WO2016112804A1

WO2016112804A1 - Composite axial-flow type hydraulic torque converter and continuously variable transmission

Info

Publication number: WO2016112804A1
Application number: PCT/CN2016/070213
Authority: WO
Inventors: 吴志强
Original assignee: 吴志强
Priority date: 2015-01-16
Filing date: 2016-01-06
Publication date: 2016-07-21
Also published as: HK1216335A1; HK1211667A1; CN104696472A; CN105422783A; CN104696472B; HK1222437A1; CN105333095A; CN108027033A

Abstract

A composite axial-flow type hydraulic torque converter. An output planet carrier (23) is connected to an input gear pair (4), the input gear pair (4) is connected to an input planet carrier (25), an output gear (26) is connected to an input planet carrier (27), an output gear ring (29) is connected to an output shaft (3), an input gear (24), an input pinion (28), and an overrun clutch (5) are connected to an axial-flow type hydraulic torque converter (6), the axial-flow type hydraulic torque converter (6) is connected to an output gear pair (7), and the output gear pair (7) and an input gear ring (21) are connected to an input shaft (1). In addition, also provided is a continuously variable transmission of a composite axial-flow type hydraulic torque converter.

Description

Composite axial flow torque converter and continuously variable transmission

Technical field

The invention belongs to the field of torque converters and shifting, and more particularly to a composite axial-flow torque converter and a continuously variable transmission for various ground vehicles, ships, railway locomotives and machine tools.

Background technique

At present, the torque converter 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 axial-flow hydraulic torque converter and a continuously variable transmission which have the advantages of shortening the service life of the engine, simple structure, convenient operation, low cost, 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 axial flow torque converter comprising an input shaft (1), an output shaft (3), an input gear pair (4), an overrunning clutch (5), an axial flow hydraulic torque converter (6) And an output gear pair (7), wherein the input shaft (1) and the output shaft (3) are provided with a planetary gear (20), an input ring gear (21), a fixed ring gear (22), and an output planet carrier ( 23), input gear (24), input carrier (25), output gear (26), input carrier (27), input pinion (28), output ring gear (29), input ring gear (21) through The planetary gear (20) on the output carrier (23) cooperates with the fixed ring gear (22) and the output carrier (23), and the fixed ring gear (22) and the input end (51) of the overrunning clutch (5) are fixed. The component is coupled, the output carrier (23) is coupled to 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 carrier (25), and the input carrier (25) The planetary gear (20) on it cooperates with the input gear (24) and the output gear (26), the output gear (26) is coupled to the input carrier (27), and the planet on which the planet carrier (27) passes is input. The gear (20) works in conjunction with the input pinion (28) and the output ring gear (29) The output ring gear (29) is coupled to the output shaft (3), the input gear (24), the input pinion (28), and the output end (52) of the overrunning clutch (5) and the axial flow torque converter (6) The output end (62) is coupled, the input end (61) of the axial flow torque converter (6) is coupled to the output gear (72) of the output gear pair (7), and the input gear of the output gear pair (7) (71) and the input ring gear (21) is coupled to the input shaft (1).

A continuously variable transmission of a composite axial flow torque converter, comprising an input shaft (1), an output shaft (3), an input gear pair (4), an input gear (5), a coupling gear pair (6), An overrunning clutch (7), an axial flow torque converter (8), an output gear pair (9), a planetary gear (20) and an output between the input shaft (1) and the output shaft (3) Planet carrier (21), fixed ring gear (22), input gear (23), connecting planet carrier (24), input pinion (25), input bull gear (26), coupling output planet carrier (27), input small Ring gear (28), input large ring gear (29), input carrier (30), input ring gear (31), output ring gear (32), input gear (23) and input gear pair (6) input gear (61) and the input shaft (1) is coupled, and the input gear (23) cooperates with the output carrier (21) and the fixed ring gear (22) through the planetary gear (20) on the output carrier (21) to fix the ring gear. (22) and the input end (71) of the overrunning clutch (7) is coupled to the fixed element, the output carrier (21) is coupled to the input bull gear (26), and the input large gear (26) is coupled to the planet carrier (24) The planetary gear (20) cooperates with the coupled planet carrier (24) and the input pinion (25) The input gear (5) is coupled to the coupling carrier (24) and the input large ring gear (29), and the input large ring gear (29) passes through the planetary gear (20) on the output carrier (27) and the output carrier (27) , Input small ring gear (28) connection, input small ring gear (28), input gear pair (4) input gear (41) and overrunning clutch (7) output (72) and axial flow torque converter The output end (82) of (8) is coupled, the input end (81) of the axial flow torque converter (8) is coupled to the output gear (92) of the output gear pair (9), and the output gear pair (9) is The input gear (91) is coupled to the input shaft (1), the output gear (42) of the coupling gear pair (4) is coupled to the input carrier (25), and the output carrier (27) is coupled to the input ring gear (31). The ring gear (31) cooperates with the input carrier (30) and the output ring gear (32) through the planetary gear (20) on the input carrier (30), and the output ring gear (32) is coupled with the output shaft (3). The input planet carrier (30) is coupled to the output gear (62) of the coupling gear pair (6).

