HK1227469A - A compound type of double pump wheel hydraulic torque converter and starter - Google Patents

Description

Compound double-pump-impeller hydraulic torque converter and starter

Technical Field

The invention belongs to the field of a hydraulic torque converter and a starter, and particularly relates to a composite double-pump-wheel hydraulic torque converter and a starter for various ground vehicles, ships, railway locomotives and machine tools.

Background

At present, hydraulic torque converters are designed according to the principles of fluid statics and the like, and have low transmitted power and low efficiency; in addition, the cost is high.

Disclosure of Invention

The invention overcomes the defects of the prior art and provides the composite double-pump-wheel hydraulic torque converter and the starter which have the advantages of prolonged service life of the engine, simple structure, convenient operation and control, low cost, energy conservation and high efficiency.

In order to realize the purpose of the invention, the technical scheme adopted by the invention is as follows:

a compound double pump wheel hydraulic torque converter and starter comprises an input shaft 1, an output shaft 3, a fixed one-way clutch 4, a speed change mechanism 5, a one-way clutch 6, an output gear pair 7, a first input gear pair 8, a coupling gear pair 9, a second input gear pair 10, a double pump wheel hydraulic torque converter 11, a starting gear pair 12, an overrunning clutch 13, a starting gear 14 and a neutral gear mechanism 15, wherein an input end 41 of the fixed one-way clutch 4 is coupled with a fixed element, a planetary gear 20, an input pinion 21, an output large gear 22, an input planetary carrier 23, an output double planetary carrier 24, an output small gear ring 25, an input large gear ring 26, an input planetary carrier 27, an output gear ring 28 and an output gear 29 are arranged between the input shaft 1 and the output shaft 3, the input pinion 21 is coupled with an output gear 122 of the starting gear pair 12 and an output end 132 of the overrunning clutch 13, the input end 131 of the overrunning clutch 13 and the output end 62 of the one-way clutch 6 are connected with the input shaft 1, the input pinion 21 is mutually matched with the output gearwheel 22 and the input planet carrier 23 through the planet gear 20 on the input planet carrier 23, the output gearwheel 22 is connected with the input gear 81 of the first input gear pair 8, the output gear 82 of the first input gear pair 8 is connected with the input planet carrier 27, the input planet carrier 27 is mutually matched with the output gear ring 28 and the output gear 29 through the planet gear 20 on the input planet carrier 27, the output gear 29 is connected with the input gear 71 of the output gear pair 7 and the output gear 92 of the coupling gear pair 9, the input end 151 of the idle gear mechanism 15 is connected with the output gear 72 of the output gear pair 7 and the input end 61 of the one-way clutch 6, the output end 152 of the idle gear mechanism 15 is connected with the output shaft 3, the output gear ring 28 is connected with the input large gear ring 26, the large input ring gear 26 is matched with the double output planet carrier 24 and the small output ring gear 25 through the planet gears 20 on the double output planet carrier 24 to work, the double output planet carrier 24 is connected with the input gear 91 of the connecting gear pair 9, the small output ring gear 25 is connected with the input end 51 of the speed change mechanism 5, the output end 52 of the speed change mechanism 5 is connected with the output end 42 of the fixed one-way clutch 4, the input gear 101 of the second input gear pair 10 and the input planet carrier 23, the input gear 102 of the second output gear pair 10 is connected with the input end 111 of the double-pump-wheel hydraulic torque converter 11, the output end 112 of the double-pump-wheel hydraulic torque converter 11 is connected with the input gear 121 of the starting gear pair 12, and the output gear 122 of the starting gear pair 12 is connected with the starting gear 14.

Each element needing to be connected and the elements separated by the other elements can be connected with the other elements by adopting a hollow or connecting frame method through or across the other elements; when the coupled elements are gears or ring gears, they are meshed or coupled with each other; the transmission ratios of the gear pairs and the speed change mechanism are designed according to actual requirements.

The double-impeller hydraulic torque converter can be replaced by a hydraulic coupler.

When the invention is applied to a vehicle, the change of the output torque and the speed can be automatically changed according to the magnitude of resistance received when the vehicle runs.

