CN202203359U - Multi-gear planet type hydraulic gearbox transmission mechanism - Google Patents
Multi-gear planet type hydraulic gearbox transmission mechanism Download PDFInfo
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- CN202203359U CN202203359U CN 201120150436 CN201120150436U CN202203359U CN 202203359 U CN202203359 U CN 202203359U CN 201120150436 CN201120150436 CN 201120150436 CN 201120150436 U CN201120150436 U CN 201120150436U CN 202203359 U CN202203359 U CN 202203359U
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The utility model discloses a multi-gear planet type hydraulic gearbox transmission mechanism, mainly comprising a lock and vibration reduction clutch assembly (A), a hydraulic torque converter (B), a power output device (5), a built-in cycloid gear pump (6), a turbine output axle (21), a planet gearbox (D), an output axle (14), a reducer assembly (E) and the like. On the basis of not increasing the numbers of the existing clutch, the brake and the planet line, the power output using seven forward gears and one backward gear is realized by the hydraulic gearbox transmission mechanism. The multi-gear planet type hydraulic gearbox transmission mechanism has features of compact structure and relatively small volume and facilitates the arrangement of the whole device.
Description
Technical field
The present invention relates to mechanical transmission fields, belong to a kind of many gears planetary trnamission driving mechanism.
Background technique
The planetary trnamission transmission device generally is made up of fluid torque converter and mechanical planetary transmission, is characterized in same shaft drive, is applicable to the machinery of coaxial arrangement, unidirectional output; And planetary compact structure, specific volume power density is big, is applicable to high-power machinery and requires to arrange compact machinery and vehicle.The adaptive performance of this transmission device is very strong, can make vehicle regulate running state automatically, has become the main transmission device of non-on-highway vehicle transmission systems such as heavy duty dump truck, scraper, excavator, vibrating roller, multipurpose engineering truck at present.
" vehicle hydraulic transmission " National Defense Industry Press front page in June nineteen eighty-three has been introduced the non-road vehicle dydraudynamic drive unit of Allison for the 345th page; The torque converter that is applied to mine, engineering machinery field at present still extensively adopts this hydraudynamic drive structure; Such dydraudynamic drive unit is made up of the fluid torque converter of band lockup clutch, six grades of planetary transmissions and hydraulic retarder, exports with the power that can produce six forward gearss and a reverse gear after the Engine Matching.But increasingly sophisticated along with the development of technology and field operation environment; Mine, the non-on-highway vehicle of engineering machinery field 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 has satisfied not 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 the load condition in order to improve mobile speed; Under the constant situation of engine performance, need the littler hypervelocity gear of velocity ratio; And traditional dydraudynamic drive unit with six gears that advance has only a hypervelocity gear, and velocity ratio is relatively large, is difficult to satisfy the needs of real work.
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 has only six forward gearss at most; Therefore the ratio rank between the speed ratio are bigger; The fuel consume point is difficult to approach 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 that the volume and weight of complete machine is bigger, can not satisfy the requirement of modernized camp equipment to the miniaturization of dydraudynamic drive unit body.Therefore, need a kind of compacter more dydraudynamic drive units of gear, structure that advance that have badly more.Through 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, discover replacement basically, thereby improved the gearshift quality of speed changer less than velocity ratio.
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, the engineering machinery field non-on-highway vehicle of modernization and the technical performance requirement new of high-power implement to planetary dydraudynamic drive unit; On the basis that does not increase original clutch, break and planet row quantity, a kind of compact more torque converter driving mechanism of seven forward gearss (two overdirve gears are wherein arranged), complete machine structure that has is provided.
Technological scheme of the present invention:
A kind of many gears planetary trnamission of the present invention driving mechanism mainly is made up of locking and damping clutch assembly (A), fluid torque converter (B), PTO (5), built-in cycloid gear pump (6), turbine output shaft (21), planetary transmission (D), output shaft (14), speed reducer assembly parts such as (E); On the basis that does not increase original clutch, break and planet row quantity; Through 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 element structures; 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) through spline and for whole torque converter power oil and lubricant oil is provided, and this built-in oil pump is positioned at driving mechanism inside, can effectively practice thrift the space of dydraudynamic drive unit.Locking and damping clutch (1) are connected with the turbine seat (22) of torque-converters, and 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 rotation, turbine seat (22) drives turbine output shaft (21) rotation synchronously through spline simultaneously; This has improved the power utilization of motor, broadening the effect scope.When load was big, locking and damping clutch piston can be thrown off, and torque-converters can be worked under the bending moment operating mode.