The components that need to be coupled may be directly connected. When separated by other components, the method of coupling a shaft, a hollow or a coupling frame may be adopted, and may be connected through or across several other components; when the coupled component is When the gears or ring gears are engaged or coupled with each other, the components that do not need to be coupled can be rotated relative to each other.

The gear ratios of the gear pairs and the shifting mechanism are designed according to actual needs.

The torque converter can be selected from a fluid coupling, a pressure motor and a hydraulic pump, and an electromagnetic clutch.

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 makes the engine and the starter operate in the economic speed region, that is, the engine works in the range of the very small pollution discharge speed, and avoids the engine discharging a large amount of exhaust gas during the idle speed and high speed operation, thereby reducing the exhaust gas. Emissions are 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 transmission system and the starter. In addition, when the driving 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 speed, reduces the wear of the engine, prolongs the overhaul interval mileage, and is beneficial to improving productivity.

Further, the present invention is a composite axial-flow torque converter and a continuously variable transmission 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; FIG. 2 is a structural view of a second embodiment of the present invention; the connection between two components in the drawing uses a thick solid line to indicate a fixed connection, and a thin solid line indicates 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 axial flow torque converter includes an input shaft 1, an output shaft 3, an input gear pair 4, an overrunning clutch 5, an axial flow torque converter 6, and an output gear. The auxiliary shaft 7 is provided with a planetary gear 20, an input ring gear 21, a fixed ring gear 22, an output carrier 23, an input gear 24, an input carrier 25, an output gear 26, and an input between the input shaft 1 and the output shaft 3. The carrier 27, the input pinion 28, and the output ring gear 29, the input ring gear 21 cooperates with the fixed ring gear 22 and the output carrier 23 through the planetary gears 20 on the output carrier 23, and fixes the ring gear 22 and the overrunning clutch 5 The input end 51 is coupled to a fixed member, the output carrier 23 is coupled to 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 carrier 25, and the input planet carrier 25 is coupled to the planetary gear 20 thereon. The input gear 24 and the output gear 26 cooperate, the output gear 26 is coupled to the input carrier 27, and the input carrier 27 cooperates with the input pinion 28 and the output ring gear 29 through the planetary gear 20 thereon, and outputs the ring gear 29 and the output. Shaft 3 is connected, input gear 24, input small The wheel 28 and the output 52 of the overrunning clutch 5 are coupled to the output 62 of the axial-flow torque converter 6, the input 61 of the axial-flow torque converter 6 being coupled to the output gear 72 of the output gear pair 7 The input gear 71 of the output gear pair 7 and the input ring gear 21 are coupled to the input shaft 1.

The input gear 24 and the input carrier 25 pass the power transmitted thereto through the planetary gears 20 on the input carrier 25 to the output gear 26. The output gear 26 is transmitted to the input carrier 27, the input carrier 27, and the input pinion 28. The power delivered thereto is converged to the output ring gear 29 by the planetary gears 20 on the input carrier 27.

Since the speed distribution relationship of each of the above components can be changed, the two power flows will change according to the change of the rotational speed distribution between the two. When the rotational speed of the input gear 24 and the input pinion 28 is zero, the input carrier 25 and the input planet are input. The frame 27 is reduced in speed, and when the rotational speeds of the input gear 24 and the input pinion 28 are continuously increased, the rotational speeds of the output gear 26 and the output ring gear 29 are also increased, that is, when the input gear 24 is input. When the rotational speed of the pinion gear 28 changes, the rotational speeds of the output gear 26, the output ring gear 29, and the output shaft 3 also change.