The invention has the following advantages:

(1) most of power of the invention is transmitted by the gear ring, the planetary gear, the planet carrier and the gear, so that the transmission power and the transmission efficiency are greatly improved, and the invention has simple structure and is easier to maintain;

(2) the torque conversion and the speed change are automatically completed, high-efficiency transmission can be realized, and the engine and the starter can work in the optimal range except starting;

(3) the invention enables the engine and the starter to run in an economic rotating speed area, namely the engine to work in a rotating speed range with very small pollution emission, and avoids the emission of a large amount of waste gas when the engine runs at idle speed and high speed, thereby reducing the emission of the waste gas and being beneficial to protecting the environment;

(4) the invention can utilize the internal rotation speed difference to play the roles of buffering and overload protection, is beneficial to prolonging the service life of the engine, a transmission system and a starter, and can lead the vehicle to automatically reduce the speed when the running resistance is increased, otherwise, the vehicle can increase the speed, thereby being beneficial to improving the running performance of the vehicle;

(5) the invention ensures that the input power is uninterrupted, can ensure that the vehicle has good acceleration and higher average speed, reduces the abrasion of the engine, prolongs the overhaul interval mileage and is beneficial to improving the productivity;

(6) when the invention is started, the invention has the performance of automatic torque conversion and speed change, the input power is uninterrupted, the impact phenomenon can not occur, the stable starting of the engine can be ensured, the noise is reduced, the starting abrasion of the engine is reduced, and the service lives of the starting motor and the storage battery are prolonged;

(7) the invention reduces the transmission mechanism of the existing starter, reduces the manufacturing cost, and only needs to take braking measures to the starting motor after the engine is started to stop the transmission.

The present invention also relates to a hybrid double-impeller torque converter and a starter used for various land vehicles, ships, railway locomotives, and machine tools.

Drawings

The attached drawings are structural diagrams of the embodiments of the invention.

Detailed Description

The invention will be described in further detail with reference to the following description and accompanying drawings:

example (b):

as shown in fig. 1, a compound double pump impeller hydraulic torque converter and starter comprises an input shaft 1, an output shaft 3, a fixed one-way clutch 4, a speed change mechanism 5, a one-way clutch 6, an output gear pair 7, a first input gear pair 8, a coupling gear pair 9, a second input gear pair 10, a double pump impeller hydraulic torque converter 11, a starting gear pair 12, an overrunning clutch 13, a starting gear 14 and a neutral gear mechanism 15, wherein an input end 41 of the fixed one-way clutch 4 is coupled with a fixed element, a planetary gear 20, an input pinion 21, an output large gear 22, an input carrier 23, an output double carrier 24, an output small gear ring 25, an input large gear ring 26, an input carrier 27, an output gear ring 28 and an output gear 29 are arranged between the input shaft 1 and the output shaft 3, the input pinion 21 is coupled with an output gear 122 of the starting gear pair 12 and an output end 132 of the overrunning clutch 13, the input end 131 of the overrunning clutch 13 and the output end 62 of the one-way clutch 6 are connected with the input shaft 1, the input pinion 21 is mutually matched with the output gearwheel 22 and the input planet carrier 23 through the planet gear 20 on the input planet carrier 23, the output gearwheel 22 is connected with the input gear 81 of the first input gear pair 8, the output gear 82 of the first input gear pair 8 is connected with the input planet carrier 27, the input planet carrier 27 is mutually matched with the output gear ring 28 and the output gear 29 through the planet gear 20 on the input planet carrier 27, the output gear 29 is connected with the input gear 71 of the output gear pair 7 and the output gear 92 of the coupling gear pair 9, the input end 151 of the idle gear mechanism 15 is connected with the output gear 72 of the output gear pair 7 and the input end 61 of the one-way clutch 6, the output end 152 of the idle gear mechanism 15 is connected with the output shaft 3, the output gear ring 28 is connected with the input large gear ring 26, the large input ring gear 26 is matched with the double output planet carrier 24 and the small output ring gear 25 through the planet gears 20 on the double output planet carrier 24 to work, the double output planet carrier 24 is connected with the input gear 91 of the connecting gear pair 9, the small output ring gear 25 is connected with the input end 51 of the speed change mechanism 5, the output end 52 of the speed change mechanism 5 is connected with the output end 42 of the fixed one-way clutch 4, the input gear 101 of the second input gear pair 10 and the input planet carrier 23, the input gear 102 of the second output gear pair 10 is connected with the input end 111 of the double-pump-wheel hydraulic torque converter 11, the output end 112 of the double-pump-wheel hydraulic torque converter 11 is connected with the input gear 121 of the starting gear pair 12, and the output gear 122 of the starting gear pair 12 is connected with the starting gear 14.

