿圈29，输入轴1与输入大齿轮21以及超越离合器8的输入端81联接,超越离合器8的输入端81与输入小齿圈29联接,调速型液力偶合器3的输入端31与超越离合器8的输出端82以及单向离合器4的输出端42联接,单向离合器4的输入端41与输出齿轮24联接,调速型液力偶合器3的输出端32与输入小齿轮23联接,输入小齿轮23通过输出联接行星架22上的行星齿轮20与输出联接行星架22、输入大齿轮21相互配合工作，输出联接行星架22与输出齿轮副7的输入齿轮71联接,输出齿轮副7的输出齿轮72与输入齿轮副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25以及输入大齿圈28联接,输入齿轮25通过固定行星架26上的行星齿轮20与输出齿轮24、固定行星架26相互配合工作，固定行星架26与固定元件固接,输入大齿圈28通过输出行星架27上的行星齿轮20与输出行星架27、输入小齿圈29相互配合工作，输出行星架27与输出轴5联接。As shown in FIG. 2, a composite speed regulating fluid coupling includes an input shaft 1, a variable speed fluid coupling 3, a one-way clutch 4, an output shaft 5, an input gear pair 6, and an output gear pair. 7. Overrunning clutch 8, between the input shaft 1 and the output shaft 5, a planetary gear 20, an input large gear 21, an output coupling carrier 22, an input pinion 23, an output gear 24, an input gear 25, and a fixed planet are provided. The frame 26, the output carrier 27, the input large ring gear 28, the input small ring gear 29, the input shaft 1 is coupled to the input large gear 21 and the input end 81 of the overrunning clutch 8, the input end 81 of the overrunning clutch 8 and the input small ring gear 29, the input end 31 of the variable speed hydraulic coupling 3 is coupled with the output end 82 of the overrunning clutch 8 and the output end 42 of the one-way clutch 4, and the input end 41 of the one-way clutch 4 is coupled with the output gear 24 to adjust the speed The output end 32 of the type fluid coupling 3 is coupled to the input pinion 23, and the input pinion 23 cooperates with the output coupling carrier 22 and the input large gear 21 through the planetary gear 20 on the output coupling carrier 22, and outputs the coupled planet. The frame 22 is coupled to the input gear 71 of the output gear pair 7 The output gear 72 of the output gear pair 7 is coupled to the input gear 61 of the input gear pair 6, the output gear 62 of the input gear pair 6 is coupled to the input gear 25 and the input large ring gear 28, and the input gear 25 is passed through the fixed carrier 26. The planetary gear 20 cooperates with the output gear 24 and the fixed carrier 26 to fix the fixed carrier 26 and the fixed component. The input large ring gear 28 passes through the planetary gear 20 on the output carrier 27 and the output carrier 27, and the input small teeth. The rings 29 cooperate with each other and the output carrier 27 is coupled to the output shaft 5.
输入大齿轮21、输入小齿轮23把传递到各自的功率通过输出联接行星架22上的行星齿轮20汇流于输出联接行星架22，由于调速型液力偶合器3与输入小齿轮23联接,所以输入小齿轮23的转速可以不断地随着调速型液力偶合器3转速的变化而变化,从而使输出联接行星架22的转速也随之变化。The input large gear 21 and the input pinion 23 converge the planetary gears 20 transmitted to the respective powers through the output coupling carrier 22 to the output coupling carrier 22, since the variable speed fluid coupling 3 is coupled to the input pinion 23, Therefore, the rotational speed of the input pinion 23 can be constantly changed as the rotational speed of the variable speed fluid coupling 3 changes, so that the rotational speed of the output coupled carrier 22 also changes.
输入功率经过输入轴1分流为两路，一路传递到输入大齿轮21，另一路经过超越离合器8再分流为两路，一路经过调速型液力偶合器3传递到输入小齿轮23，另一路传递到输入小齿圈29，输入大齿轮21、输入小齿轮23把传递到各自的功率通过输出联接行星架22上的行星齿轮20汇流于输出联接行星架22，输出联接行星架22再通过输出齿轮副7传递到输入齿轮副6，输入齿轮副6再分流为两路，一路传递到输入大齿圈28，此时，输入大齿圈28与输入小齿圈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5,从而实现了把发动机的功率通过输出轴5对外输出。The input power is split into two paths through the input shaft 1, one is transmitted to the input large gear 21, the other is divided into two through the overrunning clutch 8, and one is transmitted to the input pinion 23 through the variable speed fluid coupling 3, and the other path is passed. It is transmitted to the input small ring gear 29, and the input large gear 21 and the input pinion 23 converge the planetary gears 20 transmitted to the respective powers through the output coupling carrier 22 to the output coupling carrier 22, and the output coupling planet carrier 22 passes through the output. The gear pair 7 is transmitted to the input gear pair 6, and the input gear pair 6 is divided into two paths, one way is transmitted to the input large ring gear 28, at this time, the input large ring gear 28 and the input small ring gear 29 are transmitted to their respective powers. The planetary gears 20 on the output carrier 27 merge with the output carrier 27, and the output carrier 27 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.