Turbine output shaft (21) is connected with the interior rotary clutch assembly (C) of planetary transmission (D), and transmission of power is located to planetary transmission (D).Rotary clutch assembly (C) adopts nesting type structure; Constitute by first rotary clutch (C1) and second rotary clutch (C2); Second rotary clutch (C2) is positioned at the outside of first rotary clutch (C1), a shared piston shell, and this has effectively practiced thrift the bulk of gearbox; Reduced weight; First rotary clutch (C1) is connected with jack shaft (20), and second rotary clutch (C2) is connected with first sun gear (7), and the drive hub of second rotary clutch (C2) is connected with second planet carrier (18) spline; First gear ring (9) is the gear ring that floats, and it is through first break (Z1) braking, and first planet carrier (8) is connected with second gear ring (10) through helical teeth, and carries out axially locating by thrust-bearing; Second gear ring (10) is braked through second break (Z2), and carries out axially locating with back-up ring, and second sun gear (19) is connected with jack shaft (20) spline, and second planet carrier (18) is connected with the 3rd gear ring (11) through helical teeth, and carries out axially locating by thrust-bearing; The 3rd gear ring (11) is through the 3rd break (Z3) braking; And carry out axially locating with back-up ring; The 3rd sun gear (17) is connected with jack shaft (20) spline; The third line star frame (16) is connected with output shaft (14) spline, and carries out axially locating by thrust-bearing, and the 3rd gear ring (11) is connected with the 4th sun gear (15) through helical teeth and spline; It is as a whole that fourth line star frame external toothing (23) and fourth line star frame (24) are connected through spline, and carry out axially locating with back-up ring; Fourth line star frame (24) is braked through the 4th break (Z4), and is connected with output shaft (14) through tooth hub (12).
Retarder is arranged in the back of whole torque converter driving mechanism, and is connected with output shaft (14) through spline, is convenient to like this according to the applying working condition decision of vehicle whether retarder is installed.In addition, also can realize the variation of gear number through reducing fourth line star row (P4) and the 4th break (Z4) according to actual needs, thereby can further dwindle and alleviate the volume and the weight of dydraudynamic drive unit.
Description of drawings
Fig. 1 is the structure diagram of a kind of many gears planetary trnamission of the present invention driving mechanism
Fig. 2 is the structure diagram of traditional Allison dydraudynamic drive unit with six forward gearss
Among Fig. 1: 1. locking and damping clutch, 2. turbine, 3. guide wheel, 4. pump impeller, 5. PTO; 6. built-in cycloid gear pump, 7. first sun gear, 8. first planet carrier, 9. first gear ring, 10. second gear ring; 11. the 3rd gear ring, 12. tooth hubs, 13. retarders, 14. output shafts, 15. the 4th sun gears; 16. the third line star frame, 17. the 3rd sun gears, 18. second planet carriers, 19. second sun gears, 20. jack shafts; 21. turbine output shaft, 22. turbine seats, 23. fourth line star frame external toothings, 24. fourth line star framves
Among Fig. 2: a. lockup clutch, b. PTO, d. retarder, e. external oil pump
Embodiment:
Pump impeller (4) is connected with motor, and when engine speed was low, fluid torque converter (B) was in the bending moment operating mode, and the output power of motor is absorbed by torque-converters 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, and locking and damping clutch piston are connected with turbine seat (22) under the pressure oil effect, and motor and turbine (2) form and be 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 rotation synchronously, thereby have improved the efficient of torque converter under high-speed state, broadening the effect scope.Turbine output shaft (21) is connected with the interior rotary clutch assembly (C) of planetary transmission (D), and when first rotary clutch (C1) or second rotary clutch (C2) combination, 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 through the combination of controlling the different braking device.
1, neutral gear, the 3rd break (Z3) combine under the pressure oil effect that cycloid gear pump (6) provides, the 3rd gear ring (11) braking.Because first rotary clutch (C1) and second rotary clutch (C2) are in disengaged condition, the moment of torsion of being exported by turbine output shaft (21) can not pass to planetary transmission (D), whole gearbox inactivity output.