The input planet carrier 27 divides the power transmitted to the input planet carrier into two paths through the planet gears 20 on the input planet carrier, wherein one path flows into the output gear 29, the other path flows into the input large gear ring 26 through the output gear ring 28, the input large gear ring 26 divides the power transmitted to the input large gear ring into two paths through the planet gears 20 on the output duplex planet carrier 24, one path flows into the output duplex planet carrier 24, and the other path flows into the output small gear ring 25.

Because the rotating speed distribution relation of each element can be changed, the two power flows are changed according to the change of the rotating speed distribution between the two power flows, when the rotating speed of the output duplex planet carrier 24 and the output gear 29 is zero, the output power is zero, but the moment is not zero, at this time, the input power of the output duplex planet carrier 24 and the output gear 29 is changed from a certain value to the maximum value, the constant value refers to a value obtained by distributing input power according to a planetary gear ratio when the rotation speed of the output duplex planet carrier 24 and the output gear 29 is the same as that of the input large ring gear 26 and the input planet carrier 27 which are matched with each other, the maximum value means the total power input by the input ring gear 26, the input carrier 27, that is, when the two-way power changes, the torque transmitted to the output duplex planet carrier 24, the output gear 29 and the output shaft 3 also changes.

The input power of the starter is transmitted from the starting gear 14 to the input pinion 21 through the output gear 122 of the starting gear pair 12 or the input power of the engine through the input shaft 1 and then the overrunning clutch 13, and the power is transmitted to the output large gear 22 through the planetary gear 20 on the input planet carrier 23, the output large gear 22 transmits the power to the input planet carrier 27 through the first input gear pair 8, the input planet carrier 27 splits the power into two paths through the planetary gear 20 thereon, one path flows into the output gear 29, the other path flows into the input large gear 26 through the output ring gear 28, the input large gear 26 splits the power into two paths through the planetary gear 20 on the output double planet carrier 24, one path flows into the output double planet carrier 24, the other path flows into the input end 51 of the speed change mechanism 5 through the output small gear 25, and the output end 52 of the speed change mechanism 5 splits the power into two paths, one path flows into the input planet carrier 23, the other path flows into the double pump wheel hydraulic torque converter 11 through the second input gear pair 10, then flows into the input pinion 21 through the starting gear pair 12, the power transmitted to the input pinion 21 is merged with the power transmitted to the input pinion 21 by the starter or the engine, and the power flowing into the input planet carrier 23 is transmitted to the output gearwheel 22 through the planet gear 20 on the input planet carrier 23, the output gearwheel 22 repeats the process, so that the torque transmitted to the output duplex planet carrier 24 and the output gear 29 is continuously increased, before the engine is started, the power transmitted to the output gear 29 and the power transmitted to the output gear 29 through the output duplex planet carrier 24 and the coupling gear pair 9 are transmitted to the input end 151 of the idle gear mechanism 15 through the output gear pair 7, and then transmitted to the engine crankshaft through the one-way clutch 6 and the input shaft 1, after the engine is started, the power transmitted to the output gear 29 by engaging the idle gear mechanism 15 and the power transmitted to the output gear 29 by the output double-planet carrier 24 through the coupling gear pair 9 are transmitted to the output shaft 3 of the invention through the output gear pair 7 and the idle gear mechanism 15, so that the power of the engine is output to the outside through the output shaft 3.

