CN106763550B - Nine-gear double clutch type automatic transmission - Google Patents
Nine-gear double clutch type automatic transmission Download PDFInfo
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- CN106763550B CN106763550B CN201611260576.7A CN201611260576A CN106763550B CN 106763550 B CN106763550 B CN 106763550B CN 201611260576 A CN201611260576 A CN 201611260576A CN 106763550 B CN106763550 B CN 106763550B
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Classifications
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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
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/12—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with means for synchronisation not incorporated in the clutches
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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
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing
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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
- F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention relates to a nine-gear double clutch type automatic transmission, which is characterized in that: the odd-gear input shaft is connected with an odd-gear clutch C1 through a spline, the even-gear input shaft is connected with an even-gear clutch C2 through a spline, the even-gear input shaft is a hollow sleeve shaft, the even-gear input shaft is sleeved on the odd-gear input shaft, and the eight-gear driving gear, the second-gear driving gear, the fourth-sixth-gear driving gear and the front-to-back are sequentially connected to the even-gear input shaft; the first reverse gear driving gear, the third and fifth gear driving gear and the ninth gear driving gear are sequentially connected to the odd-numbered gears input shaft from front to back; the odd-numbered stage input shaft is supported on the transmission shell through an odd-numbered bearing, and the even-numbered stage input shaft is supported on the transmission shell through an even-numbered bearing; the seven-nine-gear synchronizer is arranged on the odd-gear input shaft; the gear shifting device has nine forward gears and one reverse gear, is matched with a front-longitudinal rear-drive vehicle, and has the advantages of ensuring that the vehicle obtains good power performance, economy, gear shifting comfort and rapidness.
Description
Technical Field
The invention relates to a nine-gear double-clutch type automatic transmission, and belongs to the technical field of automatic transmissions of automobiles in the automobile manufacturing industry.
Background
In a dual clutch type automatic transmission, a driving gear of each gear of the transmission is respectively connected with two clutches C1 and C2 arranged on an input shaft according to odd and even gears, and the clutches C1 and C2 alternately transmit power to realize gear switching. When the DCT works, the vehicle runs in a certain gear, the automatic transmission electronic control unit (TCU) judges the next gear to be started according to the signals of the related sensors, and the gear clutch is separated and does not transmit power, so that the hydraulic control electromagnetic valve is instructed to conveniently control the gear shifting executing mechanism to engage the gear in advance, when the vehicle runs to reach a gear shifting point, only the clutch in operation is separated, and the other clutch is engaged, so that the automobile runs in the next gear. During a gear shift, the power of the engine is constantly transmitted to the wheels, so the gear shift process thus completed is a power shift. The vehicle realizes the power gear shifting process, greatly improves the gear shifting comfort, ensures the vehicle to have good economy, and improves the aspects of vehicle oil consumption, emission and the like.
In existing dual clutch automatic transmission designs, a transmission having dual countershafts and intermeshing gear sets uses different dedicated gear pairs to achieve multiple forward and reverse speed ratios. Therefore, in the ratio design of a transmission, the number of gears required is excessive, and particularly in a transmission having a large number of gears, it is more prominent. The invention adopts the design mode of sharing the driving gears, reduces the number of the driving gears, reduces the arrangement space of the transmission, reduces the cost, and is beneficial to the optimization design of the speed ratio of the transmission suitable for the torque ranges of different vehicle types.
Disclosure of Invention
The invention aims to provide a nine-gear double-clutch type automatic transmission, which has nine forward gears and one reverse gear, is matched with a front-longitudinal rear-drive vehicle, and has the advantages of ensuring that the vehicle obtains good dynamic property, economy, gear shifting comfort and rapidness.
