WO2017005177A1 - Compound case-type hydraulic coupler, and starter - Google Patents

Abstract

Provided are a compound case-type hydraulic coupler and a starter having said compound case-type hydraulic coupler; an input shaft (1) is connected to a starting gear pair (11) and an overrunning clutch (10); the overrunning clutch (10) is connected to an input gear (22) and a starter gear pair (9); a large output ring gear (23) engages an input ring gear (24); a connecting shaft (13) is connected to the input ring gear (24), an electromagnetic clutch (12), and an input gear pair (4); the input gear pair (4) is connected to a null shift mechanism (6); the null shift mechanism (6) is connected to an output shaft (5); the electromagnetic clutch (12) is connected to the starting gear pair (11); an output ring gear (26) engages an input gear (3); the input gear (3) is connected to a connecting input planet carrier (27); an output gear (29) is connected to a case-type hydraulic coupler (7); the case-type hydraulic coupler (7) and a fixed one-way clutch (8) are connected to an input planet carrier (21).

Description

Composite box type fluid coupling and starter Technical field

The present invention is in the field of fluid couplings and starting, and more particularly, it is a composite tank type fluid coupling and starter for various ground vehicles, ships, railway locomotives, and machine tools.

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 type fluid coupling and a starter which prolong the service life of the engine, has a simple structure, is convenient to operate, has low cost, is energy-saving and high-efficiency.

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

A composite tank type fluid coupling and starter, comprising an input shaft (1), an input gear (3), an input gear pair (4), an output shaft (5), an empty gear mechanism (6), a box Body fluid coupling (7), fixed one-way clutch (8), starter gear pair (9), overrunning clutch (10), starting gear pair (11), electromagnetic clutch (12), coupling shaft (13) The input shaft (1) and the output shaft (5) are provided with a planetary gear (20), an input carrier (21), an input gear (22), an output large ring gear (23), and an input ring gear ( 24), fixed carrier (25), output ring gear (26), coupled input planet carrier (27), fixed gear (28), output gear (29), input shaft (1) and start gear pair (11) The output gear (112) and the input end (101) of the overrunning clutch (10) are coupled, the output end (102) of the overrunning clutch (10) and the input gear (22) and the output gear (92) of the starter gear pair (9) The output gear (92) of the starter gear pair (9) cooperates with the input gear (91) of the starter gear pair (9), and the input gear (22) passes through the planetary gears on the input carrier (21) ( 20) Interacting with the input planet carrier (21) and the output large ring gear (23) Working together, the output large ring gear (23) meshes with the input ring gear (24), the coupling shaft (13) and the input ring gear (24), the input end (121) of the electromagnetic clutch (12), and the input gear pair (4) The input gear (41) is coupled, the output gear (42) of the input gear pair (4) is coupled to the input end (61) of the neutral gear mechanism (6), and the output end (62) of the empty gear mechanism (6) is The output shaft (5) is coupled, the output end (122) of the electromagnetic clutch (12) is coupled to the input gear (111) of the start gear pair (11), and the input ring gear (24) is passed through the planetary gear on the fixed carrier (25) (20) working in cooperation with the fixed carrier (25) and the output ring gear (26), the output ring gear (26) meshes with the input gear (3), and the input gear (3) is coupled with the coupled input carrier (27). The planetary gear (20) coupled to the input carrier (27) cooperates with the fixed gear (28) and the output gear (29) to fix the carrier (25), the fixed gear (28) and the fixed one-way clutch ( 8) The input end (81) is coupled to the stationary element, the output gear (29) is coupled to the input end (71) of the tank-type fluid coupling (7), and the output of the tank-type fluid coupling (7) (72) and fixed one-way clutch (8) The end (82) and the input planet carrier (21) is coupled.

