CN102221076B - Multi-gear planet type hydraulic transmission driving mechanism - Google Patents
Multi-gear planet type hydraulic transmission driving mechanism Download PDFInfo
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- CN102221076B CN102221076B CN 201110122429 CN201110122429A CN102221076B CN 102221076 B CN102221076 B CN 102221076B CN 201110122429 CN201110122429 CN 201110122429 CN 201110122429 A CN201110122429 A CN 201110122429A CN 102221076 B CN102221076 B CN 102221076B
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Abstract
The invention discloses a multi-gear planet type hydraulic transmission driving mechanism which is mainly composed of a locking and vibration reducing clutch assembly (A), a hydraulic torque converter (B), a power output device (5), an internal cycloidal gear pump (6), a turbine output shaft (21), a planet gearbox (D), an output shaft (14), a speed reducer assembly (E) and the like. According to the multi-gear planet type hydraulic transmission driving mechanism disclosed by the invention, the power output of seven advancing gears and one reversing gear can be realized by using the novel hydraulic transmission driving structure form on the basis of not increasing the numbers of the original clutches, brakes and planet lines. The invention has the advantages of compact structure and smaller volume, so the whole machine arrangement is facilitated.
Description
Technical field
The present invention relates to mechanical transmission fields, belong to a kind of many gear planet type hydraulic gearbox transmission mechanisms.
Background technique
The planetary trnamission transmission device generally is made of fluid torque converter and mechanical planetary transmission, is characterized in coaxial transmission, is applicable to the machinery of coaxial arrangement, unidirectional output; And planetary structure is compact, and specific volume power density is large, is applicable to high-power machinery and the machinery and the vehicle that require characteristics of compact layout.The adaptive performance of this transmission device is very strong, can make vehicle automatically regulate running state, has now become the main transmission device of the off-road vehicle transmission systems such as heavy duty dump truck, scraper, excavator, vibrating roller, Multipurpose machineshop car.
The 345th page of " vehicle hydraulic transmission " National Defense Industry Press front page in June nineteen eighty-three introduced the non-road vehicle dydraudynamic drive unit of Allison, the torque converter that is applied at present mine, engineering machinery field still extensively adopts this hydraudynamic drive structure, such dydraudynamic drive unit is by forming with the fluid torque converter of lockup clutch, six grades of planetary transmissions and hydraulic retarder, with the power output that can produce six forward gearss and a reverse gear after Engine Matching.But increasingly sophisticated along with the development of technology and field operation environment, mine, engineering machinery field off-road vehicle and high-power implement improve constantly the technical requirements of transmission for hydraulic variable speed device, and the non-road vehicle dydraudynamic drive unit of traditional Allison with six gears that advance can not meet the job requirements of camp equipment under some specific work environments.For example, a lot of walking type construction machinery equipment are hanging down under load condition in order to improve mobile speed, in the situation that the constant less hypervelocity gear of velocity ratio that needs of engine performance, and traditional dydraudynamic drive unit with six gears that advance only has a hypervelocity gear, and velocity ratio is relatively large, is difficult to satisfy the needs of real work.
In torque converter, the quantity of available forward velocity ratio has determined the number of times that the Engine torque scope repeats, and the non-road vehicle dydraudynamic drive unit of traditional Allison only has at most six forward gearss, therefore the ratio rank between speed ratio are larger, the fuel consume point is difficult to close to Available Point, and fuel economy is relatively poor; Secondly, two rotary clutchs of this dydraudynamic drive unit adopt cascaded structure, its oil pump assy adopts the arrangement of external, and this makes the volume and weight of complete machine larger, can not satisfy the modernization camp equipment to the requirement of dydraudynamic drive unit body miniaturization.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 velocity ratio, improve the Economy of fuel oil, and make the operator substantially discover replacement less than velocity ratio in normal vehicle accelerating process, 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, satisfy mine, engineering machinery field modernization off-road vehicle and the high-power implement technical property requirements new to planetary dydraudynamic drive unit, on the basis that does not increase original clutch, break and planet row quantity, provide a kind of have seven forward gearss (two overdirve gears are wherein arranged), the compacter torque converter driving mechanism of complete machine structure.
Technological scheme of the present invention:
a kind of many gear planet type hydraulic gearbox transmission mechanisms of the present invention are mainly by 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 (14), the parts such as speed reducer assembly (E) consist of, do not increasing original clutch, on the basis of break and planet row quantity, by adopting novel torque converter drive mechanism form, can realize the power output of seven forward gearss and a reverse gear, and make complete machine structure compacter.