The technical scheme of the invention is realized as follows: nine keep off double clutch formula automatic gearbox, its characterized in that: the odd-numbered gear input shaft is connected with the odd-numbered gear clutch C1 through a spline, the even-numbered gear input shaft is connected with the even-numbered gear clutch C2 through a spline, the even-numbered gear input shaft is a hollow sleeve shaft, the even-numbered gear input shaft is sleeved on the odd-numbered gear input shaft,
an eight-gear driving gear, a second-gear driving gear and a fourth-sixth-gear driving gear in the input shaft assembly are sequentially connected to an even-gear input shaft from front to back; the first reverse gear driving gear, the third and fifth gear driving gear and the ninth gear driving gear are sequentially connected to the odd-numbered gears input shaft from front to back; the odd-numbered stage input shaft is supported on the transmission shell through an odd-numbered bearing, and the even-numbered stage input shaft is supported on the transmission shell through an even-numbered bearing; the seven-nine-gear synchronizer is arranged on the odd-gear input shaft;
a second gear driven gear, a fourth gear driven gear, a first gear driven gear, a third gear driven gear, a parking gear and a speed reduction driving gear are sequentially arranged on a second gear, a third gear and a fourth gear intermediate shaft in the second gear, third and fourth gear intermediate shaft assembly from front to back, a second gear and a fourth gear synchronizer is arranged at the position between the second gear driven gear and the fourth gear driven gear, a third gear synchronizer is arranged at the position between the first gear driven gear and the third gear driven gear, the front end and the middle section of the second, third and fourth gear intermediate shaft are supported by a column bearing, and the rear end of the second, third and fourth gear intermediate shaft is supported by a ball bearing;
an eight-gear driven gear, a six-gear driven gear, a reverse gear driven gear, a five-gear driven gear, a nine-gear driven gear and a five-gear, eight-gear and nine-gear reverse gear intermediate shaft speed reducing gear are sequentially arranged on a five-gear, six-gear, eight-gear and nine-gear reverse gear intermediate shaft in the five-gear, eight-gear and nine-gear reverse gear intermediate shaft assembly from front to back, a six-gear and eight-gear synchronizer is arranged between the eight-gear driven gear and the six-gear driven gear, a five-gear reverse gear synchronizer is arranged between the reverse gear driven gear and the five-gear driven gear, the front end and the middle section of the five-gear, six-gear and nine-gear reverse gear intermediate shaft are supported through a column bearing, and the rear end of the five-gear, six-gear and nine-gear reverse gear intermediate shaft is supported through a ball bearing;
the output shaft of the output shaft assembly is respectively connected with a front deceleration driven gear and a rear deceleration driven gear, the output shaft is supported by two conical bearings,
an idler wheel is connected to an idler wheel shaft of the idler wheel shaft assembly, the driving idler wheel and the driven idler wheel adopt a duplex gear structure, and the idler wheel shaft is fixed on the shell;
an eight-gear driven gear on the even-gear input shaft is meshed with the eight-gear driving gear, one side of the four-gear driving gear and one side of the six-gear driving gear are meshed with the six-gear driven gear, and the other side of the four-gear driving gear is meshed with the four-gear driven gear; one side of a three-fifth gear driving gear on the odd-numbered gear input shaft is meshed with a five-gear driven gear, the other side of the three-fifth gear driving gear is meshed with a three-gear driven gear, a reverse gear driving gear is meshed with a first-gear driven gear, and a nine-gear driving gear is meshed with a nine-gear driven gear; the front speed-reducing driven gear of the output shaft is meshed with the speed-reducing gear of the five-six-eight-nine reverse gear intermediate shaft, and the rear speed-reducing driven gear of the output shaft is meshed with the speed-reducing driving gear.
The arrangement positions of the first reverse gear driving gear and the third and fifth gear driving gears on the odd-numbered gears input shaft can be reversed, the arrangement positions of the fifth gear driven gear and the reverse gear driven gear on the fifth, sixth, eighth and ninth reverse gear intermediate shaft are reversed, the arrangement positions of the third gear driven gear and the first gear driven gear on the second, third and fourth gear intermediate shaft are reversed, and the meshing relationship among the gears is unchanged.