A composite tank type fluid coupling, comprising an input shaft (1), a one-way clutch (3), a tank type fluid coupling (4), an output shaft (5), an input gear pair (6), The output gear pair (7) and the output gear pair (8) are coupled, and a planetary gear (20), an input small ring gear (21), and an input large tooth are disposed between the input shaft (1) and the output shaft (5). a ring (22), an output planet carrier (23), an output gear (24), a fixed planet carrier (25), an input gear (26), an input planet carrier (27), an input pinion (28), The output ring gear (29) is coupled to the input small ring gear (21) and the input gear (81) of the output gear pair (8), and the output gear (82) of the output gear pair (8) is small with the input. The gear (28) is coupled, and the input small ring gear (21) cooperates with the input large ring gear (22) and the output planet carrier (23) through the planetary gear (20) on the output carrier (23), and outputs the planet carrier ( 23) coupled to the input gear (71) of the coupled output gear pair (7), coupled to the output gear (72) of the output gear pair (7) and the input gear (27) and the input gear of the input gear pair (6) (61) The coupling gear (62) of the input gear pair (6) is coupled to the input gear (26), and the input gear (26) is fixed by the planetary gear (20) and the output gear (24) fixed on the carrier (25). The planet carrier (25) cooperates with each other, the fixed carrier (25) and the input end (31) of the one-way clutch (3) are fixed to the fixed component, and the output gear (24) and the box type fluid coupling (4) The input end (41) is coupled, the output end (42) of the tank type fluid coupling (4) is coupled with the output end (32) of the one-way clutch (3) and the input large ring gear (22), and the input carrier (27) The planetary gear (20) and the input through it Wheel (28), an output ring gear (29) cooperate with each other, the output ring gear (29) and the output shaft (5) is coupled.

The elements that need to be coupled, and the elements that are separated by several other elements, can be connected to or through several other elements by means of a hollow or a coupling frame; when the coupled elements are gears or ring gears, Then, meshing or coupling; the gear ratio of each gear pair and the shifting mechanism is designed according to actual needs.

The tank type fluid coupling can be replaced by a double pump wheel hydraulic torque converter.

The air-locking mechanism can select a clutch instead.

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 type tank type 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 tank type fluid coupling and a starter include an input shaft 1, an input gear 3, an input gear pair 4, an output shaft 5, an idle gear mechanism 6, and a tank type liquid. The force coupling 7, the fixed one-way clutch 8, the starter gear pair 9, the overrunning clutch 10, the starting gear pair 11, the electromagnetic clutch 12, the coupling shaft 13, and the planetary gear between the input shaft 1 and the output shaft 5 20. Input planet carrier 21, input gear 22, output large ring gear 23, input ring gear 24, fixed planet carrier 25, output ring gear 26, coupled input carrier 27, fixed gear 28, output gear 29, input shaft 1 and The output gear 112 of the start gear pair 11 and the input end 101 of the overrunning clutch 10 are coupled, and the output end 102 of the overrunning clutch 10 is coupled to the input gear 22 and the output gear 92 of the starter gear pair 9, the output gear 92 of the starter gear pair 9 The input gear 91 of the starter gear pair 9 cooperates with each other. The input gear 22 cooperates with the input carrier 21 and the output large ring gear 23 through the planetary gear 20 on the input carrier 21, and outputs the large ring gear 23 and the input tooth. Ring 24 meshes, coupling shaft 13 Coupling with the input ring gear 24, the input end 121 of the electromagnetic clutch 12, and the input gear 41 of the input gear pair 4, the output gear 42 of the input gear pair 4 is coupled to the input end 61 of the neutral gear mechanism 6, the idle gear mechanism 6 The output end 62 is coupled to the output shaft 5, and the output end 122 of the electromagnetic clutch 12 is coupled to the input gear 111 of the start gear pair 11. The input ring gear 24 passes through the planetary gear 20 on the fixed carrier 25 and the fixed carrier 25, and the output ring gear. 26 cooperates with each other, the output ring gear 26 meshes with the input gear 3, the input gear 3 is coupled with the coupling input carrier 27, and the planetary gear 20 coupled to the input carrier 27 cooperates with the fixed gear 28 and the output gear 29 to cooperate with each other. The fixed planet carrier 25, the fixed gear 28 and the input end 81 of the fixed one-way clutch 8 are coupled to a fixed element, and the output gear 29 is coupled to the input 71 of the tank-type fluid coupling 7, the tank-type fluid coupling 7 The output end 72 and the output end 82 of the fixed one-way clutch 8 are coupled to the input carrier 21.