As shown in fig. 1, 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, the space that can effectively save dydraudynamic drive unit.Locking and damping clutch (1) are connected with the turbine seat (22) of torque-converters, turbine seat (22) is connected with turbine output shaft (21), 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 (22) drives turbine output shaft (21) 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 (21) and 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 (20), the second rotary clutch (C2) is connected with the first sun gear (7), the drive hub of the second rotary clutch (C2) and the second planet carrier (18) spline joint, the first gear ring (9) is the gear ring that floats, and it is by the first break (Z1) braking, and the first planet carrier (8) is connected with the second gear ring (10) by helical teeth, and carries out axially locating by thrust-bearing, the second gear ring (10) is by second brake (Z2) braking, and carry out axially locating with back-up ring, the second sun gear (19) and jack shaft (20) spline joint, the second planet carrier (18) is connected with the 3rd gear ring (11) by helical teeth, and carries out axially locating by thrust-bearing, the 3rd gear ring (11) is by the 3rd break (Z3) braking, and carry out axially locating with back-up ring, the 3rd sun gear (17) and jack shaft (20) spline joint, third planet frame (16) and output shaft (14) spline joint, and carrying out axially locating by thrust-bearing, the 3rd gear ring (11) is connected with the 4th sun gear (15) by helical teeth and spline, fourth planet frame external toothing (23) is as a whole by spline joint with fourth planet frame (24), and carries out axially locating with back-up ring, fourth planet frame (24) is braked by the 4th break (Z4), and is connected with output shaft (14) by tooth hub (12).
Retarder (F) is arranged in the back of whole torque converter driving mechanism, and is connected with output shaft (14) by spline, is convenient to like this determine whether to install retarder according to the applying working condition of vehicle.In addition, also can realize the variation of gear number by reducing fourth planet row (P4) and the 4th break (Z4) according to actual needs, thereby can further dwindle and alleviate volume and the weight of dydraudynamic drive unit.
Description of drawings
Fig. 1 is the structure diagram of a kind of many gear planet type hydraulic gearbox transmission mechanisms of the present invention
Fig. 2 is the structure diagram of the traditional Allison dydraudynamic drive unit with six forward gearss
In 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 sun gear, 8. the first planet carrier, 9. the first gear ring, 10. the second gear ring, 11. the 3rd gear rings, 12. tooth hubs, 13. retarder, 14. output shaft, 15. the 4th sun gears, 16. third planet framves, 17. the 3rd sun gear, 18. the second planet carrier, 19. second sun gears, 20. jack shafts, 21. turbine output shaft, 22. the turbine seat, 23. fourth planet frame external toothings, 24. fourth planet framves
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 (21) 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 (22) 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 (21) through turbine seat (22), motor and turbine output shaft (21) 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 (21) and 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, neutral gear, the 3rd break (Z3) combination under the pressure oil effect that cycloid gear pump (6) provides, the 3rd gear ring (11) braking.Because the first rotary clutch (C1) and the second rotary clutch (C2) are in disengaged condition, can not pass to planetary transmission (D), whole gearbox inactivity output by the moment of torsion of turbine output shaft (21) output.
2, one grade, the first rotary clutch (C1) and the 4th break (Z4) combination under the pressure oil effect that cycloid gear pump (6) provides, fourth planet frame (24) braking.moment of torsion by turbine output shaft (21) output passes to jack shaft (20) by the first rotary clutch (C1), then the 3rd sun gear (17) of arranging (P3) by third planet passes to third planet row's (P3) the 3rd gear ring (11), passed to again fourth planet row's (P4) the 4th sun gear (15) by third planet row's (P3) the 3rd gear ring (11), then the tooth hub (12) through fourth planet row (P4) passes to output shaft (14), by output shaft (14), moment of torsion is exported at last.
3, second gear, the first rotary clutch (C1) and the 3rd break (Z3) combination under the pressure oil effect, the 3rd gear ring (11) braking.Moment of torsion by turbine output shaft (21) output passes to jack shaft (20) by the first rotary clutch (C1), the 3rd sun gear (17) of arranging (P3) by third planet passes to third planet frame (16), pass to output shaft (14) by third planet frame (16), by output shaft (14), moment of torsion is exported at last.
4, third gear, the first rotary clutch (C1) and second brake (Z2) combination under the pressure oil effect, the second gear ring (10) braking.moment of torsion by turbine output shaft (21) output passes to jack shaft (20) by the first rotary clutch (C1), part moment of torsion passes to the second planet carrier (18) by second sun gear (19) of the second planet row (P2), pass to the 3rd gear ring (11) by the second planet carrier (18), another part moment of torsion is directly passed to third planet row's (P3) the 3rd sun gear (17) through jack shaft (20), differential due to third planet row's (P3) the 3rd gear ring (11) and the 3rd sun gear (17), moment of torsion passes to output shaft (14) through third planet frame (16), by output shaft (14), moment of torsion is exported at last.