The invention has the advantages of more reasonable structure, compactness and simplicity.
Drawings
FIG. 1 is a schematic view of the arrangement of the present invention.
FIG. 2 is a block diagram of the forward and reverse arrangement of the three-to-five speed drive gear and the one reverse drive gear of the present invention.
Detailed Description
The invention is further described below with reference to the accompanying drawings: as shown in fig. 1, the nine-speed double clutch type automatic transmission is characterized in that: the odd-numbered stage input shaft 2 is connected with the odd-numbered stage clutch C1 through a spline, the even-numbered stage input shaft 1 is connected with the even-numbered stage clutch C2 through a spline, the even-numbered stage input shaft 1 is a hollow sleeve shaft, the even-numbered stage input shaft 1 is sleeved on the odd-numbered stage input shaft 2,
an eight-gear driving gear 4, a second-gear driving gear 15 and a fourth-sixth-gear driving gear 7 in the input shaft assembly are sequentially connected to the even-gear input shaft 1 from front to back; the first reverse gear driving gear 20, the third and fifth gear driving gear 21 and the ninth gear driving gear 27 are sequentially connected to the odd-numbered gear input shaft 2 from front to back; the odd-numbered stage input shaft 2 is supported on the transmission housing by an odd-numbered bearing 32, and the even-numbered stage input shaft 1 is supported on the transmission housing by an even-numbered bearing 3; the seven-nine speed synchronizer 26 is arranged on the odd-speed input shaft 2;
a second gear driven gear 33, a fourth gear driven gear 37, a first gear driven gear 36, a third gear driven gear 34, a parking gear 30 and a reduction driving gear 29 are sequentially arranged on a second gear, third gear and fourth gear intermediate shaft 31 from front to back, a second gear and fourth gear synchronizer 28 is arranged at a position between the second gear driven gear 33 and the fourth gear driven gear 37, a third gear synchronizer 35 is arranged at a position between the first gear driven gear 36 and the third gear driven gear 34, the front end and the middle section of the second, third and fourth gear intermediate shaft 31 are supported by a cylindrical bearing 5, and the rear end of the second, third and fourth gear intermediate shaft 31 is supported by a ball bearing 19;
an eight-gear driven gear 6, a six-gear driven gear 9, a reverse gear driven gear 12, a five-gear driven gear 14, a nine-gear driven gear 16 and a five-gear, eight-gear and nine-reverse gear intermediate shaft reduction gear 17 are sequentially arranged on a five-gear, six-gear and eight-gear reverse gear intermediate shaft 18 from front to back in the five-gear, eight-gear and nine-reverse gear intermediate shaft assembly, a six-gear and eight-gear synchronizer 8 is arranged between the eight-gear driven gear 6 and the six-gear driven gear 9, a five-gear reverse gear synchronizer 13 is arranged between the reverse gear driven gear 12 and the five-gear driven gear 14, the front end and the middle section of the five-gear, six-gear and eight-reverse gear intermediate shaft 18 are supported through a column bearing 5, and the rear end of the five-gear, eight-gear and nine-reverse gear intermediate shaft 18 is supported through a ball bearing 19;
the output shaft 23 of the output shaft assembly is respectively connected with a front deceleration driven gear 25 and a rear deceleration driven gear 24, the output shaft 23 is supported by two cone bearings 22,
an idler wheel 10 is connected to an idler wheel shaft 11 of the idler wheel shaft assembly, the driving idler wheel and the driven idler wheel adopt a duplex gear structure, and the idler wheel shaft 11 is fixed on the shell;
the eight-gear driven gear 6 on the even-gear input shaft 1 is meshed with the eight-gear driving gear 4, one side of the four-gear and six-gear driving gear 7 is meshed with the six-gear driven gear 9, and the other side of the four-gear and six-gear driving gear 7 is meshed with the four-gear driven gear 37; one side of a three-five-gear driving gear 21 on the odd-gear input shaft 2 is meshed with a five-gear driven gear 14, the other side is meshed with a three-gear driven gear 34, a reverse gear driving gear 20 is meshed with a first-gear driven gear 36, and a nine-gear driving gear 27 is meshed with a nine-gear driven gear 16; the front reduction driven gear 25 of the output shaft 23 is meshed with the five six eight nine reverse intermediate shaft reduction gear 17, and the rear reduction driven gear 24 of the output shaft 23 is meshed with the reduction driving gear 29.
