WO2017005176A1 - Compound case mill hydraulic coupler, and starter - Google Patents

Abstract

Provided are a compound case mill hydraulic coupler and a starter; an input shaft (1) is connected to an input starting gear pair (12) and an input end (131) of an overrunning clutch (13); the overrunning clutch (13) is connected to an input ring gear (22) and a starter gear pair (10); an output planet carrier (21) is connected to an output gear pair (9); a connecting shaft (8) is connected to a null shift mechanism (6), an input gear (7), the output gear pair (9), and an electromagnetic clutch (11); the null shift mechanism (6) is connected to an output shaft (5); the electromagnetic clutch (11) is connected to the input starting gear pair (12); the input gear (7) engages a large input ring gear (29); a small output gear (28) is connected to a case mill hydraulic coupler (4); the case mill hydraulic coupler (4) is connected to an input planet carrier (25); an output gear (24) is connected to as input gear (23) and a fixed one-way clutch (3).

Description

Composite box-grinding fluid coupling and starter Technical field

The invention belongs to the field of fluid couplings and starting, and more particularly to a composite box-grinding fluid coupling and a starter for various ground vehicles, ships, railway locomotives and machine tools.

Background technique

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.

Summary of the invention

The invention overcomes the deficiencies of the prior art, and provides a composite box-grinding fluid coupling and a starter which prolong the service life of the engine, has a simple structure, is convenient to operate, has low cost, and is energy-saving and high-efficiency.

In order to achieve the object of the present invention, the technical solution adopted by the present invention is as follows:

Composite box-grinding fluid coupling and starter, including input shaft (1), fixed one-way clutch (3), box-grinding fluid coupling (4), output shaft (5), empty gear Mechanism (6), input gear (7), coupling shaft (8), output gear pair (9), starter gear pair (10), electromagnetic clutch (11), input start gear pair (12), overrunning clutch (13 a fixed shaft (14), between the input shaft (1) and the output shaft (5), a planetary gear (20), an output carrier (21), an input ring gear (22), and an input gear (23) ), output gear (24), input planet carrier (25), fixed gear (26), fixed planet carrier (27), output small ring gear (28), input large ring gear (29), input shaft (1) and The output gear (122) of the input starter gear pair (12) and the input end (131) of the overrunning clutch (13) are coupled, the output end (132) of the overrunning clutch (13) and the input ring gear (22) and the starter gear pair The output gear (102) of (10) is coupled, the output gear (102) of the starter gear pair (10) cooperates with the input gear (101) of the starter gear pair (10), and the input ring gear (22) passes through the output. Planetary gear (20) on planet carrier (21) and output planet carrier (21 The input gears (23) cooperate with each other, the output carrier (21) is coupled to the input gear (91) of the output gear pair (9), and the input end of the coupling shaft (8) and the empty gear mechanism (6) (61) ), the input gear (7), the output gear (92) of the output gear pair (9), and the input end (111) of the electromagnetic clutch (11) are coupled, and the output end (62) and output shaft of the idle gear mechanism (6) (5) Coupling, the output end (112) of the electromagnetic clutch (11) is coupled with the input gear (121) of the input start gear pair (12), the input gear (7) is meshed with the input large ring gear (29), and the input large teeth The ring (29) cooperates with the fixed planet carrier (27) and the output small ring gear (28) through the planetary gear (20) on the fixed planet carrier (27), and outputs a small ring gear (28) and a box-grinding hydraulic force. The input end (41) of the coupling (4) is coupled, and the output end (42) of the box-grinding fluid coupling (4) is coupled to the input carrier (25), and the planetary gears passing through the input planet carrier (25) (20) Cooperating with the output gear (24) and the fixed gear (26), the output gear (24) is coupled with the input gear (23) and the output end (32) of the fixed one-way clutch (3), and the fixed gear (26) ) and the fixed planet carrier (27) is connected to the fixed shaft (14) The input end (31) of the fixed one-way clutch (3) and the fixed shaft (14) are coupled to the fixed element.