2, one grade, first rotary clutch (C1) and the 4th break (Z4) combine under the pressure oil effect that cycloid gear pump (6) provides, fourth line star frame (24) braking.Moment of torsion by turbine output shaft (21) output passes to jack shaft (20) through first rotary clutch (C1); Pass to the third line star row's (P3) the 3rd gear ring (11) then through the third line star row's (P3) the 3rd sun gear (17); Pass to fourth line star row's (P4) the 4th sun gear (15) again by the third line star row's (P3) the 3rd gear ring (11); Then the tooth hub (12) through fourth line star row (P4) passes to output shaft (14), by output shaft (14) moment of torsion is exported at last.
3, second gear, first rotary clutch (C1) and the 3rd break (Z3) combine 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) through first rotary clutch (C1); The 3rd sun gear (17) through the third line star row (P3) passes to the third line star frame (16); Pass to output shaft (14) by the third line star frame (16), by output shaft (14) moment of torsion is exported at last.
4, third gear, first rotary clutch (C1) and second break (Z2) combine under the pressure oil effect, second gear ring (10) braking.Moment of torsion by turbine output shaft (21) output passes to jack shaft (20) through first rotary clutch (C1); Second sun gear (19) that part moment of torsion is arranged (P2) through second planet passes to second planet carrier (18); Pass to the 3rd gear ring (11) by second planet carrier (18); Another part moment of torsion is directly passed to the third line star row's (P3) the 3rd sun gear (17) through jack shaft (20); Because the third line star row's (P3) the 3rd gear ring (11) is differential with the 3rd sun gear (17), moment of torsion passes to output shaft (14) through the third line star frame (16), by output shaft (14) moment of torsion is exported at last.
5, fourth gear, first rotary clutch (C1) and first break (Z1) combine under the pressure oil effect, first gear ring (9) braking.Moment of torsion part by turbine output shaft (21) output passes to first sun gear (7) through second rotary clutch (C2); Pass to second gear ring (10) through first planet carrier (8); Another part moment of torsion passes to second planet row's (P2) on the jack shaft second sun gear (19) and the third line star row's (P3) the 3rd sun gear (17) through first rotary clutch (C1); Because second planet row's (P2) second sun gear (19) is differential with second gear ring (10); Second planet row (P2) is by second planet carrier (18) output torque, and passes to the third line star row's (P3) the 3rd gear ring (11), because the third line star row's (P3) the 3rd gear ring (11) and the third line star row's (P3) the 3rd sun gear (17) is differential; Moment of torsion passes to output shaft (14) through the third line star frame (16), by output shaft (14) moment of torsion is exported at last.
6, five grades; First rotary clutch (C1) and second rotary clutch (C2) combine under the pressure oil effect; Moment of torsion part by turbine output shaft (21) output passes to the 3rd gear ring (11) through second rotary clutch (C2) through second planet carrier (18); Another part moment of torsion passes to the third line star row's (P3) the 3rd sun gear (17) through first rotary clutch (C1); Because the 3rd sun gear (17), the 3rd gear ring (11) and the third line star frame (16) rotate with speed with turbine output shaft (21); Moment of torsion passes to output shaft (14) by the third line star frame (16) in 1: 1 ratio, at last by output shaft (14) with moment of torsion output, realized the direct high output of speed changer.
7, six grades, second rotary clutch (C2) and first break (Z1) combine under the pressure oil effect, first gear ring (9) braking.Moment of torsion part by turbine output shaft (21) output passes to first sun gear (7) through second rotary clutch (C2); Pass to second gear ring (10) through first planet carrier (8); Pass to second sun gear (19) by second gear ring (10) through second planet row's (P2) planet wheel, pass to the 3rd sun gear (17) by second sun gear (19) through jack shaft (20), another part moment of torsion passes to second planet carrier (18) through second rotary clutch (C2); Pass to the 3rd gear ring (11) again; Because the 3rd gear ring (11) is differential with the 3rd sun gear (17), moment of torsion passes to output shaft (14) by the third line star frame (16), by output shaft (14) moment of torsion is exported at last.