The input power is split into two paths via the input shaft 1, and the first path is transmitted to the axial-flow torque converter 6 via the output gear pair 7, and then transmitted to the input gear 24 and the input pinion 28; the second path The ring gear 21 is input, and the power is transmitted to the output carrier 23 through the planetary gears 20 on the output carrier 23, the output carrier 23 is transmitted to the input carrier 25 through the input gear pair 4, the input gear 24, and the input carrier The power transmitted thereto is converged to the output gear 26 through the planetary gears 20 on the input carrier 25, and then transmitted to the input carrier 27, the input carrier 27, the input pinion 28, and the planetary gears on the input carrier 27. The power transmitted thereto is converged to the output ring gear 29 and then transmitted to the output shaft 3, thereby realizing the external output of the engine power through the output shaft 3.

For the present invention, when the rotational speed of the input shaft 1 is constant, the torque on the output gear 26, the output ring gear 29, and the output shaft 3 varies with the change in the rotational speed thereof, and the lower the rotational speed, the transmission to the output gear 26 and the output ring gear 29 And the torque on the output shaft 3 is larger, and conversely, the smaller, in the process, the axial-flow torque converter 6 also acts as a torque, thereby realizing the difference in the driving resistance of the vehicle according to the vehicle. A compound axial-flow torque converter that changes torque and speed.

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 3 is zero, and the input power of the engine passes through the input shaft 1 Passed to the input ring gear 21, and then transmitted to the output carrier 23 through the planetary gears 20 on the output carrier 23, and the output carrier 23 is transmitted to the input carrier 25 through the input gear pair 4, wherein When there is no power or relatively little power flows into the input gear 24 and the input pinion 28, and the input end 51 of the overrunning clutch 5 is coupled with the fixed element to restrict the steering, so that the steering of the input gear 24 and the input pinion 28 cannot be The input steering is reversed and the rotational speed is zero. At this time, the power transmitted to the input carrier 25 is transferred to the output gear 26 through the planetary gear 20 thereon, and then transmitted to the input carrier 27, the input. The planet carrier 27 is again passed through the planet gears 20 on it. The power is converged to the output ring gear 29 and then transmitted to the output shaft 3. When the torque transmitted to the output shaft 3 is transmitted through the transmission system to the driving wheel, the traction force generated is sufficient to overcome the starting resistance of the vehicle, and the car starts and starts to accelerate. The rotational speed of the output end 62 of the axial-flow torque converter 6 is also gradually increased, and the rotational speeds of the input input gear 24 and the input pinion 28 are also gradually increased, thereby causing the output gear 26 and the output ring gear. 29 and the torque of the output shaft 3 decreases as the number of revolutions increases.

Embodiment 2:

As shown in FIG. 2, a continuously variable transmission of a composite axial-flow torque converter includes an input shaft 1), an output shaft 3, an input gear pair 4, an input gear 5, a coupling gear pair 6, and an overrunning clutch. 7. The axial flow torque converter 8 and the output gear pair 9, wherein the input shaft 1 and the output shaft 3 are provided with a planetary gear 20, an output carrier 21, a fixed ring gear 22, an input gear 23, and a coupling. Planet carrier 24, input pinion 25, input bull gear 26, coupling output carrier 27, input small ring gear 28, input large ring gear 29, input carrier 30, input ring gear 31, output ring gear 32, input gear 23 The input gear 61 of the coupling gear pair 6 and the input shaft 1 are coupled. The input gear 23 cooperates with the output carrier 21 and the fixed ring gear 22 through the planetary gears 20 on the output carrier 21 to fix the ring gear 22 and the overrunning clutch 7. The input end 71 is coupled to the fixed member, the output carrier 21 is coupled to the input bull gear 26, and the input bull gear 26 cooperates with the coupling carrier 24 and the input pinion 25 via the planetary gear 20 coupled to the carrier 24, the input gear 5 and Connecting the planet carrier 24 and inputting the large ring gear 29 The input large ring gear 29 is coupled to the output carrier 27 and the input small ring gear 28 via the planetary gears 20 on the output carrier 27, and is input to the small ring gear 28, the input gear 41 of the input gear pair 4, and the output end of the overrunning clutch 7. 72 is coupled to the output end 82 of the axial flow torque converter 8, the input end 81 of the axial flow torque converter 8 is coupled to the output gear 92 of the output gear pair 9, and the input gear 91 of the output gear pair 9 is The input shaft 1 is coupled, the output gear 42 of the coupling gear pair 4 is coupled to the input carrier 25, the output carrier 27 is coupled to the input ring gear 31, and the input ring gear 31 is passed through the planetary gear 20 on the input carrier 30 and the input carrier 30. The output ring gear 32 cooperates, the output ring gear 32 is coupled to the output shaft 3, and the input carrier 30 is coupled to the output gear 62 of the coupling gear pair 6.