A composite box-grinding fluid coupling comprising an input shaft (1), a one-way clutch (3), a box-grinding fluid coupling (4), an output shaft (5), an input gear (6), and a coupling An input gear (7) and an output gear pair (8), wherein the input shaft (1) and the output shaft (5) are provided with a planetary gear (20), an input pinion (21), and an input carrier (22). , output large gear (23), fixed planet carrier (24), output small ring gear (25), input large ring gear (26), output planet carrier (27), input ring gear (28) an input gear (29), the input shaft (1) is coupled to the input pinion (21) and the input gear (29), and the input pinion (21) is passed through the planetary gear (20) on the input carrier (22) Working with the input carrier (22) and the output bull gear (23), the output large gear (23) is coupled to the input gear (81) of the output gear pair (8), and the output gear of the output gear pair (8) (82) ) coupled to the input gear (6) and the coupling input gear (7), the coupling input gear (7) meshes with the input large ring gear (26), and the input large ring gear (26) passes through the planetary gears on the fixed carrier (24) (20) working in cooperation with the fixed carrier (24) and the output small ring gear (25), the fixed carrier (24) and the input end (31) of the one-way clutch (3) are fixed to the fixed component, and the output small teeth The ring (25) is coupled to the input end (41) of the box-grinding fluid coupling (4), the output end (42) of the box-grinding fluid coupling (4) and the output end of the one-way clutch (3) ( 32) and the input planet carrier (22) is coupled, the input gear (6) is meshed with the input ring gear (28), and the input ring gear (28) is passed through the planetary gear (20) on the output carrier (27) and the output planet carrier ( 27), the input gear (29) work together, the output line The star frame (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.

The box-grinding fluid coupling can be replaced by an external hydraulic torque converter of the relief valve.

The air-locking mechanism can select a clutch instead.

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 has the following advantages:

(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) 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) 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) 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) 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) 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) The invention reduces the transmission mechanism of the current starter machine and reduces the manufacturing cost. After the engine is started, only the braking and separating measures of the starting motor are required to stop the transmission.

Further, the present invention is a composite box-grinding fluid coupling and starter for various ground vehicles, ships, railway locomotives, and machine tools.

DRAWINGS

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a structural view of a first embodiment of the present invention;

2 is a structural diagram of a second embodiment of the present invention;

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.

detailed description

The present invention will be further described in detail below in conjunction with the drawings and specific embodiments.

Embodiment 1:

As shown in FIG. 1 , a composite box-grinding fluid coupling and a starter include an input shaft 1 , a fixed one-way clutch 3 , a box-grinding fluid coupling 4 , an output shaft 5 , and an idle gear mechanism. 6. Input gear 7, coupling shaft 8, output gear pair 9, starter gear pair 10, electromagnetic clutch 11, input start gear pair 12, overrunning clutch 13, fixed shaft 14, said input shaft 1 and output shaft 5 Between the planetary gear 20, the output carrier 21, the input ring gear 22, the input gear 23, the output gear 24, the input carrier 25, the fixed gear 26, the fixed carrier 27, the output small ring gear 28, the input large ring gear 29 The input shaft 1 is coupled to the output gear 122 of the input starter gear pair 12 and the input end 131 of the overrunning clutch 13, and the output end 132 of the overrunning clutch 13 is coupled to the input ring gear 22 and the output gear 102 of the starter gear pair 10, the starter The output gear 102 of the gear pair 10 cooperates with the input gear 101 of the starter gear pair 10, and the input ring gear 22 cooperates with the output carrier 21 and the input gear 23 through the planetary gear 20 on the output carrier 21 to output the planet. Rack 21 and output The input gear 91 of the wheel set 9 is coupled, and the coupling shaft 8 is coupled to the input end 61 of the neutral gear mechanism 6, the input gear 7, the output gear 92 of the output gear pair 9, and the input end 111 of the electromagnetic clutch 11, and the idle gear mechanism 6 The output end 62 is coupled to the output shaft 5, the output end 112 of the electromagnetic clutch 11 is coupled to the input gear 121 of the input starter gear pair 12, the input gear 7 is meshed with the input large ring gear 29, and the input large ring gear 29 is passed through the fixed carrier 27 The upper planetary gear 20 cooperates with the fixed carrier 27 and the output small ring gear 28, and the output small ring gear 28 is coupled with the input end 41 of the box-grinding fluid coupling 4, and the output of the box-grinding fluid coupling 4 The end 42 is coupled to the input carrier 25, the input carrier 25 is coupled to the output gear 24 and the fixed gear 26 via the planetary gear 20 thereon, and the output gear 24 is coupled to the input gear 23 and the output 32 of the fixed one-way clutch 3. The fixed gear 26 and the fixed carrier 27 are coupled to the fixed shaft 14, and the input end 31 of the fixed one-way clutch 3 and the fixed shaft 14 are coupled to the fixed element.