Before the engine is started, the idle gear mechanism 6 is disengaged and the electromagnetic clutch 12 is engaged. The input power of the starter is transmitted to the input gear 22 via the starter gear pair 9, and the input gear 22 is transmitted to the output through the planetary gear 20 on the input carrier 21. The ring gear 23, the output large ring gear 23 is transmitted to the input shaft 1 through the input ring gear 24, the coupling shaft 13, the electromagnetic clutch 12 and the start gear pair 11, and is transmitted to the crankshaft of the engine, and the generated driving force is sufficient to overcome the engine starting resistance. When the engine starts.

After the engine is started, the idle gear mechanism 6 is engaged, and the electromagnetic clutch 12 is disengaged. The input gear 22 transmits the power transmitted from the engine to the input shaft 1 and the overrunning clutch 12 through the planetary gear 20 input to the carrier 21, and is transmitted to the output. The ring gear 23, the output large ring gear 23 is transmitted to the input ring gear 24, and the input ring gear 24 diverts the power transmitted thereto into two paths, one pass through the coupling shaft 13, the input gear pair 4, and the idle gear mechanism 6 to The output shaft 5 of the present invention; the other path is transmitted to the output ring gear 26 through the planetary gear 20 on the fixed carrier 25, and the output ring gear 26 is transmitted to the coupled input carrier 27 through the input gear 3, coupled to the input carrier 27 and passed The planetary gear 20 on it is transmitted to the transmission The output gear 29, the output gear 29 is transmitted to the input carrier 21 through the tank type fluid coupling 7, the power transmitted to the input carrier 21, and the power transmitted from the engine to the input gear 22 via the input shaft 1 and the overrunning clutch 10, Then, the planetary gear 20 on the input carrier 21 is transmitted to the output large ring gear 23, and the large ring gear 23 is outputted, and the repeated cycle of the shifting is continuously performed between the respective components, wherein the output of the tank type fluid coupling 7 is output. The rotational speed continuously shifts steplessly as the input power and the running resistance change, so that the output rotational speed of the output large ring gear 23 also constantly changes, and through the input ring gear 24, the coupling shaft 13, the input gear pair 4, and the air The gear shifting mechanism 6 is transmitted to the output shaft 5 of the present invention, thereby realizing the external output of the engine power through the output shaft 5.

For the present invention, when the rotational speed of the input shaft 1 is constant, the torque on the input carrier 21, the output large ring gear 23, and the output shaft 5 varies with the change of the rotational speed thereof, and the lower the rotational speed, the transmission to the input carrier 21 and the output. The larger the torque on the large ring gear 23 and the output shaft 5, and vice versa, the smaller the size, so that the composite box type fluid coupling and the starter which can change the torque and speed according to the driving resistance of the present invention are realized. .