8, seven grades, second rotary clutch (C2) and second break (Z2) combine under the pressure oil effect, second gear ring (10) braking.Moment of torsion by turbine output shaft (21) output passes to second planet carrier (18) through second rotary clutch (C2); Pass to the 3rd gear ring (11) and second sun gear (19) respectively by second planet carrier (18) then; The moment of torsion of second sun gear (19) passes to the 3rd sun gear (17) through jack shaft (20) again; Because the 3rd gear ring (11) is differential with the 3rd sun gear (17), moment of torsion passes to output shaft (14) by the third line star frame (16), by output shaft (14) moment of torsion is exported at last.
9, reverse gear, first break (Z1) and the 3rd break (Z3) combine under the pressure oil effect, first gear ring (9) and the 3rd gear ring (11) braking; Moment of torsion by turbine output shaft (21) output passes to first sun gear (7) through second rotary clutch (C2); Pass to second gear ring (10) through first planet carrier (8) then, pass to second sun gear (19) by second gear ring (10) through second planet row's (P2) planet wheel again, because second planet carrier (18) and the 3rd gear ring (11) braking; Second sun gear (19) counterrotating; And drive jack shaft (20) and the 3rd sun gear (17) counterrotating, thus making also counterrotating of the third line star frame (16), moment of torsion passes to output shaft (14) by the third line star 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.
The combination situation of clutch, break when the present invention realizes each gear:
Claims (1)
1. the driving mechanism of gear planetary trnamission more than a kind; Mainly be made up of locking and damping clutch assembly (A), fluid torque converter (B), PTO (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, and turbine seat (22) is connected with turbine output shaft (21), and turbine output shaft (21) is connected with the interior rotary clutch assembly (C) of planetary transmission (D); Rotary clutch assembly (C) adopts nesting type structure; Constitute by first rotary clutch (C1) and second rotary clutch (C2); Second rotary clutch (C2) is positioned at the outside of first rotary clutch (C1), a shared piston shell, and first rotary clutch (C1) is connected with jack shaft (20); Second rotary clutch (C2) is connected with first sun gear (7), and the drive hub of second rotary clutch (C2) is connected with second planet carrier (18) spline; First gear ring (9) is the gear ring that floats, and it is through first break (Z1) braking, and first planet carrier (8) is connected with second gear ring (10) through helical teeth; And carrying out axially locating by thrust-bearing, second gear ring (10) is through second break (Z2) braking, and carries out axially locating with back-up ring; Second sun gear (19) is connected with jack shaft (20) spline, and second planet carrier (18) is connected with the 3rd gear ring (11) through helical teeth, and carries out axially locating by thrust-bearing; The 3rd gear ring (11) is through the 3rd break (Z3) braking; And carry out axially locating with back-up ring, and the 3rd sun gear (17) is connected with jack shaft (20) spline, and the third line star frame (16) is connected with output shaft (14) spline; And carry out axially locating by thrust-bearing; The 3rd gear ring (11) is connected with the 4th sun gear (15) through helical teeth and spline, and it is as a whole that fourth line star frame external toothing (23) and fourth line star frame (24) are connected through spline, and carries out axially locating with back-up ring; Fourth line star frame (24) is braked through the 4th break (Z4), and is connected with output shaft (14) through tooth hub (12); Retarder is arranged in the back of whole torque converter driving mechanism, and is connected with output shaft (14) through spline.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201120150436 CN202203359U (en) | 2011-05-12 | 2011-05-12 | Multi-gear planet type hydraulic gearbox transmission mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201120150436 CN202203359U (en) | 2011-05-12 | 2011-05-12 | Multi-gear planet type hydraulic gearbox transmission mechanism |