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 input ring gear 22 via the starter gear pair 10, and the input ring gear 22 is transmitted to the input gear carrier 22 through the planetary gear 20 on the output carrier 21. The output carrier 21, the output carrier 21 is then transmitted to the input shaft 1 through the output gear pair 9, the coupling shaft 8, the electromagnetic clutch 11 and the input start gear pair 12, and then transmitted to the engine crankshaft, and the generated power is sufficient to overcome the engine start. When the resistance is reached, the engine starts.

After the engine is started, the idle gear mechanism 6 is engaged, the electromagnetic clutch 11 is disengaged, and the input ring gear 22 transmits the power transmitted from the engine to the input shaft 1 and the overrunning clutch 13 through the planetary gears 20 on the output carrier 21, and is transmitted to the output. The carrier 21, the output carrier 21 is transmitted to the coupling shaft 8 through the output gear pair 9, the coupling shaft 8 splits the power transmitted thereto into two paths, one way through the idle gear mechanism 6 is transmitted to the output shaft 5 of the present invention; The other path is transmitted to the input large ring gear 29 through the input gear 7, and the input large ring gear 29 is transmitted to the output small ring gear 28 through the planetary gear 20 on the fixed carrier 27, and the output small ring gear 28 is fluidly coupled by the box grinding type. The device 4 is transmitted to the input carrier 25, and the input carrier 25 is transmitted to the output gear 24 through the planetary gear 20 thereon, and the output gear 24 is transmitted to the input gear 23, and transmitted to The power input to the gear 23 and the power transmitted from the engine through the input shaft 1 and the overrunning clutch 13 to the input ring gear 22 are transmitted to the output carrier 21 through the planetary gears 20 on the output carrier 21, and the output carrier 21 is again The repetitive cycle of shifting between the components is continuously performed, wherein the output rotational speed of the box-grinding fluid coupling 4 continuously shifts steplessly with changes in input power and running resistance, thereby causing the output speed of the output carrier 21 It is also constantly changing, and is transmitted to the output shaft 5 of the present invention through the output gear pair 9, the coupling shaft 8, and the neutral gear mechanism 6, thereby achieving external output of the engine power through the output shaft 5.

For the present invention, when the rotational speed of the input shaft 1 is constant, the torque on the output carrier 21, the input gear 23, and the output shaft 5 varies with the change in the rotational speed thereof, and the lower the rotational speed, the transmission to the output carrier 21, the input gear 23 And the torque on the output shaft 5 is larger, and conversely, the smaller, thereby realizing the composite box-grinding fluid coupling and the starter which can change the torque and the speed according to the difference in the running resistance of the vehicle.

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. When the starter is started, the input power of the starter is transmitted to the input ring gear 22 through the starter gear pair 10, Wherein, since no power flows into the input gear 23 at this time, and the input end 31 of the fixed one-way clutch 3 is coupled with the fixed element, the steering is restricted to make the input gear 23 unable to rotate opposite to the engine, and the rotational speed is zero. When the power transmitted to the input ring gear 22 is transmitted to the output carrier 21 through the planetary gears 20 on the output carrier 21, the output carrier 21 passes through the output gear pair 9, the coupling shaft 8, the electromagnetic clutch 11 and The input starter gear pair 12 is transmitted to the input shaft 1 and then to the engine crankshaft. When the torque transmitted to the crankshaft of the engine is sufficient to overcome the starting resistance of the engine, the engine starts and begins to accelerate.