5, fourth gear, the first rotary clutch (C1) and the first break (Z1) combination under the pressure oil effect, the first gear ring (9) braking.a moment of torsion part by turbine output shaft (21) output passes to the first sun gear (7) by the second rotary clutch (C2), pass to the second gear ring (10) through the first planet carrier (8), another part moment of torsion passes to second sun gear (19) of the second planet row (P2) on jack shaft and third planet row's (P3) the 3rd sun gear (17) by the first rotary clutch (C1), differential due to second sun gear (19) of the second planet row (P2) and the second gear ring (10), the second planet row (P2) is by the second planet carrier (18) output torque, and pass to third planet row's (P3) the 3rd gear ring (11), differential due to third planet row's (P3) the 3rd gear ring (11) and third planet row's (P3) the 3rd sun gear (17), moment of torsion passes to output shaft (14) through third planet frame (16), by output shaft (14), moment of torsion is exported at last.
6, five grades, the first rotary clutch (C1) and the second rotary clutch (C2) combination under the pressure oil effect, a moment of torsion part by turbine output shaft (21) output passes to the 3rd gear ring (11) by the second rotary clutch (C2) through the second planet carrier (18), another part moment of torsion passes to third planet row's (P3) the 3rd sun gear (17) by the first rotary clutch (C1), due to the 3rd sun gear (17), the 3rd gear ring (11) and third planet frame (16) and the synchronized rotation of turbine output shaft (21), moment of torsion passes to output shaft (14) by third planet frame (16) in the ratio of 1: 1, by output shaft (14), moment of torsion is exported at last, realized the direct high output of speed changer.
7, six grades, the second rotary clutch (C2) and the first break (Z1) combination under the pressure oil effect, the first gear ring (9) braking.a moment of torsion part by turbine output shaft (21) output passes to the first sun gear (7) by the second rotary clutch (C2), pass to the second gear ring (10) through the first planet carrier (8), pass to the second sun gear (19) by the second gear ring (10) through the planet wheel of the second planet row (P2), pass to the 3rd sun gear (17) by the second sun gear (19) through jack shaft (20), another part moment of torsion passes to the second planet carrier (18) by the second rotary clutch (C2), pass to again the 3rd gear ring (11), differential due to the 3rd gear ring (11) and the 3rd sun gear (17), moment of torsion passes to output shaft (14) by third planet frame (16), by output shaft (14), moment of torsion is exported at last.
8, seven grades, the second rotary clutch (C2) and second brake (Z2) combination under the pressure oil effect, the second gear ring (10) braking.moment of torsion by turbine output shaft (21) output passes to the second planet carrier (18) by the second rotary clutch (C2), then pass to respectively the 3rd gear ring (11) and the second sun gear (19) by the second planet carrier (18), the moment of torsion of the second sun gear (19) passes to the 3rd sun gear (17) through jack shaft (20) again, differential due to the 3rd gear ring (11) and the 3rd sun gear (17), moment of torsion passes to output shaft (14) by third planet frame (16), by output shaft (14), moment of torsion is exported at last.
9, reverse gear, the first break (Z1) and the 3rd break (Z3) combination under the pressure oil effect, the first gear ring (9) and the 3rd gear ring (11) braking, moment of torsion by turbine output shaft (21) output passes to the first sun gear (7) by the second rotary clutch (C2), then pass to the second gear ring (10) through the first planet carrier (8), pass to the second sun gear (19) by the second gear ring (10) through the planet wheel of the second planet row (P2) again, due to the second planet carrier (18) and the 3rd gear ring (11) braking, the second sun gear (19) counterrotating, and drive jack shaft (20) and the 3rd sun gear (17) counterrotating, thereby make also counterrotating of third planet frame (16), moment of torsion passes to output shaft (14) by third planet frame (16), by output shaft (14), moment of torsion is exported at last, realized the reverse gear function.