According to the invention, when the rotating speed of the input shaft 1 is unchanged, the torque on the output duplex planet carrier 24, the output gear 29 and the output shaft 3 changes along with the change of the rotating speed, the lower the rotating speed is, the larger the torque is transmitted to the output duplex planet carrier 24, the output gear 29 and the output shaft 3, and vice versa, so that the composite double-pump-wheel hydraulic torque converter and the starter can change the torque and the speed along with the difference of the running resistance of the vehicle.

When the invention is used, the power, the rotating speed and the load of the starter input through the starting gear 14 are unchanged, namely the rotating speed and the torque of the input pinion 21 are constant, before the engine is started, the rotating speed of the engine is zero, when the starter is started, because the output shaft 3 is still, namely the output duplex planet carrier 24 and the output gear 29 are still, the input power of the starter is transmitted to the input pinion 21 through the starting gear pair 12, wherein, because no power flows into the input planet carrier 23 at the moment, and the input end 41 of the fixed one-way clutch 4 is connected with a fixed element, the effect of limiting the rotation direction is realized, the input planet carrier 23 can not rotate in the opposite rotation direction of the engine, the rotating speed is zero, at the moment, the power transmitted to the input pinion 21 is transmitted to the output gearwheel 22 through the planet gear 20 on the input planet carrier 23, the output gearwheel 22 transmits the power to the input planet carrier 27 through the first input gearwheel pair 8, the input carrier 27 splits the power into two paths through the planetary gears 20 thereon, one path flows into the output gear 29, the other path flows into the input large ring gear 26 through the output ring gear 28, the input large ring gear 26 splits the power into two paths through the planetary gears 20 on the output double carrier 24, one path flows into the output double carrier 24, the other path flows into the input end 51 of the speed change mechanism 5 through the output small ring gear 25, the output end 52 of the speed change mechanism 5 splits the power into two paths, one path flows into the input carrier 23, the other path flows into the double pump hydraulic torque converter 11 through the second input gear pair 10, and flows into the input pinion 21 through the starting gear pair 12, the power transmitted to the input pinion 21 is merged with the power transmitted to the input pinion 21 by the starter or the engine, and the power flowing into the input carrier 23 is transmitted to the output large gear 22 through the planetary gears 20 on the input carrier 23, the output gearwheel 22 repeats the above process again, so that the torque transmitted to the output double planet carrier 24 and the output gear 29 increases continuously, the power transmitted to the output gear 29 and the power transmitted from the output double planet carrier 24 to the output gear 29 through the coupling gear pair 9 are transmitted to the input end 151 of the idle gear 15 through the output gear pair 7, and then transmitted to the engine crankshaft through the one-way clutch 6 and the input shaft 1, and when the starting force generated by the torque transmitted to the engine crankshaft is enough to overcome the starting resistance of the engine, the engine is started and starts to accelerate.