当发动机的输入功率增大或者输出轴5的阻力减少时，另一路传递到输入齿轮25的功率随之而增大，输入齿轮25则通过固定行星架26上的行星齿轮20把功率传递到输出齿轮24，输出齿轮24再通过单向离合器4、调速型液力偶合器3传递到输入小齿轮23，即输入小齿轮23的输入功率随之而增大，输入大齿轮21、输入小齿轮23把传递到各自的功率通过输出联接行星架22上的行星齿轮20汇流于输出联接行星架22，输出联接行星架22再重复上述过程，使传递到输入大齿圈28上的转速不断变化，输入大齿圈28与输入小齿圈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5,从而实现了把发动机的功率通过输出轴5对外输出。When the input power of the engine increases or the resistance of the output shaft 5 decreases, the power that is transmitted to the input gear 25 is increased, and the input gear 25 transmits power to the output through the planetary gears 20 on the fixed carrier 26. The gear 24 and the output gear 24 are transmitted to the input pinion 23 through the one-way clutch 4 and the variable speed fluid coupling 3, that is, the input power of the input pinion 23 is increased accordingly, and the input large gear 21 and the input pinion are input. 23 converging the respective powers through the planetary gears 20 on the output coupling carrier 22 to the output coupling carrier 22, outputting the coupled planet carrier 22 and repeating the above process, so that the rotational speed transmitted to the input large ring gear 28 is constantly changing, The input large ring gear 28 and the input small ring gear 29 converge the planetary gears 20 transmitted to the respective powers through the output carrier 27 to the output carrier 27, and the output carrier 27 is transmitted to the output shaft 5 of the present invention. The power of the engine is externally output through the output shaft 5.
对于本发明，当输入轴1的转速不变，输入大齿圈28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调速型液力偶合器。For the present invention, when the rotational speed of the input shaft 1 is constant, the rotational speed on the large ring gear 28 is input, and the vehicle is input with the work. The rate or the driving resistance varies, the lower the resistance, the higher the rotational speed transmitted to the input large ring gear 28, and vice versa, so that the present invention can be changed with the input power or running resistance of the vehicle. Speed compound speed governing fluid coupling.
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，一路传递到输入大齿轮21，另一路经过超越离合器8再分流为两路，一路经过调速型液力偶合器3传递到输入小齿轮23，另一路传递到输入小齿圈29，输入大齿轮21、输入小齿轮23把传递到各自的功率通过输出联接行星架22上的行星齿轮20汇流于输出联接行星架22，输出联接行星架22再通过输出齿轮副7传递到输入齿轮副6，输入齿轮副6再分流为两路，一路传递到输入大齿圈28，此时，输入大齿圈28与输入小齿圈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5,从而实现了把发动机的功率通过输出轴5对外输出。When the invention is used, 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 flow is divided into two paths, one way is transmitted to the input large gear 21, the other way is divided into two by the overrunning clutch 8, one is transmitted to the input pinion 23 through the variable speed fluid coupling 3, and the other is transmitted to the input small ring gear. 29. The input bull gear 21 and the input pinion 23 converge the planetary gears 20 that are transmitted to the respective powers through the output coupling carrier 22 to the output coupling carrier 22, and the output coupled carrier 22 is then transmitted to the input through the output gear pair 7. The gear pair 6 and the input gear pair 6 are split into two paths, one way to the input large ring gear 28, at which time the input large ring gear 28 and the input small ring gear 29 are transmitted to their respective powers through the output carrier 27. The planetary gear 20 merges with the output carrier 27, and the output carrier 27 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.