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 11 is separated, and the output shaft 5 is rotated. Zero, the input power of the engine is transmitted to the input ring gear 22 via the input shaft 1 and the overrunning clutch 13, wherein since no power flows into the input gear 23 at this time, and the input end 31 of the fixed one-way clutch 3 is coupled to the fixed element, The function of limiting the steering is such that the input gear 23 cannot rotate opposite to the steering of the engine, and the rotational speed is zero. At this time, the power transmitted to the input ring gear 22 is transmitted to the output through the planetary gear 20 on the output carrier 21. The planet carrier 21, the output planet carrier 21 is transmitted to the coupling shaft 8 through the output gear pair 9, and the coupling shaft 8 diverts the power transmitted thereto into two paths, one pass through the idle gear mechanism 6 to the output shaft 5 of the present invention, When the torque transmitted to the output shaft 5, the traction generated by the drive train to the drive wheel is sufficient to overcome the starting resistance of the car, the car starts and begins to increase. The other path is transmitted to the input large ring gear 29 through the input gear 7, and the input large ring gear 29 is transmitted to the output small ring gear 28 through the planetary gear 20 on the fixed carrier 27, and the output small ring gear 28 is passed through the box grinding type hydraulic force. The coupling 4 is transmitted to the input carrier 25, and the input carrier 25 is transmitted to the output gear 24 through the planetary gears 20 on the input carrier 25, and the output gear 24 is transmitted to the output carrier 21 for transmission to the output carrier 21. And the power transmitted from the engine through the input shaft 1 and the overrunning clutch 13 to the input ring gear 22 is transmitted to the output carrier 21 through the planetary gears 20 on the output carrier 21, and the output carrier 21 is continuously between the components. The repeated cycle of the shifting is performed, wherein the output rotational speed of the box-grinding fluid coupling 4 is continuously steplessly changed in accordance with the change in the running resistance, so that the output rotational speed of the input gear 23 is also constantly changed, and the output gear is passed through The secondary 9, the coupling shaft 8, and the idle gear mechanism 6 are transmitted to the output shaft 5 of the present invention, so that the torque of the output shaft 5 decreases as the number of revolutions increases.

Embodiment 2:

As shown in FIG. 2, a composite box-grinding fluid coupling includes an input shaft 1, a one-way clutch 3, a box-grinding fluid coupling 4, an output shaft 5, an input gear 6, and a coupling input gear 7. Output gear pair 8, the input shaft 1 and the output shaft Between 5, a planetary gear 20, an input pinion 21, an input carrier 22, an output bull gear 23, a fixed carrier 24, an output small ring gear 25, an input large ring gear 26, an output carrier 27, and an input ring gear 28 are provided. The input gear 29 is coupled to the input pinion 21 and the input gear 29. The input pinion 21 cooperates with the input carrier 22 and the output bull gear 23 through the planetary gear 20 on the input carrier 22 to output a large gear. 23 is coupled to the input gear 81 of the output gear pair 8, the output gear 82 of the output gear pair 8 is coupled to the input gear 6 and the coupling input gear 7, the coupling input gear 7 is meshed with the input large ring gear 26, and the input large ring gear 26 is fixed The planetary gears 20 on the planet carrier 24 cooperate with the fixed planet carrier 24 and the output small ring gear 25, and the fixed planet carrier 24 and the input end 31 of the one-way clutch 3 are fixed to the fixed component, and the small ring gear 25 and the box mill are output. The input end 41 of the fluid coupling 4 is coupled, the output 42 of the box-grinding fluid coupling 4 is coupled to the output 32 of the one-way clutch 3 and the input carrier 22, and the input gear 6 is meshed with the input ring gear 28, Input ring gear 28 through the output The planetary gears 20 on the carrier 27 cooperate with the output carrier 27 and the input gear 29, and the output carrier 27 is coupled to the output shaft 5.

The input pinion 21 and the input carrier 22 converge the planetary gears 20 transmitted to the respective powers through the input carrier 22 to the output bull gear 23, and since the box-grinding fluid coupling 4 is coupled to the input carrier 22, the input The rotational speed of the carrier 22 can be constantly varied as the rotational speed of the tank-grinding fluid coupling 4 changes, so that the rotational speed of the output bull gear 23 also changes.