When the invention is used, before the engine is started, the idle gear mechanism 6 is disengaged, the electromagnetic clutch 12 is engaged, and the engine speed is zero. When the starter is started, the input power of the starter is transmitted to the input gear 22 through the starter gear pair 9, wherein Since no power flows into the input carrier 21 at this time, and the input end 81 of the fixed one-way clutch 8 is coupled to the fixed component, the steering is restricted, so that the input carrier 21 cannot rotate opposite to the engine, and the rotational speed is zero. At this time, the power transmitted to the input gear 22 is transmitted to the output large ring gear 23 through the planetary gear 20 input to the carrier 21, and the large ring gear 23 is output through the input ring gear 24, the coupling shaft 13, and the electromagnetic clutch. 12 and the starter gear pair 11 is transmitted to the input shaft 1 and then to the engine crankshaft. 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 12 is separated, and the output shaft 5 is rotated. Zero, the input power of the engine is transmitted to the input gear 22 via the input shaft 1 and the overrunning clutch 10, wherein since no power flows into the input carrier 21 at this time, and the input end 81 of the fixed one-way clutch 8 is coupled to the fixed member, The function of restricting the steering is such that the input carrier 21 cannot rotate opposite to the engine, and the rotational speed is zero. At this time, the power transmitted to the input gear 22 is transmitted to the output through the planetary gear 20 input to the carrier 21. The large ring gear 23, the output large ring gear 23 is transmitted to the input ring gear 24, and the input ring gear 24 diverts the power transmitted thereto into two paths, one pass through the coupling shaft 13, the input gear pair 4, and the idle gear mechanism 6. To the output shaft 5 of the present invention; the other path is transmitted to the output ring gear 26 through the planetary gear 20 on the fixed carrier 25, and the output ring gear 26 is transmitted to the joint through the input gear 3. The input carrier 27 is coupled to the input carrier 27 and transmitted to the output gear 29 through the planetary gear 20 thereon. The output gear 29 is transmitted to the input carrier 21 through the tank type fluid coupling 7 and transmitted to the input carrier 21. The power and the power transmitted from the engine through the input shaft 1 and the overrunning clutch 10 to the input gear 22 are transmitted to the output large ring gear 23 through the planetary gear 20 on the input carrier 21, and the large ring gear 23 is output between the respective components. The repeated cycle of the shifting is continuously performed, wherein the output rotational speed of the tank type fluid coupling 7 is continuously steplessly changed in accordance with the change in the running resistance, so that the output rotational speed of the output large ring gear 23 is also constantly changed. And the input ring gear 24, the coupling shaft 13, the input gear pair 4, and the idle gear mechanism 6 are transmitted to the output shaft 5 of the present invention, so that the torque of the output shaft 5 is reduced as the number of revolutions increases.

Embodiment 2:

As shown in FIG. 2, a composite tank type fluid coupling includes an input shaft 1, a one-way clutch 3, a tank type fluid coupling 4, an output shaft 5, an input gear pair 6, and a coupling output gear. Sub 7 , output gear pair 8, the input shaft 1 and the input A planetary gear 20, an input small ring gear 21, an input large ring gear 22, an output carrier 23, an output gear 24, a fixed carrier 25, an input gear 26, an input carrier 27, and an input pinion 28 are disposed between the output shafts 5. The output ring gear 29 is coupled to the input small gear ring 21 and the input gear 81 of the output gear pair 8. The output gear 82 of the output gear pair 8 is coupled to the input pinion 28, and the input small ring gear 21 is passed through the output carrier. The planetary gear 20 on the 23 cooperates with the input large ring gear 22 and the output carrier 23, the output carrier 23 is coupled with the input gear 71 of the coupled output gear pair 7, and the output gear 72 of the output gear pair 7 is coupled to the input carrier. 27 and the input gear 61 of the input gear pair 6 are coupled, the output gear 62 of the input gear pair 6 is coupled to the input gear 26, and the input gear 26 is matched with the output gear 24 and the fixed carrier 25 by the planetary gear 20 on the fixed carrier 25. Working, the fixed carrier 25 and the input end 31 of the one-way clutch 3 are fixed to the fixed element, and the output gear 24 is coupled to the input 41 of the tank type fluid coupling 4, the output of the tank type fluid coupling 4 42 and one-way clutch Output 3 and an input terminal 32 coupled to the ring gear 22, input planet carrier 27 through the planetary gear 20 on the input pinion 28, output gear 29 cooperate with each other, the output gear 29 and the output shaft 5 is coupled.

The input small ring gear 21 and the input large ring gear 22 converge the respective power transmitted through the planetary gears 20 on the output carrier 23 to the output carrier 23, since the box type fluid coupling 4 is coupled to the input large ring gear 22. Therefore, the rotational speed of the input large ring gear 22 can be constantly changed in accordance with the change in the rotational speed of the tank type fluid coupling 4, so that the rotational speed of the output carrier 23 also changes.

