CN106763549B - Novel ten-gear double-clutch type automatic transmission - Google Patents
Novel ten-gear double-clutch type automatic transmission Download PDFInfo
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- CN106763549B CN106763549B CN201611258184.7A CN201611258184A CN106763549B CN 106763549 B CN106763549 B CN 106763549B CN 201611258184 A CN201611258184 A CN 201611258184A CN 106763549 B CN106763549 B CN 106763549B
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten 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
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2051—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with eight engaging means
Abstract
The invention relates to a novel ten-gear double-clutch type automatic transmission, which consists of an input shaft assembly, a two, three, four and eight-gear intermediate shaft assembly, a five, six and ninety reverse gear intermediate shaft assembly, an output shaft assembly and an idler shaft assembly, and is 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, and the even-numbered gear input shaft is sleeved on the odd-numbered gear input shaft; the second reverse gear driving gear, the fourth and sixth gear driving gear and the eighty gear driving gear are sequentially connected to the even gear input shaft from front to back; the three-gear driving gear, the five-gear driving gear, the first-gear driving gear and the nine-gear driving gear are sequentially connected to the odd-gear 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 gear shifting device has ten 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 novel ten-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 novel ten-gear double-clutch type automatic transmission, which has ten 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: the utility model provides a novel ten keep off dual clutch type automatic gearbox comprises input shaft assembly, two three eight keep off jackshaft assemblies, five six ninety reverse gear jackshaft assemblies, output shaft assembly, idler shaft assembly, 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, and the even-numbered gear input shaft is sleeved on the odd-numbered gear input shaft;
the second reverse gear driving gear, the fourth and sixth gear driving gear and the eighty gear driving gear are sequentially connected to the even gear input shaft from front to back; the three-gear driving gear, the five-gear driving gear, the first-gear driving gear and the nine-gear driving gear are sequentially connected to the odd-gear 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;
a second-gear driven gear, a fourth-gear driven gear, an eighth-gear driven gear, a third-gear driven gear, a first-gear driven gear and a reduction driving gear are sequentially arranged on the second-gear, third-gear and fourth-gear intermediate shaft from front to back, a second-gear and fourth-gear synchronizer is arranged between the second-gear driven gear and the fourth-gear driven gear, and a third-gear and eighth-gear synchronizer is arranged between the eighth-gear driven gear and the third-gear driven gear; the first-gear driven gear is provided with a first-gear synchronizer; the front end and the rear end of the two-three-four-eight-gear intermediate shaft are supported on the transmission shell through ball bearings, and the middle section of the two-three-four-eight-gear intermediate shaft is supported through a column bearing;
a reverse gear driven gear, a six-gear driven gear, a ten-gear driven gear, a five-gear driven gear, a parking gear, a nine-gear driven gear and a reduction driving gear are sequentially arranged on the five-six ninety reverse gear intermediate shaft from front to back, a six-reverse gear synchronizer is arranged between the reverse gear driven gear and the six-gear driven gear, and a fifty-gear synchronizer is arranged between the ten-gear driven gear and the five-gear driven gear; ball bearings are supported at the front end, the rear end and the middle position of the five-six ninety-reverse gear intermediate shaft;
the front speed reduction driven gear and the rear speed reduction driven gear on the output shaft are respectively meshed with a two, three, four and eight-gear speed reduction driving gear on a two, three, four and eight-gear intermediate shaft and a five, six, ninety and reverse speed reduction driving gear on a five, six, ninety and reverse speed intermediate shaft, and the output shaft is supported by two conical bearings; a seven-nine-gear synchronizer is arranged between the speed reduction driven gear and the nine-gear driving gear;
an idler wheel is arranged on an idler wheel shaft, a driving idler wheel and a driven idler wheel of the idler wheel are of a duplex gear structure, the idler wheel shaft is fixed on a transmission shell, and the driven idler wheel of the idler wheel is meshed with a reverse gear driven gear;
the four-gear and six-gear driving gear is meshed with the six-gear driven gear and the four-gear driven gear, the two-gear reverse gear driving gear is meshed with the two-gear driven gear and the idler gear, the eighty-gear driving gear is meshed with the ten-gear driven gear and the eight-gear driven gear, the three-gear driving gear is meshed with the three-gear driven gear, the five-gear driving gear is meshed with the five-gear driven gear, the first-gear driving gear is meshed with the first-gear driven gear, and the nine-gear driving gear is meshed with the nine-gear driven gear.