The input power is split into two paths through the input shaft 1, one is transmitted to the input pinion 21, and the other is transmitted to the input gear 29, and the input pinion 21 converges the power transmitted thereto through the planetary gear 20 on the input carrier 22 to the output. The large gear 23, the output large gear 23 is divided into two paths by coupling the output gear pair 8, one way is transmitted to the input ring gear 28 through the input gear 6, and at this time, the input ring gear 28 and the input 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.

When the input power of the engine increases or the resistance of the output shaft 5 decreases, the power that the other path transmits to the input large ring gear 26 through the coupling input gear 7 increases accordingly, and the input large ring gear 26 passes through the fixed planet carrier 24. The planetary gear 20 transmits power to the output small ring gear 25, and the output small ring gear 25 is transmitted to the input carrier 22 through the box-grinding fluid coupling 4, that is, the input power of the input carrier 22 increases accordingly. The input pinion 21 and the input carrier 22 converge the planetary gears 20 transmitted to the respective powers through the input carrier 22 to the output bull gear 23, and the output bull gear 23 repeats the above process to be transmitted to the input ring gear 28. The rotational speed 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 output shaft 5 of the present invention, thereby It is achieved that the power of the engine is externally output through the output shaft 5.

For the present invention, when the rotational speed of the input shaft 1 is constant, the rotational speed of the input ring gear 28 varies with the input power or running resistance of the vehicle, and the lower the resistance, the higher the rotational speed transmitted to the input ring gear 28 is. On the contrary, the lower the degree, the composite type of box-grinding fluid coupling which can change the speed according to the input power or the running resistance of the vehicle.

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 split is two paths, one is transmitted to the input pinion 21, and the other is transmitted to the input gear 29, and the input pinion 21 converges the power transmitted thereto through the planetary gear 20 on the input carrier 22 to the output bull gear 23, and the output is large. The gear 23 is split into two paths by coupling the output gear pair 8, one path being transmitted through the input gear 6 to the input ring gear 28, at which time the input ring gear 28 and the input gear 29 are transmitted to their respective powers through the output carrier 27. The planet gears 20 converge on the output planet carrier 27, The output carrier 27 is then transmitted to the output shaft 5 of the present invention, thereby realizing the external output of the engine through the output shaft 5, and the torque transmitted to the output shaft 5 is sufficient to be transmitted through the transmission system to the drive wheel. When the resistance of the automobile is overcome, the car starts to accelerate. At this time, when the resistance of the output shaft 5 decreases, the power of the other path transmitted to the input large ring gear 26 through the coupling input gear 7 increases accordingly, and the input large ring gear 26 is increased. Then, the power is transmitted to the output small ring gear 25 through the planetary gears 20 on the fixed carrier 24, and the output small ring gear 25 is transmitted to the input carrier 22 through the box-grinding fluid coupling 4, that is, the input to the input carrier 22. As the power increases, the input pinion 21 and the input carrier 22 converge the planetary gears 20 that are transmitted to the respective powers through the input carrier 22 to the output bull gear 23, and the output gears 23 repeat the above process to transmit The rotational speed to the input ring gear 28 is constantly changing, and the input ring gear 28 and the input gear 29 merge the power transmitted to the respective power through the planetary gear 20 on the output carrier 27 to the output carrier 27, and the output The star frame 27 is transmitted to the output shaft 5 of the present invention, thereby realizing the external output of the engine through the output shaft 5. When the torque transmitted to the output shaft 5 is transmitted to the drive wheel through the transmission system, the traction force is sufficient for further When the resistance of the automobile is overcome, the automobile continues to accelerate, and the rotational speed of the output end 42 of the box-grinding fluid coupling 4 is also gradually increased, and the rotational speed of the associated input carrier 22 is gradually increased, thereby The rotational speeds of the output bull gear 23, the input ring gear 28, and the output shaft 5 are continuously increased and continuously increased.