As shown in fig. 2, the arrangement positions of the first reverse gear driving gear 20 and the third and fifth gears driving gear 21 on the odd-numbered stage input shaft 2 can be reversed front and back, while the arrangement positions of the fifth gear driven gear 14 and the reverse gear driven gear 12 on the fifth, sixth, eighth, and ninth reverse gear intermediate shaft 18 are reversed front and back, and the arrangement positions of the third gear driven gear 34 and the first gear driven gear 36 on the second, third and fourth gear intermediate shaft 31 are reversed front and back, so that the meshing relationship between the gears is unchanged.
When the clutch C1 is combined in operation, power is transmitted to the odd-gear input shaft 2 through the clutch C1, and the odd-gear input shaft 2 is integrally connected with the first, third, fifth, ninth and reverse gear driving gears. For the odd gears, the power is transmitted to the first, third, fifth, ninth and reverse driven gears on the corresponding intermediate shafts through the first, third, fifth, ninth and reverse driving gears of the odd-gear input shaft 2, the power is transmitted to the corresponding intermediate shafts through the synchronizer, and then the power is transmitted to the output shaft 23 through the fifth, sixth, eighth and ninth reverse intermediate shaft reduction gears 17 and the reduction driving gear 29 to output the power. When the clutch C2 is engaged, power is transmitted to the even-numbered stage input shaft 1 via the clutch C2, and the even-numbered stage input shaft 1 is integrally connected with the second, fourth, sixth and eighth-numbered stage drive gears. For the even gear, the power is transmitted to the two, four, six and eight-gear driven gears on the corresponding intermediate shafts by the two, four, six and eight-gear driving gears of the even gear input shaft 1, the power is transmitted to the corresponding intermediate shafts through the synchronizer, and then the power is transmitted to the output shaft 23 through the five, six, eight and nine reverse gear intermediate shaft reduction gear 17 and the reduction driving gear 29 to be output. For the reverse gear, when the clutch C1 is combined, power is transmitted to the idle gear 10 on the reverse gear idle gear shaft 11 by the odd-numbered stage input shaft 2 and the reverse gear driving gear 20 integrally connected with the odd-numbered stage input shaft, and then transmitted to the intermediate shaft 18 through the reverse gear 12 and the synchronizer 13, and is transmitted to the output shaft 23 through the reduction gear 17 to output power. When the vehicle runs in a certain gear, the next gear to be run can be always in an engaged state; when the gear shifting point is reached, the gear shifting action can be completed by only disengaging the clutch in the engaged state and engaging the clutch in the disengaged state, namely switching the working states of the two clutches.