When vehicle needs assisted deceleration, make in retarder (13) housing to be full of transmission liquid, retarder rotor can increase the load of output shaft (14) under the drag effect of transmission liquid, thereby has realized assisted deceleration.When the present invention realizes each gear clutch, break in conjunction with situation:
Claims (1)
1. gear planet type hydraulic gearbox transmission mechanism more than a kind, 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 (14), speed reducer assembly (E), 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 (22) of torque-converters, turbine seat (22) is connected with turbine output shaft (21), and the rotary clutch assembly (C) in turbine output shaft (21) and 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 (20), the second rotary clutch (C2) is connected with the first sun gear (7), the drive hub of the second rotary clutch (C2) and the second planet carrier (18) spline joint, the first gear ring (9) is the gear ring that floats, it is by the first break (Z1) braking, the first planet carrier (8) is connected with the second gear ring (10) by helical teeth, and carry out axially locating by thrust-bearing, the second gear ring (10) is by second brake (Z2) braking, and carry out axially locating with back-up ring, the second sun gear (19) and jack shaft (20) spline joint, the second planet carrier (18) is connected with the 3rd gear ring (11) by helical teeth, and carry out axially locating by thrust-bearing, the 3rd gear ring (11) is by the 3rd break (Z3) braking, and carry out axially locating with back-up ring, the 3rd sun gear (17) and jack shaft (20) spline joint, third planet frame (16) and output shaft (14) spline joint, and carry out axially locating by thrust-bearing, the 3rd gear ring (11) is connected with the 4th sun gear (15) by helical teeth and spline, fourth planet frame external toothing (23) is as a whole by spline joint with fourth planet frame (24), and carry out axially locating with back-up ring, fourth planet frame (24) is by the 4th break (Z4) braking, and be connected with output shaft (14) by tooth hub (12), retarder (F) is arranged in the back of whole torque converter driving mechanism, and is connected with output shaft (14) by spline.
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| Application Number | Priority Date | Filing Date | Title |
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| CN 201110122429 CN102221076B (en) | 2011-05-12 | 2011-05-12 | Multi-gear planet type hydraulic transmission driving mechanism |
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| CN 201110122429 CN102221076B (en) | 2011-05-12 | 2011-05-12 | Multi-gear planet type hydraulic transmission driving mechanism |
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| CN102221076A CN102221076A (en) | 2011-10-19 |
| CN102221076B true CN102221076B (en) | 2013-05-08 |
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| CN 201110122429 Expired - Fee Related CN102221076B (en) | 2011-05-12 | 2011-05-12 | Multi-gear planet type hydraulic transmission driving mechanism |
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Families Citing this family (12)
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| KR102312893B1 (en) * | 2011-12-19 | 2021-10-18 | 알리손 트랜스미션, 인크. | Automatic transmission with improved gear arrangement |
| CN102588551B (en) * | 2012-03-03 | 2015-06-03 | 陕西航天动力高科技股份有限公司 | Hydrodynamic drive system for mine car |
| CN102606708B (en) * | 2012-03-30 | 2015-04-01 | 杭州前进齿轮箱集团股份有限公司 | Multi-gear hydrodynamic transmission applicable to various working conditions |
| CN102913610A (en) * | 2012-10-16 | 2013-02-06 | 中国北方车辆研究所 | Floating gear ring axial positioning mechanism used for high-speed planet row |
| CN105422784A (en) * | 2014-05-07 | 2016-03-23 | 吴志强 | Continuously variable transmission of composite multi-element working wheel hydraulic torque converter |
| CN104696471A (en) * | 2014-07-15 | 2015-06-10 | 三江瓦力特特种车辆有限公司 | Multi-oil-pump hydraulic automatic transmission |
| CN104494425B (en) * | 2014-12-16 | 2017-03-29 | 贵州凯星液力传动机械有限公司 | A kind of variator with transfer case |
| JP6159435B1 (en) * | 2016-03-03 | 2017-07-05 | 株式会社Ｓｕｂａｒｕ | Fluid transmission device |
| CN106402293B (en) * | 2016-09-30 | 2021-02-23 | 中国北方车辆研究所 | Eight-gear planetary automatic transmission |
| CN107178585B (en) * | 2017-06-30 | 2023-08-04 | 贵州凯星液力传动机械有限公司 | High-power hydraulic variable-speed transmission device |
| CN108518458A (en) * | 2018-04-26 | 2018-09-11 | 广西柳工机械股份有限公司 | Loading machine gearbox |
| CN114251449B (en) * | 2021-12-06 | 2024-03-19 | 中国航天科工集团有限公司 | Nested clutch shift control method |
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| CN101592222A (en) * | 2009-06-24 | 2009-12-02 | 贵州凯星液力传动机械有限公司 | A kind of countershaft transmission |
| CN202203359U (en) * | 2011-05-12 | 2012-04-25 | 贵州凯星液力传动机械有限公司 | Multi-gear planet type hydraulic gearbox transmission mechanism |
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2011
- 2011-05-12 CN CN 201110122429 patent/CN102221076B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2622485Y (en) * | 2003-05-30 | 2004-06-30 | 贵州凯星液力传动机械有限公司 | Hydraulic speed variator |
| DE102004041509A1 (en) * | 2004-08-27 | 2006-03-16 | Zf Friedrichshafen Ag | Automobile multi-speed gearbox, with eight forward and two reverse gears, has three planet wheel sets and six switch units between the drive input and output shafts |
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| CN202203359U (en) * | 2011-05-12 | 2012-04-25 | 贵州凯星液力传动机械有限公司 | Multi-gear planet type hydraulic gearbox transmission mechanism |
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