The input power is split into two paths through the input shaft 1, one is transmitted to the input small ring gear 21, the other is transmitted to the input pinion 28 via the output gear pair 8, and the input small ring gear 21 passes the power transmitted thereto through the output carrier 23. The upper planetary gear 20 merges with the output carrier 23, and the output carrier 23 is split into two paths by coupling the output gear pair 7, and is transmitted to the input carrier 27 at one time. At this time, the input carrier 27 and the input pinion 28 transmit The respective powers are converge to the output ring gear 29 through the planetary gears 20 on the input carrier 27, and the output ring gear 29 is transmitted to the output shaft 5 of the present invention, thereby realizing the external output of the engine power through the output shaft 5.

When the input power of the engine increases or the resistance of the output shaft 5 decreases, the power of the other path transmitted to the input gear 26 through the input gear pair 6 increases, and the input gear 26 passes through the planetary gear 20 on the fixed carrier 25. The power is transmitted to the output gear 24, and the output gear 24 is transmitted to the input large ring gear 22 through the tank type fluid coupling 4, that is, the input power of the input large ring gear 22 is increased, and the small ring gear 21 is input. The input large ring gear 22 converges the planetary gears 20 transmitted to the respective powers through the output carrier 23 to the output carrier 23, and the output carrier 23 repeats the above process to continuously change the rotational speed transmitted to the input carrier 27. The input carrier 27 and the input pinion 28 converge the planetary gear 20 transmitted to the respective power through the input carrier 27 to the output ring gear 29, and the output ring gear 29 is transmitted to the output shaft 5 of the present invention, thereby realizing The power of the engine is externally output through the output shaft 5.

For the present invention, when the rotational speed of the input shaft 1 is constant, the rotational speed input to the carrier 27 varies with the input power or running resistance of the vehicle, and the lower the resistance, the higher the rotational speed transmitted to the input carrier 27. The higher, conversely, the lower, thereby realizing the composite tank type fluid coupling that 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 small ring gear 21, the other is transmitted to the input pinion 28 via the output gear pair 8, and the input small ring gear 21 converges the power transmitted thereto through the planetary gears 20 on the output carrier 23. On the output planet carrier 23, the output planet carrier 23 is split into two paths by coupling the output gear pair 7, one way to the input planet carrier 27, at this time, the input planet carrier 27 and the input pinion 28 merge the planetary gear 20 transmitted to the respective power through the input carrier 27 to the output ring gear 29, and the output ring gear 29 is transmitted to the output shaft 5 of the present invention, thereby realizing the power of the engine. It is output to the outside through the output shaft 5.

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 passes through the input gear. The power delivered by the secondary 6 to the input gear 26 is increased, the input gear 26 transmits power to the output gear 24 via the planet gears 20 on the fixed planet carrier 25, and the output gear 24 passes through the tank-type fluid coupling 4 The input power to the input large ring gear 22, i.e., the input large ring gear 22, increases, and the input small ring gear 21, the input large ring gear 22, transmits the respective power through the planetary gear 20 on the output carrier 23. Converging on the output carrier 23, the output carrier 23 repeats the above process, so that the rotational speed transmitted to the input carrier 27 is constantly changing, and the input carrier 27 and the input pinion 28 transmit the respective powers through the input carrier 27. The planetary gear 20 merges with the output ring gear 29, and the output ring gear 29 is transmitted to the output shaft 5 of the present invention. When the torque transmitted to the output shaft 5 is transmitted to the drive wheel through the transmission system, When the gravitation is enough to further overcome the resistance of the automobile, the car continues to accelerate, and the rotational speed of the output end 42 of the tank type fluid coupling 4 is gradually increased, and the rotational speed of the input large ring gear 22 is also gradually increased. High, so that the rotational speeds on the output carrier 23, the input carrier 27, and the output shaft 5 are continuously increased.