Claims (2)

Composite box-grinding fluid coupling and starter, including input shaft (1), fixed one-way clutch (3), box-grinding fluid coupling (4), output shaft (5), empty gear Mechanism (6), input gear (7), coupling shaft (8), output gear pair (9), starter gear pair (10), electromagnetic clutch (11), input start gear pair (12), overrunning clutch (13 a fixed shaft (14), characterized in that: between the input shaft (1) and the output shaft (5), a planetary gear (20), an output carrier (21), an input ring gear (22), Input gear (23), output gear (24), input carrier (25), fixed gear (26), fixed planet carrier (27), output small ring gear (28), input large ring gear (29), input shaft (1) coupled to the output gear (122) of the input starter gear pair (12) and the input end (131) of the overrunning clutch (13), the output end (132) of the overrunning clutch (13) and the input ring gear (22) and The output gear (102) of the starter gear pair (10) is coupled, the output gear (102) of the starter gear pair (10) and the input gear (101) of the starter gear pair (10) cooperate to input the ring gear ( 22) by the planetary gear (20) on the output planet carrier (21) The output carrier (21) and the input gear (23) cooperate with each other, and the output carrier (21) is coupled with the input gear (91) of the output gear pair (9), and the coupling shaft (8) and the empty gear mechanism (6) The input end (61), the input gear (7), the output gear (92) of the output gear pair (9), and the input end (111) of the electromagnetic clutch (11) are coupled to the output end of the idle gear mechanism (6) ( 62) coupled to the output shaft (5), the output end (112) of the electromagnetic clutch (11) is coupled to the input gear (121) of the input start gear pair (12), the input gear (7) and the input large ring gear (29) Engagement, the input large ring gear (29) cooperates with the fixed planet carrier (27) and the output small ring gear (28) through the planetary gear (20) on the fixed planet carrier (27), and outputs a small ring gear (28) and The input end (41) of the box-grinding fluid coupling (4) is coupled, and the output end (42) of the box-grinding fluid coupling (4) is coupled to the input carrier (25), and the input carrier (25) passes The planetary gear (20) cooperates with the output gear (24) and the fixed gear (26), and the output gear (24) is coupled with the input gear (23) and the output end (32) of the fixed one-way clutch (3). , fixed gear (26) and fixed planet carrier (27) Input terminal of the fixed shaft (14) coupled to the fixed one-way clutch (3) (31) and a stationary shaft (14) coupled to the fixed member. A composite box-grinding fluid coupling comprising an input shaft (1), a one-way clutch (3), a box-grinding fluid coupling (4), an output shaft (5), an input gear (6), and a coupling An input gear (7) and an output gear pair (8) are characterized in that: a planetary gear (20), an input pinion (21), and an input planet are disposed between the input shaft (1) and the output shaft (5). Rack (22), output large gear (23), fixed planet carrier (24), output small ring gear (25), input large ring gear (26), output planet carrier (27), input ring gear (28), input a gear (29), an input shaft (1) coupled to the input pinion (21) and an input gear (29), the input pinion (21) passing through the planet gear (20) on the input carrier (22) and the input carrier ( 22), the output large gear (23) cooperates with each other, the output large gear (23) is coupled with the input gear (81) of the output gear pair (8), and the output gear (82) of the output gear pair (8) and the input gear ( 6) and the coupling input gear (7) is coupled, the input input gear (7) is meshed with the input large ring gear (26), and the input large ring gear (26) is fixed by the planetary gear (20) fixed on the carrier (24). Planet carrier (24) and output small ring gear (25) work together The fixed carrier (24) and the input end (31) of the one-way clutch (3) are fixed to the fixed component, and the output small ring gear (25) is coupled to the input end (41) of the box-grinding fluid coupling (4). The output end (42) of the box-grinding fluid coupling (4) is coupled to the output end (32) of the one-way clutch (3) and the input carrier (22), and the input gear (6) and the input ring gear (28) Engagement, the input ring gear (28) cooperates with the output carrier (27) and the input gear (29) through the planetary gears (20) on the output carrier (27), and outputs the planet carrier (27) and the output shaft ( 5) Connection.

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