Claims (2)
1. Nine keep off double clutch formula automatic gearbox, its characterized in that: the odd-numbered gear input shaft is connected with the odd-numbered gear clutch C1 through a spline, the even-numbered gear input shaft is connected with the even-numbered gear clutch C2 through a spline, the even-numbered gear input shaft is a hollow sleeve shaft, the even-numbered gear input shaft is sleeved on the odd-numbered gear input shaft,
an eight-gear driving gear, a second-gear driving gear and a fourth-sixth-gear driving gear in the input shaft assembly are sequentially connected to an even-gear input shaft from front to back; the first reverse gear driving gear, the third and fifth gear driving gear and the ninth gear driving gear are sequentially connected to the odd-numbered gears input shaft from front to back; the odd-numbered stage input shaft is supported on the transmission shell through an odd-numbered bearing, and the even-numbered stage input shaft is supported on the transmission shell through an even-numbered bearing; the seven-nine-gear synchronizer is arranged on the odd-gear input shaft;
a second gear driven gear, a fourth gear driven gear, a first gear driven gear, a third gear driven gear, a parking gear and a speed reduction driving gear are sequentially arranged on a second gear, a third gear and a fourth gear intermediate shaft in the second gear, third and fourth gear intermediate shaft assembly from front to back, a second gear and a fourth gear synchronizer is arranged at the position between the second gear driven gear and the fourth gear driven gear, a third gear synchronizer is arranged at the position between the first gear driven gear and the third gear driven gear, the front end and the middle section of the second, third and fourth gear intermediate shaft are supported by a column bearing, and the rear end of the second, third and fourth gear intermediate shaft is supported by a ball bearing;
an eight-gear driven gear, a six-gear driven gear, a reverse gear driven gear, a five-gear driven gear, a nine-gear driven gear and a five-gear, eight-gear and nine-gear reverse gear intermediate shaft speed reducing gear are sequentially arranged on a five-gear, six-gear, eight-gear and nine-gear reverse gear intermediate shaft in the five-gear, eight-gear and nine-gear reverse gear intermediate shaft assembly from front to back, a six-gear and eight-gear synchronizer is arranged between the eight-gear driven gear and the six-gear driven gear, a five-gear reverse gear synchronizer is arranged between the reverse gear driven gear and the five-gear driven gear, the front end and the middle section of the five-gear, six-gear and nine-gear reverse gear intermediate shaft are supported through a column bearing, and the rear end of the five-gear, six-gear and nine-gear reverse gear intermediate shaft is supported through a ball bearing;
the output shaft of the output shaft assembly is respectively connected with a front deceleration driven gear and a rear deceleration driven gear, the output shaft is supported by two conical bearings,
an idler wheel is connected to an idler wheel shaft of the idler wheel shaft assembly, the driving idler wheel and the driven idler wheel adopt a duplex gear structure, and the idler wheel shaft is fixed on the shell;
an eight-gear driven gear on the even-gear input shaft is meshed with the eight-gear driving gear, one side of the four-gear driving gear and one side of the six-gear driving gear are meshed with the six-gear driven gear, and the other side of the four-gear driving gear is meshed with the four-gear driven gear; one side of a three-fifth gear driving gear on the odd-numbered gear input shaft is meshed with a five-gear driven gear, the other side of the three-fifth gear driving gear is meshed with a three-gear driven gear, a reverse gear driving gear is meshed with a first-gear driven gear, and a nine-gear driving gear is meshed with a nine-gear driven gear; the front speed-reducing driven gear of the output shaft is meshed with the speed-reducing gear of the five-six-eight-nine reverse gear intermediate shaft, and the rear speed-reducing driven gear of the output shaft is meshed with the speed-reducing driving gear.