Claims (2)

Composite box type fluid coupling and starter, including input shaft (1), input gear (3), input gear pair (4), output shaft (5), empty gear mechanism (6), cabinet Hydraulic coupling (7), fixed one-way clutch (8), starter gear pair (9), overrunning clutch (10), starting gear pair (11), electromagnetic clutch (12), coupling shaft (13), The utility model is characterized in that a planetary gear (20), an input planet carrier (21), an input gear (22), an output large ring gear (23) and an input are arranged between the input shaft (1) and the output shaft (5). Ring gear (24), fixed planet carrier (25), output ring gear (26), coupled input planet carrier (27), fixed gear (28), output gear (29), input shaft (1) and start gear pair ( 11) The output gear (112) and the input end (101) of the overrunning clutch (10) are coupled, the output end (102) of the overrunning clutch (10) and the input gear (22) and the output gear of the starter gear pair (9) (92) The output gear (92) of the starter gear pair (9) cooperates with the input gear (91) of the starter gear pair (9), and the input gear (22) passes through the input carrier (21). Planetary gear (20) and input planet carrier (21), output large teeth The ring (23) cooperates with each other, the output large ring gear (23) meshes with the input ring gear (24), the coupling shaft (13) and the input ring gear (24), the input end (121) of the electromagnetic clutch (12), and the input. The input gear (41) of the gear pair (4) is coupled, the output gear (42) of the input gear pair (4) is coupled to the input end (61) of the neutral gear mechanism (6), and the output of the idle gear mechanism (6) The end (62) is coupled to the output shaft (5), the output end (122) of the electromagnetic clutch (12) is coupled to the input gear (111) of the start gear pair (11), and the input ring gear (24) is coupled to the carrier (25). The upper planetary gear (20) cooperates with the fixed carrier (25) and the output ring gear (26), the output ring gear (26) meshes with the input gear (3), the input gear (3) and the input input carrier (27) coupling, coupling the input planet carrier (27) with the fixed gear (28) and the output gear (29) through the planetary gear (20) thereon, and fixing the carrier (25), the fixed gear (28), and The input end (81) of the fixed one-way clutch (8) is coupled to the fixed component, the output gear (29) is coupled to the input end (71) of the tank type fluid coupling (7), and the tank type fluid coupling ( 7) output (72) and fixed one-way Clutch (8) the output (82) and the input planet carrier (21) is coupled. A composite tank type fluid coupling, comprising an input shaft (1), a one-way clutch (3), a tank type fluid coupling (4), an output shaft (5), an input gear pair (6), The output gear pair (7) and the output gear pair (8) are characterized in that: a planetary gear (20) and an input small ring gear (21) are arranged between the input shaft (1) and the output shaft (5). Input large ring gear (22), output carrier (23), output gear (24), fixed carrier (25), input gear (26), input carrier (27), input pinion (28), output a ring gear (29), an input shaft (1) coupled to the input small ring gear (21) and an input gear (81) of the output gear pair (8), an output gear (82) of the output gear pair (8) and an input pinion (28) Coupling, the input small ring gear (21) cooperates with the input large ring gear (22) and the output planet carrier (23) through the planetary gear (20) on the output carrier (23), and outputs the planet carrier (23) ) coupled to the input gear (71) of the coupled output gear pair (7), coupled to the output gear (72) of the output gear pair (7) and the input carrier (27) and the input gear (61) of the input gear pair (6) Coupling, the output gear (62) of the input gear pair (6) is coupled with the input gear (26) The input gear (26) cooperates with the output gear (24) and the fixed carrier (25) through the planetary gear (20) on the fixed carrier (25), fixes the carrier (25) and the one-way clutch (3) The input end (31) is fixed to the fixed component, the output gear (24) is coupled to the input end (41) of the tank type fluid coupling (4), and the output of the tank type fluid coupling (4) ( 42) coupled with the output end (32) of the one-way clutch (3) and the input large ring gear (22), the planetary gear (20) and the input pinion (28) and the output teeth of the input carrier (27) passing therethrough The ring (29) cooperates with each other, and the output ring gear (29) is coupled to the output shaft (5).

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