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，另一路传递到输入齿轮25的功率随之而增大，输入齿轮25则通过固定行星架26上的行星齿轮20把功率传递到输出齿轮24，输出齿轮24再通过单向离合器4、调速型液力偶合器3传递到输入小齿轮23，即输入小齿轮23的输入功率随之而增大，输入大齿轮21、输入小齿轮23把传递到各自的功率通过输出联接行星架22上的行星齿轮20汇流于输出联接行星架22，输出联接行星架22再重复上述过程，使传递到输入大齿圈28上的转速不断变化，输入大齿圈28与输入小齿圈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，调速型液力偶合器3的输出端32的转速也逐渐升高，与之相联的输入小齿轮23的转速也随之逐渐升高，从而使输出联接行星架22、输入大齿圈28以及输出轴5上的转速随之增加而不断地升高。 When the torque transmitted to the output shaft 5 is sufficient to overcome the resistance of the vehicle when the traction generated by the transmission system is sufficient to overcome the resistance of the vehicle, the vehicle starts to accelerate. At this time, when the resistance of the output shaft 5 decreases, the other is transmitted to the input. The power of the gear 25 is increased accordingly, and the input gear 25 transmits power to the output gear 24 through the planetary gear 20 on the fixed carrier 26, and the output gear 24 passes through the one-way clutch 4 and the variable speed fluid coupling 3 The input power transmitted to the input pinion 23, i.e., the input pinion 23, increases, and the input bull gear 21 and the input pinion 23 converge the output to the respective power through the planetary gear 20 on the output coupling carrier 22. Connecting the planet carrier 22, the output coupling planet carrier 22 repeats the above process, so that the rotational speed transmitted to the input large ring gear 28 is constantly changing, and the input large ring gear 28 and the input small ring gear 29 are transmitted to their respective powers through the output planet carrier. The planet gears 20 on 27 converge on the output planet carrier 27, and the output planet carrier 27 is transmitted to the output shaft 5 of the present invention. When the torque transmitted to the output shaft 5 is transmitted through the transmission system to When the traction force generated on the driving wheel is sufficient to further overcome the resistance of the automobile, the vehicle continues to accelerate, and the rotational speed of the output end 32 of the variable speed fluid coupling 3 is also gradually increased, and the rotational speed of the input pinion 23 associated with it is also This is gradually increased, so that the rotational speeds of the output coupling carrier 22, the input large ring gear 28, and the output shaft 5 are continuously increased.
Claims (2)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201680039159.1A CN107923508A (en) | 2015-07-07 | 2016-07-06 | A kind of composite variable speed fluid coupling and starter |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510389864.1 | 2015-07-07 | ||
| CN201510389864.1A CN105003608A (en) | 2015-07-07 | 2015-07-07 | Compound variable speed fluid coupling and starter |
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| Publication Number | Publication Date |
|---|---|
| WO2017005187A1 true WO2017005187A1 (en) | 2017-01-12 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/CN2016/088751 Ceased WO2017005187A1 (en) | 2015-07-07 | 2016-07-06 | Composite variable speed hydraulic coupler and starter |
Country Status (3)
| Country | Link |
|---|---|
| CN (2) | CN105003608A (en) |
| HK (1) | HK1211672A1 (en) |
| WO (1) | WO2017005187A1 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105003608A (en) * | 2015-07-07 | 2015-10-28 | 吴志强 | Compound variable speed fluid coupling and starter |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3425297A (en) * | 1965-11-01 | 1969-02-04 | Inpower Works Ltd | Fluid torque transmitter |
| EP0521769A1 (en) * | 1991-07-03 | 1993-01-07 | Regie Nationale Des Usines Renault S.A. | Shift device for transverse automatic transmission with the powerflow passing through two stages of coupled gears |
| CN102062193A (en) * | 2010-07-07 | 2011-05-18 | 吴志强 | Composite variable speed fluid coupling |
| CN104455299A (en) * | 2014-12-12 | 2015-03-25 | 吴志强 | A composite constant filling hydraulic coupling and starter |
| CN104482161A (en) * | 2014-12-12 | 2015-04-01 | 吴志强 | A composite hydraulic special-shaped coupling and starter |
| CN104534054A (en) * | 2014-12-12 | 2015-04-22 | 吴志强 | A composite speed-regulating hydraulic coupling and starter |
| CN105003608A (en) * | 2015-07-07 | 2015-10-28 | 吴志强 | Compound variable speed fluid coupling and starter |
-
2015
- 2015-07-07 CN CN201510389864.1A patent/CN105003608A/en active Pending
- 2015-11-11 HK HK15111108.9A patent/HK1211672A1/en unknown
-
2016
- 2016-07-06 CN CN201680039159.1A patent/CN107923508A/en active Pending
- 2016-07-06 WO PCT/CN2016/088751 patent/WO2017005187A1/en not_active Ceased
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3425297A (en) * | 1965-11-01 | 1969-02-04 | Inpower Works Ltd | Fluid torque transmitter |
| EP0521769A1 (en) * | 1991-07-03 | 1993-01-07 | Regie Nationale Des Usines Renault S.A. | Shift device for transverse automatic transmission with the powerflow passing through two stages of coupled gears |
| CN102062193A (en) * | 2010-07-07 | 2011-05-18 | 吴志强 | Composite variable speed fluid coupling |
| CN104455299A (en) * | 2014-12-12 | 2015-03-25 | 吴志强 | A composite constant filling hydraulic coupling and starter |
| CN104482161A (en) * | 2014-12-12 | 2015-04-01 | 吴志强 | A composite hydraulic special-shaped coupling and starter |
| CN104534054A (en) * | 2014-12-12 | 2015-04-22 | 吴志强 | A composite speed-regulating hydraulic coupling and starter |
| CN105003608A (en) * | 2015-07-07 | 2015-10-28 | 吴志强 | Compound variable speed fluid coupling and starter |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105003608A (en) | 2015-10-28 |
| HK1211672A1 (en) | 2016-05-27 |
| CN107923508A (en) | 2018-04-17 |
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