2. The nine-speed double clutch automatic transmission according to claim 1, wherein the arrangement positions of the first reverse gear driving gear and the third and fifth gear driving gears on the odd-numbered stage input shaft are reversed front and back, the arrangement positions of the fifth gear driven gear and the reverse gear driven gear on the fifth, sixth, eighth, and ninth reverse gear intermediate shaft are reversed front and back, the arrangement positions of the third gear driven gear and the first gear driven gear on the second, third and fourth gear intermediate shaft are reversed front and back, and the meshing relationship between the gears is unchanged.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611260576.7A CN106763550B (en) | 2016-12-30 | 2016-12-30 | Nine-gear double clutch type automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611260576.7A CN106763550B (en) | 2016-12-30 | 2016-12-30 | Nine-gear double clutch type automatic transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106763550A CN106763550A (en) | 2017-05-31 |
| CN106763550B true CN106763550B (en) | 2023-09-08 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201611260576.7A Active CN106763550B (en) | 2016-12-30 | 2016-12-30 | Nine-gear double clutch type automatic transmission |
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| CN (1) | CN106763550B (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR102496252B1 (en) * | 2017-12-04 | 2023-02-08 | 현대자동차주식회사 | Multy-stage dual clutch transmission for hybrid vehicle |
| CN109083987A (en) * | 2018-08-31 | 2018-12-25 | 徐州工程学院 | A kind of nine speed dual clutch gearboxes for all-wheel drive vehicles |
| CN113685508B (en) * | 2020-05-18 | 2024-01-26 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN112067287A (en) * | 2020-09-17 | 2020-12-11 | 中国第一汽车股份有限公司 | Odd-gear input shaft torque fatigue test method and test system |
| CN112709789A (en) * | 2020-12-25 | 2021-04-27 | 中国第一汽车股份有限公司 | Eight-gear double-clutch transmission |
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| CN101949430A (en) * | 2010-08-13 | 2011-01-19 | 中国第一汽车集团公司 | Novel double clutch type automatic transmission (DCT) layout structure |
| CN201827309U (en) * | 2010-09-26 | 2011-05-11 | 北京北齿有限公司 | Nine-gear heavy speed changer |
| JP2012087863A (en) * | 2010-10-19 | 2012-05-10 | Suzuki Motor Corp | Dual clutch transmission |
| CN102182795A (en) * | 2011-03-30 | 2011-09-14 | 浙江万里扬变速器股份有限公司 | Transmission with three shafts and two clutches |
| CN102352913A (en) * | 2011-09-30 | 2012-02-15 | 长城汽车股份有限公司 | Multi-gear vertical dual clutch transmission |
| CN202371093U (en) * | 2011-12-26 | 2012-08-08 | 中国第一汽车股份有限公司 | Second-gear reverse-gear structure of double-clutch type automatic speed changer |
| CN202579992U (en) * | 2012-05-04 | 2012-12-05 | 东风汽车有限公司 | Double-intermediate-shaft double-clutch automatic gearbox structure |
| JP2014005917A (en) * | 2012-06-27 | 2014-01-16 | Masahiro Okubo | Multistage transmission of nine gears for forward drive and one gear for backward drive |
| CN103671751A (en) * | 2013-12-10 | 2014-03-26 | 陕西法士特齿轮有限责任公司 | Nine-gear double-intermediate-shaft transmission |
| CN203809617U (en) * | 2013-12-19 | 2014-09-03 | 比亚迪股份有限公司 | Eight-forward-gear transmission and vehicle with eight-forward-gear transmission |
| CN103821882A (en) * | 2014-03-04 | 2014-05-28 | 东风商用车有限公司 | Double middle shaft transmission structure with hollow shaft synchronism and shifting method thereof |
| CN104896033A (en) * | 2014-03-06 | 2015-09-09 | 曼卡车和巴士股份公司 | Dual clutch transmission, in particular for a commercial vehicle |
| CN105443676A (en) * | 2014-08-29 | 2016-03-30 | 广州汽车集团股份有限公司 | Multi-gear dual clutch transmission and vehicle |
| CN204114031U (en) * | 2014-09-28 | 2015-01-21 | 中国第一汽车股份有限公司 | A kind of novel double-clutch automatic transmission layout |
| CN105299157A (en) * | 2015-11-10 | 2016-02-03 | 中国北方车辆研究所 | Nine-stage transmission |
| CN105465295A (en) * | 2016-01-13 | 2016-04-06 | 北京理工大学 | Nine-speed dual-clutch transmission |
| CN206439350U (en) * | 2016-12-30 | 2017-08-25 | 中国第一汽车股份有限公司 | Nine gear double-clutch automatic transmissions |
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