The input pinion 25 and the input bull gear 26 converge the power transmitted thereto through the planetary gears 20 coupled to the carrier 24 to the coupled carrier 24, and the coupled carrier 24 is transmitted through the input gear 5 to the input large ring gear 29, The input small ring gear 28, the input large ring gear 29, converges the power transmitted thereto to the coupled output carrier 27 by the planetary gears 20 coupled to the output carrier 27.

Since the speed distribution relationship of each of the above components can be changed, the two power flows will change according to the change of the rotational speed distribution between the two. When the input pinion 25 and the input small ring gear 28 have a rotational speed of zero, the input large gear 26, When the input large ring gear 29 is used to reduce the speed and increase the torque, when the input pinion 25 and the input small ring gear 28 are continuously increased in speed, the rotational speed of the coupled carrier 24 and the coupled output carrier 27 also increases. When the rotational speed of the input pinion 25 and the input small ring gear 28 changes, the rotational speeds of the coupled carrier 24, the coupled output carrier 27, and the output shaft 3 also change.

The input power is split into three paths via the input shaft 1, the first path is transmitted to the input planet carrier 30 via the input gear 23 and the coupling gear pair 6, and the second path is transmitted to the axial flow hydraulic force via the output gear pair 9. The torque device 8 and the axial flow torque converter 8 are further divided into two paths, one path is transmitted to the input small ring gear 28, the other path is transmitted to the input pinion gear 25 via the input gear pair 4, and the third path is input to the input gear 23 And transmitting power to the output carrier 21 through the planetary gears 20 on the output carrier 21, and then to the input bull gear 26, the input pinion 25, and the input bull gear 26 are transmitted through the planetary gears 20 coupled to the carrier 24. The power here is converged to the coupled planet carrier 24, passed through the input gear 5, to the input large ring gear 29, the input small ring gear 28, and the input large ring gear 29 is transmitted through the planet gears 20 coupled to the output planet carrier 27 The power of this is converged to the output output carrier 27, coupled to the output carrier 27 and then transmitted to the input ring gear 31, The input carrier 30 and the input ring gear 31 pass the power transmitted thereto through the planetary gear 20 on the input carrier 30 to the output ring gear 32, and the output ring gear 32 is transmitted to the output shaft 3, thereby realizing the power of the engine. It is output to the outside through the output shaft 3.

For the present invention, when the rotational speed of the input shaft 1 is constant, the torque on the coupled carrier 24, the coupled output carrier 27, and the output shaft 3 varies with the change in the rotational speed thereof, and the lower the rotational speed, the transmission to the coupled carrier 24, the coupling The greater the torque on the output planet carrier 27 and the output shaft 3, and vice versa, the smaller the axial torque converter 8 also acts as a torque converter, thereby enabling the present invention to travel with the vehicle. A continuously variable transmission of a composite axial-flow torque converter that changes torque and speed with different resistance.

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 3 is zero, and the input power of the engine passes through the input shaft 1 Passing to the input gear 23 and transmitting power to the output carrier 21 through the planetary gears 20 on the output carrier 21, and then to the input bull gear 26, wherein no or less power flows into the input pinion at this time. 25. The small ring gear 28 is input, and the input end 71 of the overrunning clutch 7 is coupled to the fixed component to limit the steering, so that the steering of the input pinion 25 and the input small ring gear 28 cannot be opposite to the input steering, and the rotational speed is zero. At this time, the power transmitted to the input bull gear 26 is transferred to the coupled carrier 24 through the planetary gear 20 coupled to the carrier 24, and then transmitted to the input large ring gear 29 through the input gear 5. The input large ring gear 29 converges the power transmitted thereto by the planetary gears 20 coupled to the output carrier 27 to the coupled output carrier 27, and the coupled output carrier 27 is transferred to the input ring gear 31, the input The carrier 30, the input ring gear 31, through the planetary gears 20 on the input carrier 30, converge the power transmitted thereto to the output ring gear 32, and the output ring gear 32 is transmitted to the output shaft 3, when it is transmitted to the output shaft 3. Torque, when the traction force generated by the transmission system to the driving wheel is sufficient to overcome the starting resistance of the vehicle, the car starts and starts to accelerate, and the rotational speed of the output end 82 of the axial torque converter 8 is gradually increased. The rotational speed of the input pinion 25 and the input small ring gear 28 is also gradually increased, so that the torque of the coupled carrier 24, the coupled output carrier 27, and the output shaft 3 decreases as the rotational speed increases.