After the engine is started, the input power, the input rotating speed and the load of the engine are unchanged, namely the rotating speed and the torque of the input shaft 1 are constant, before the automobile starts, the idle gear mechanism 15 is engaged, the rotating speed of the output shaft 3 is zero, the input power of the engine is transmitted to the input pinion 21 through the input shaft 1 and the overrunning clutch 13, wherein, because no power flows into the input planet carrier 23 at the moment, the input end 41 of the fixed one-way clutch 4 is connected with a fixed element to play a role of limiting the steering, the input planet carrier 23 cannot rotate in the opposite direction of the engine, the rotating speed is zero, at the moment, the power transmitted to the input pinion 21 transmits to the output gearwheel 22 through the planet gear 20 on the input planet carrier 23, the output gearwheel 22 transmits to the input planet carrier 27 through the first input gear pair 8, and the input planet carrier 27 divides the power into two paths through the planet gear 20 on the input planet carrier 27, one path flows into the output gear 29, the other path flows into the input large gear ring 26 through the output gear ring 28, the input large gear ring 26 splits the power into two paths through the planet gears 20 on the output double planet carrier 24, one path flows into the output double planet carrier 24, the other path flows into the input end 51 of the speed change mechanism 5 through the output small gear ring 25, the output end 52 of the speed change mechanism 5 splits the power into two paths, one path flows into the input planet carrier 23, the other path flows into the double pump wheel hydraulic torque converter 11 through the second input gear pair 10, then flows into the input small gear 21 through the starting gear pair 12, the power transmitted to the input small gear 21 is merged with the power transmitted to the input small gear 21 by the starter or the engine, and the power flowing into the input planet carrier 23 is transmitted to the output large gear 22 through the planet gears 20 on the input planet carrier 23, and the output large gear 22 repeats the process, the torque transmitted to the output double-planet carrier 24 and the output gear 29 is increased continuously, the power transmitted to the output gear 29 and the power transmitted to the output gear 29 from the output double-planet carrier 24 through the coupling gear pair 9 are transmitted to the output shaft 3 of the invention through the output gear pair 7 and the idle gear mechanism 15, when the torque transmitted to the output shaft 3 and the traction force generated by the transmission to the driving wheel through the transmission system are enough to overcome the starting resistance of the automobile, the automobile starts and starts to accelerate, the rotating speed of the output double-planet carrier 24, the output gear 29 and the output shaft 3 which are connected with the automobile is increased gradually from zero, at the moment, the power flowing into the input planet carrier 23 is reduced gradually, and the torque of the output shaft 3 is reduced along with the increase of the rotating speed.

Claims (1)

1. The utility model provides a compound double pump wheel torque converter and starter, includes input shaft (1), output shaft (3), fixed one way clutch (4), speed change mechanism (5), one way clutch (6), output gear pair (7), first input gear pair (8), coupling gear pair (9), second input gear pair (10), double pump wheel torque converter (11), starting gear pair (12), freewheel clutch (13), starting gear (14), idle gear mechanism (15), input (41) and the fixed component hookup of fixed one way clutch (4), its characterized in that: a planetary gear (20), an input pinion (21), an output gearwheel (22), an input planet carrier (23), an output duplex planet carrier (24), an output small gear ring (25), an input large gear ring (26), an input planet carrier (27), an output gear ring (28) and an output gear (29) are arranged between the input shaft (1) and the output shaft (3), the input pinion (21) is connected with an output gear (122) of the starting gear pair (12) and an output end (132) of the overrunning clutch (13), an input end (131) of the overrunning clutch (13) and an output end (62) of the one-way clutch (6) are connected with the input shaft (1), the input pinion (21) is mutually matched with the output gearwheel (22) and the input planet carrier (23) through the planetary gear (20) on the input planet carrier (23), the output gearwheel (22) is connected with an input gear (81) of the first input gear pair (8), an output gear (82) of a first input gear pair (8) is connected with an input planet carrier (27), the input planet carrier (27) is mutually matched with an output gear ring (28) and an output gear (29) through a planetary gear (20) on the input planet carrier, the output gear (29) is connected with an input gear (71) of an output gear pair (7) and an output gear (92) of a connecting gear pair (9), an input end (151) of an idle gear mechanism (15) is connected with an output gear (72) of the output gear pair (7) and an input end (61) of a one-way clutch (6), an output end (152) of the idle gear mechanism (15) is connected with an output shaft (3), the output gear ring (28) is connected with an input large gear ring (26), the input large gear ring (26) is mutually matched with an output duplex planet carrier (24) and an output small gear ring (25) through a planetary gear (20) on the output duplex planet carrier (24), an output double-gear carrier (24) is connected with an input gear (91) of a connecting gear pair (9), an output small gear ring (25) is connected with an input end (51) of a speed change mechanism (5), an output end (52) of the speed change mechanism (5) is connected with an output end (42) of a fixed one-way clutch (4), an input gear (101) of a second input gear pair (10) and an input planet carrier (23), an input gear (102) of the second output gear pair (10) is connected with an input end (111) of a double-pump-wheel hydraulic torque converter (11), an output end (112) of the double-pump-wheel hydraulic torque converter (11) is connected with an input gear (121) of a starting gear pair (12), and an output gear (122) of the starting gear pair (12) is connected with a starting gear (14).