CN202674221U - Six-gear planetary type hydrodynamic drive device - Google Patents

Six-gear planetary type hydrodynamic drive device Download PDF

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Publication number
CN202674221U
CN202674221U CN 201220344915 CN201220344915U CN202674221U CN 202674221 U CN202674221 U CN 202674221U CN 201220344915 CN201220344915 CN 201220344915 CN 201220344915 U CN201220344915 U CN 201220344915U CN 202674221 U CN202674221 U CN 202674221U
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China
Prior art keywords
gear
output shaft
rotary clutch
gear ring
turbine
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CN 201220344915
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Chinese (zh)
Inventor
饶凤
马晨启
李世鹏
罗静
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Guizhou Winstar Hydraulic Transmission Machinery Co Ltd
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Guizhou Winstar Hydraulic Transmission Machinery Co Ltd
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Abstract

The utility model discloses a six-gear planetary type hydrodynamic drive device which is mainly composed of a shutting and vibration-reduction clutch assembly (A), , a hydraulic torque converter (B), a power output device (5), a built-in trochoid pump (6), a turbine output shaft (18), a planetary gear box (D), an output shaft and the like. The six-gear planetary type hydrodynamic drive device can improve fuel economy of a complete machine, can improve gear shift quality of the gear box, and is compact in structure, small in size and beneficial for distribution of the complete machine.