Claims

A composite axial flow torque converter comprising an input shaft (1), an output shaft (3), an input gear pair (4), an overrunning clutch (5), an axial flow hydraulic torque converter (6) And an output gear pair (7), wherein the input shaft (1) and the output shaft (3) are provided with a planetary gear (20), an input ring gear (21), a fixed ring gear (22), Output carrier (23), input gear (24), input carrier (25), output gear (26), input carrier (27), input pinion (28), output ring gear (29), input ring gear (21) Working with the fixed ring gear (22) and the output carrier (23) through the planetary gears (20) on the output carrier (23), fixing the ring gear (22) and the input end of the overrunning clutch (5) ( 51) coupled with the fixed component, the output carrier (23) is coupled to the input gear (41) of the input gear pair (4), and the output gear (42) of the input gear pair (4) is coupled to the input carrier (25), input The planet carrier (25) cooperates with the input gear (24) and the output gear (26) through the planetary gears (20) thereon, the output gear (26) is coupled with the input carrier (27), and the input carrier (27) passes Planetary gear (20) and input pinion (28), output teeth thereon (29) In cooperation, the output ring gear (29) is coupled to the output shaft (3), the input gear (24), the input pinion (28), and the output end (52) of the overrunning clutch (5) and the axial flow fluid The output end (62) of the torque converter (6) is coupled, the input end (61) of the axial flow torque converter (6) is coupled with the output gear (72) of the output gear pair (7), and the output gear pair The input gear (71) of (7) and the input ring gear (21) are coupled to the input shaft (1).
A continuously variable transmission of a composite axial flow torque converter, comprising an input shaft (1), an output shaft (3), an input gear pair (4), an input gear (5), a coupling gear pair (6), An overrunning clutch (7), an axial flow torque converter (8), and an output gear pair (9), characterized in that: a planetary gear is arranged between the input shaft (1) and the output shaft (3) ( 20), output planet carrier (21), fixed ring gear (22), input gear (23), connecting planet carrier (24), input pinion (25), input large gear (26), coupled output planet carrier (27) ), input small ring gear (28), input large ring gear (29), input planet carrier (30), input ring gear (31), output ring gear (32), input gear (23) and coupling gear pair (6) The input gear (61) and the input shaft (1) are coupled, and the input gear (23) cooperates with the output carrier (21) and the fixed ring gear (22) through the planetary gears (20) on the output carrier (21). The fixed ring gear (22) and the input end (71) of the overrunning clutch (7) are coupled to the fixed element, the output carrier (21) is coupled to the input bull gear (26), and the input large gear (26) is coupled to the planet carrier ( 24) Planetary gear (20) and connecting planet carrier (24), input small teeth (25) In cooperation, the input gear (5) is coupled to the coupled carrier (24) and the input large ring gear (29), and the input large ring gear (29) is passed through the planetary gear (20) on the output carrier (27). The output carrier (27), the input small ring gear (28) are coupled, the input small gear (28), the input gear (41) of the input gear pair (4), and the output end (72) of the overrunning clutch (7) and the shaft The output end (82) of the flow torque converter (8) is coupled, and the input end (81) of the axial flow torque converter (8) is coupled to the output gear (92) of the output gear pair (9). The input gear (91) of the output gear pair (9) is coupled to the input shaft (1), the output gear (42) of the coupling gear pair (4) is coupled to the input carrier (25), and the output carrier (27) and the input teeth are output. The ring (31) is coupled, and the input ring gear (31) cooperates with the input planet carrier (30) and the output ring gear (32) through the planetary gear (20) on the input carrier (30), and outputs the ring gear (32) and The output shaft (3) is coupled, and the input carrier (30) is coupled to the output gear (62) of the coupling gear pair (6).