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| Publication Number | Publication Date |
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| CN202203359U true CN202203359U (en) | 2012-04-25 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN 201120150436 Expired - Lifetime CN202203359U (en) | 2011-05-12 | 2011-05-12 | Multi-gear planet type hydraulic gearbox transmission mechanism |
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Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102221076A (en) * | 2011-05-12 | 2011-10-19 | 贵州凯星液力传动机械有限公司 | Multi-gear planet type hydraulic transmission driving mechanism |
| CN103758977A (en) * | 2014-01-09 | 2014-04-30 | 湖北航天技术研究院特种车辆技术中心 | Eight-gear hydraulic automatic speed changer |
| CN105650216A (en) * | 2016-03-23 | 2016-06-08 | 北京汽车股份有限公司 | Automatic transmission and vehicle provided with same |
| CN106594201A (en) * | 2017-01-27 | 2017-04-26 | 广州汽车集团股份有限公司 | Automatic transmission and vehicle |
| CN106678297A (en) * | 2017-01-27 | 2017-05-17 | 广州汽车集团股份有限公司 | Automatic transmission and vehicle |
| CN109469716A (en) * | 2018-12-13 | 2019-03-15 | 贵州凯星液力传动机械有限公司 | A kind of six gear gears of php slurry |
| CN104832608B (en) * | 2014-02-12 | 2019-06-28 | 福特全球技术公司 | Multiple-speed gear-box |
| CN110159733A (en) * | 2019-05-24 | 2019-08-23 | 盛瑞传动股份有限公司 | Oil line arrangement structure and gearbox |
| CN111038246A (en) * | 2019-12-24 | 2020-04-21 | 贵州凯星液力传动机械有限公司 | Planetary gear type hybrid power transmission device |
| CN112984059A (en) * | 2021-04-27 | 2021-06-18 | 北京航空航天大学 | Longitudinal rear-drive planetary gear automatic gearbox |
| CN113108040A (en) * | 2021-03-29 | 2021-07-13 | 北方汤臣传动科技有限公司 | Eight-gear automatic transmission of mining truck integrating hydraulic retarber arranged in parallel shafts |
-
2011
- 2011-05-12 CN CN 201120150436 patent/CN202203359U/en not_active Expired - Lifetime
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102221076B (en) * | 2011-05-12 | 2013-05-08 | 贵州凯星液力传动机械有限公司 | Multi-gear planet type hydraulic transmission driving mechanism |
| CN102221076A (en) * | 2011-05-12 | 2011-10-19 | 贵州凯星液力传动机械有限公司 | Multi-gear planet type hydraulic transmission driving mechanism |
| CN103758977A (en) * | 2014-01-09 | 2014-04-30 | 湖北航天技术研究院特种车辆技术中心 | Eight-gear hydraulic automatic speed changer |
| CN103758977B (en) * | 2014-01-09 | 2016-08-17 | 湖北航天技术研究院特种车辆技术中心 | Eight grades of hydraulic automatic speed variators |
| CN104832608B (en) * | 2014-02-12 | 2019-06-28 | 福特全球技术公司 | Multiple-speed gear-box |
| CN105650216B (en) * | 2016-03-23 | 2017-11-28 | 北京汽车股份有限公司 | Automatic transmission and there is its vehicle |
| CN105650216A (en) * | 2016-03-23 | 2016-06-08 | 北京汽车股份有限公司 | Automatic transmission and vehicle provided with same |
| CN106678297A (en) * | 2017-01-27 | 2017-05-17 | 广州汽车集团股份有限公司 | Automatic transmission and vehicle |
| CN106594201B (en) * | 2017-01-27 | 2018-09-14 | 广州汽车集团股份有限公司 | automatic transmission and vehicle |
| CN106594201A (en) * | 2017-01-27 | 2017-04-26 | 广州汽车集团股份有限公司 | Automatic transmission and vehicle |
| CN109469716A (en) * | 2018-12-13 | 2019-03-15 | 贵州凯星液力传动机械有限公司 | A kind of six gear gears of php slurry |
| CN110159733A (en) * | 2019-05-24 | 2019-08-23 | 盛瑞传动股份有限公司 | Oil line arrangement structure and gearbox |
| CN111038246A (en) * | 2019-12-24 | 2020-04-21 | 贵州凯星液力传动机械有限公司 | Planetary gear type hybrid power transmission device |
| CN113108040A (en) * | 2021-03-29 | 2021-07-13 | 北方汤臣传动科技有限公司 | Eight-gear automatic transmission of mining truck integrating hydraulic retarber arranged in parallel shafts |
| CN112984059A (en) * | 2021-04-27 | 2021-06-18 | 北京航空航天大学 | Longitudinal rear-drive planetary gear automatic gearbox |
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