Description

A kind of six grades of planetary dydraudynamic drive units
Technical field
The present invention relates to mechanical transmission fields, belong to a kind of planetary dydraudynamic drive unit with six gears that advance.
Background technique
The quantity of available forward velocity ratio has determined the number of times that the Engine torque scope repeats in the torque converter, and the non-road vehicle dydraudynamic drive unit of traditional Allison only has five forward gearss, therefore the ratio rank between the speed ratio are larger, the fuel consume point is difficult to close to Available Point, and fuel economy is relatively poor.Therefore, need a kind of the have gears that advance, dydraudynamic drive unit that structure is compacter badly more.By increasing the quantity of dydraudynamic drive unit velocity ratio, can make and be tending towards reasonable than rank size between the velocity ratio, improve the Economy of fuel oil, and make the operator in normal vehicle accelerating process, substantially discover replacement less than velocity ratio, thereby improved the gearshift quality of speed changer.
Summary of the invention:
The technical problem that the present invention solves: in order to improve the Economy of engine fuel, improve the shift quality of speed changer, further reduce and reduce the volume and weight of dydraudynamic drive unit, a kind of have six forward gearss (two overdirve gears are wherein arranged), the compacter planetary dydraudynamic drive unit of complete machine structure are provided.
Technological scheme of the present invention:
A kind of six grades of planetary dydraudynamic drive units of the present invention mainly are made of parts such as locking and damping clutch assembly (A), fluid torque converter (B), power take-off (5), built-in cycloid gear pump (6), turbine output shaft (18), planetary transmission (D), output shafts (10), on the basis that does not increase original clutch, break and planet row quantity, by adopting novel torque converter drive mechanism form, can realize the power output of six forward gearss and a reverse gear, and make complete machine structure compacter.As shown in Figure 2, fluid torque converter (B) adopts traditional single-stage two-phase three element structure, the pump impeller (4) of fluid torque converter (B) is connected with motor, built-in cycloid gear pump (6) respectively, it drives built-in cycloid gear pump (6) by spline and provides power oil and lubricant oil for whole torque converter, this built-in oil pump is positioned at driving mechanism inside, can effectively save the space of dydraudynamic drive unit.Locking and damping clutch (1) are connected with the turbine seat (19) of torque-converters, turbine seat (19) is connected with turbine output shaft (18), under the locking operating mode, the pressure oil that system provides can promote locking and damping clutch piston, realize being rigidly connected of motor and turbine (2), make turbine (2) and motor reach synchronous rotary, turbine seat (19) drives turbine output shaft (18) synchronous rotary by spline simultaneously, this has improved the power utilization of motor, broadening the effect scope.When load was larger, locking and damping clutch piston can be thrown off, and torque-converters can be worked under the bending moment operating mode.
Rotary clutch assembly (C) in turbine output shaft (18) and the planetary transmission (D) is connected, and transmission of power is located to planetary transmission (D).Rotary clutch assembly (C) adopts nesting type structure, consisted of by the first rotary clutch (C1) and the second rotary clutch (C2), the second rotary clutch (C2) is positioned at the outside of the first rotary clutch (C1), share a piston shell, this has effectively saved the bulk of gearbox, reduced weight, the first rotary clutch (C1) is connected with jack shaft (17), the second rotary clutch (C2) is connected with the first sun gear (16), the drive hub of the second rotary clutch (C2) and the second planet carrier (13) spline joint; The first gear ring (7) is the gear ring that floats, and it is by the first break (Z1) braking, and the first planet carrier (15) is connected with the second gear ring (8) by helical teeth, and carries out axially locating by thrust-bearing; The second gear ring (8) is by second brake (Z2) braking, and carry out axially locating with back-up ring, the second sun gear (14) and jack shaft (17) spline joint, the second planet carrier (13) is connected with the 3rd gear ring (9) by helical teeth, and carries out axially locating by thrust-bearing; The 3rd gear ring (9) is by the 3rd break (Z3) braking, and carry out axially locating with back-up ring, the 3rd sun gear (12) and jack shaft (17) spline joint, third planet frame (11) is connected with output shaft (10) by spline.
Description of drawings
Fig. 1 is the structure diagram of a kind of six grades of planetary dydraudynamic drive units of the present invention
Fig. 2 is the structure diagram of the traditional Allison dydraudynamic drive unit with five forward gearss
Among Fig. 1: 1. locking and damping clutch, 2. turbine, 3. guide wheel, 4. pump impeller, 5. power take-off, 6. built-in cycloid gear pump, 7. the first gear ring, 8. the second gear ring, 9. the 3rd gear ring, 10. output shaft, 11. the third planet frame, 12. the 3rd sun gears, 13. second planet carriers, 14. the second sun gear, 15. first planet carriers, 16. first sun gears, 17. jack shaft, 18. turbine output shafts, 19. turbine seats
Embodiment:
Pump impeller (4) is connected with motor, when engine speed is low, fluid torque converter (B) is in the bending moment operating mode, and the output power of motor is absorbed by torque converter turbine (2) after the transmission oil effect, is exported by turbine output shaft (18) afterwards; When engine speed is higher, fluid torque converter (B) is in the locking operating mode, locking and damping clutch piston are connected with turbine seat (19) under the pressure oil effect, motor and turbine (2) form and are rigidly connected, the power that motor provides is directly passed to turbine output shaft (18) through turbine seat (19), motor and turbine output shaft (18) are realized synchronous rotary, thereby improved the efficient of torque converter under high-speed state, broadening the effect scope.Rotary clutch assembly (C) in turbine output shaft (18) and the planetary transmission (D) is connected, when the first rotary clutch (C1) or the second rotary clutch (C2) in conjunction with the time, moment of torsion is passed to planetary transmission (D) and locates.In planetary transmission (D), can realize the transmission of each grade moment of torsion by the combination of controlling the different braking device.
1, one grade, the first rotary clutch (C1) and the 3rd break (Z3) combination under the pressure oil effect that cycloid gear pump (6) provides, third planet frame (11) braking.Moment of torsion by turbine output shaft (18) output passes to jack shaft (17) by the first rotary clutch (C1), then pass to third planet row's (P3) third planet frame (11) by third planet row's (P3) the 3rd sun gear (12), third planet frame (11) by third planet row (P3) passes to output shaft (10) again, by output shaft (10) moment of torsion is exported at last.
2, second gear, the first rotary clutch (C1) and second brake (Z2) combination under the pressure oil effect, the second gear ring (8) braking.Moment of torsion by turbine output shaft (18) output passes to jack shaft (17) by the first rotary clutch (C1), the second sun gear (14) by the second planet row (P2) passes to the second planet carrier (13), pass to the 3rd gear ring (9) by the second planet carrier (13), another part moment of torsion is directly passed to third planet row's (P3) the 3rd sun gear (12) through jack shaft (17), because third planet row's (P3) the 3rd gear ring (9) is differential with the 3rd sun gear (12), moment of torsion passes to output shaft (10) through third planet frame (11), by output shaft (10) moment of torsion is exported at last.
3, third gear, the first rotary clutch (C1) and the first break (Z1) combination under the pressure oil effect, the first gear ring (7) braking.Moment of torsion by turbine output shaft (18) output passes to jack shaft (17) by the first rotary clutch (C1), part moment of torsion passes to the first planet carrier (15) by first sun gear (16) of the first planet row (P2), pass to the second gear ring (8) by the first planet carrier (15), another part moment of torsion is directly passed to second sun gear (14) of the second planet row (P2) through jack shaft (17), because second gear ring (8) of the second planet row (P2) is differential with the second sun gear (14), moment of torsion is through the second planet carrier (13) output torque, and pass to third planet row's (P3) the 3rd gear ring (9), because third planet row's (P3) the 3rd gear ring (9) and third planet row's (P3) the 3rd sun gear (12) is differential, moment of torsion passes to output shaft (10) through third planet frame (11), by output shaft (10) moment of torsion is exported at last.
4, fourth gear, the first rotary clutch (C1) and the second rotary clutch (C2) combination under the pressure oil effect, moment of torsion part by turbine output shaft (18) output passes to the 3rd gear ring (9) by the second rotary clutch (C2) through the second planet carrier (13), another part moment of torsion passes to third planet row's (P3) the 3rd sun gear (12) by the first rotary clutch (C1), because the 3rd sun gear (12), the 3rd gear ring (9) and third planet frame (11) and the synchronized rotation of turbine output shaft (18), moment of torsion passes to output shaft (10) by third planet frame (11) in 1: 1 ratio, by output shaft (10) moment of torsion is exported at last, realized the direct high output of speed changer.
5, five grades, the second rotary clutch (C2) and the first break (Z1) combination under the pressure oil effect, the first gear ring (7) braking.Moment of torsion part by turbine output shaft (18) output passes to the first sun gear (16) by the second rotary clutch (C2), pass to the second gear ring (8) through the first planet carrier (15), pass to the second sun gear (14) by the second gear ring (8) through the planet wheel of the second planet row (P2), pass to the 3rd sun gear (12) by the second sun gear (14) through jack shaft (17), another part moment of torsion passes to the second planet carrier (13) by the second rotary clutch (C2), pass to again the 3rd gear ring (9), because the 3rd gear ring (9) is differential with the 3rd sun gear (12), moment of torsion passes to output shaft (10) by third planet frame (11), by output shaft (10) moment of torsion is exported at last.
6, six grades, the second rotary clutch (C2) and second brake (Z2) combination under the pressure oil effect, the second gear ring (8) braking.Moment of torsion by turbine output shaft (18) output passes to the second planet carrier (13) by the second rotary clutch (C2), then pass to respectively the 3rd gear ring (9) and the second sun gear (14) by the second planet carrier (13), the moment of torsion of the second sun gear (14) passes to the 3rd sun gear (12) through jack shaft (17) again, because the 3rd gear ring (9) is differential with the 3rd sun gear (12), moment of torsion passes to output shaft (10) by third planet frame (11), by output shaft (10) moment of torsion is exported at last.
7, reverse gear, the first break (Z1) and the 3rd break (Z3) combination under the pressure oil effect, the first gear ring (7) and the 3rd gear ring (9) braking, moment of torsion by turbine output shaft (18) output passes to the first sun gear (16) by the second rotary clutch (C2), then pass to the second gear ring (8) through the first planet carrier (15), pass to the second sun gear (14) by the second gear ring (8) through the planet wheel of the second planet row (P2) again, because the second planet carrier (13) and the 3rd gear ring (9) braking, the second sun gear (14) counterrotating, and drive jack shaft (17) and the 3rd sun gear (12) counterrotating, thereby make also counterrotating of third planet frame (11), moment of torsion passes to output shaft (10) by third planet frame (11), by output shaft (10) moment of torsion is exported at last, realized the reverse gear function.
When the present invention realizes each gear clutch, break in conjunction with situation:

Claims (1)

1. six grades of planetary dydraudynamic drive units, mainly be made of locking and damping clutch assembly (A), fluid torque converter (B), power take-off (5), built-in cycloid gear pump (6), turbine output shaft (21), planetary transmission (D), output shaft (10), it is characterized in that: the pump impeller (4) of fluid torque converter (B) is connected with motor, built-in cycloid gear pump (6) respectively; Locking and damping clutch (1) are connected with the turbine seat (19) of torque-converters, turbine seat (19) is connected with turbine output shaft (18), and the rotary clutch assembly (C) in turbine output shaft (18) and the planetary transmission (D) is connected; Rotary clutch assembly (C) adopts nesting type structure, consisted of by the first rotary clutch (C1) and the second rotary clutch (C2), the second rotary clutch (C2) is positioned at the outside of the first rotary clutch (C1), share a piston shell, the first rotary clutch (C1) is connected with jack shaft (17), the second rotary clutch (C2) is connected with the first sun gear (16), the drive hub of the second rotary clutch (C2) and the second planet carrier (13) spline joint; The first gear ring (7) is the gear ring that floats, it is by the first break (Z1) braking, the first planet carrier (15) is connected with the second gear ring (8) by helical teeth, and carry out axially locating by thrust-bearing, the second gear ring (8) is by second brake (Z2) braking, and carry out axially locating with back-up ring, the second sun gear (14) and jack shaft (17) spline joint, the second planet carrier (13) is connected with the 3rd gear ring (9) by helical teeth, and carry out axially locating by thrust-bearing, the 3rd gear ring (9) is by the 3rd break (Z3) braking, and carry out axially locating with back-up ring, the 3rd sun gear (12) and jack shaft (17) spline joint, third planet frame (11) and output shaft (10) spline joint.
CN 201220344915 2012-07-13 2012-07-13 Six-gear planetary type hydrodynamic drive device Active CN202674221U (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103573960A (en) * 2013-10-22 2014-02-12 重庆大学 Electromechanical hydraulic hybrid power transmission device for cutting part of coal mining heading machine
CN113374839A (en) * 2021-05-31 2021-09-10 北方汤臣传动科技有限公司 Six-gear automatic transmission for low-speed heavy-duty vehicle

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103573960A (en) * 2013-10-22 2014-02-12 重庆大学 Electromechanical hydraulic hybrid power transmission device for cutting part of coal mining heading machine
CN103573960B (en) * 2013-10-22 2016-08-17 重庆大学 Mine with cutting part of heading machine mechanical electronic hydraulic composite power actuating device
CN113374839A (en) * 2021-05-31 2021-09-10 北方汤臣传动科技有限公司 Six-gear automatic transmission for low-speed heavy-duty vehicle

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