The invention has the advantages of reasonable structure, compactness and simplicity.
Drawings
Fig. 1 is a schematic view of the arrangement of the present invention.
Detailed Description
The invention is further described below with reference to the accompanying drawings: as shown in FIG. 1, the novel ten-gear double-clutch type automatic transmission consists of an input shaft assembly, a two, three, four and eight-gear intermediate shaft assembly, a five, six and ninety reverse gear intermediate shaft assembly, an output shaft assembly and an idler shaft assembly, and is characterized in that: the odd-numbered gear input shaft 2 is connected with the odd-numbered gear clutch C1 through a spline, the even-numbered gear input shaft 1 is connected with the even-numbered gear clutch C2 through a spline, the even-numbered gear input shaft 1 is a hollow sleeve shaft, and the even-numbered gear input shaft 1 is sleeved on the odd-numbered gear input shaft 2;
input shaft assembly
The second reverse gear driving gear 16, the fourth and sixth gear driving gear 20 and the eighty gear driving gear 11 are sequentially connected to the even gear input shaft 1 from front to back; the three-gear driving gear 21, the five-gear driving gear 34, the first-gear driving gear 22 and the nine-gear driving gear 28 are sequentially connected to the odd-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;
middle shaft assembly with two gears, three gears and eight gears
A second gear driven gear 4, a fourth gear driven gear 40, an eighth gear driven gear 39, a third gear driven gear 37, a first gear driven gear 35 and a reduction driving gear 30 are sequentially arranged on the second, third and fourth gear intermediate shaft 31 from front to back, a second and fourth gear synchronizer 29 is arranged at a position between the second gear driven gear 4 and the fourth gear driven gear 40, and a third and eighth gear synchronizer 38 is arranged at a position between the eighth gear driven gear 39 and the third gear driven gear 37; the first-gear driven gear 35 is provided with a first-gear synchronizer 36; the front end and the rear end of the middle shaft 31 of the second, third and fourth eight gears are supported on the transmission shell through ball bearings 5, and the middle section of the middle shaft 31 of the second, third and fourth eight gears is supported through a column bearing 33;
five-six ninety reverse gear intermediate shaft assembly
A reverse gear driven gear 6, a six-gear driven gear 10, a ten-gear driven gear 12, a five-gear driven gear 14, a parking gear 15, a nine-gear driven gear 17 and a reduction driving gear 18 are sequentially arranged on the five-six ninety reverse gear intermediate shaft 19 from front to back, a six-reverse gear synchronizer 7 is arranged at the position between the reverse gear driven gear 6 and the six-gear driven gear 10, and a fifty-gear synchronizer 13 is arranged at the position between the ten-gear driven gear 12 and the five-gear driven gear 14; the front end, the rear end and the middle position of the five-six ninety reverse gear intermediate shaft 19 are supported by ball bearings 5;
output shaft assembly
The front speed reduction driven gear 25 and the rear speed reduction driven gear 26 on the output shaft 24 are respectively meshed with a two, three, four and eight speed reduction driving gear 30 on a two, three, four and eight speed intermediate shaft 31 and a five, six, ninety and reverse speed reduction driving gear 18 on a five, six, ninety and reverse speed intermediate shaft 19, and the output shaft 24 is supported by two conical bearings 23; a seven-nine gear synchronizer 27 is arranged between the speed reduction driven gear 26 and the nine-gear driving gear 28;
idler shaft assembly
An idler wheel 8 is arranged on the idler wheel shaft 9, a driving idler wheel and a driven idler wheel of the idler wheel 8 are of a duplex gear structure, the idler wheel shaft 9 is fixed on a transmission shell, and the driven idler wheel of the idler wheel 8 is meshed with the reverse driven gear 6;
the fourth and sixth gears driving gear 20 is meshed with the sixth gear driven gear 10 and the fourth gear driven gear 40, the second reverse gear driving gear 16 is meshed with the second gear driven gear 4 and the idle gear 8, the eighty gear driving gear 11 is meshed with the tenth gear driven gear 12 and the eighth gear driven gear 39, the third gear driving gear 21 is meshed with the third gear driven gear 37, the fifth gear driving gear 34 is meshed with the fifth gear driven gear 14, the first gear driving gear 22 is meshed with the first gear driven gear 35, and the ninth gear driving gear 28 is meshed with the ninth gear driven gear 17.
When the clutch C1 is engaged, power is transmitted to the odd-numbered stage input shaft 2 via the clutch C1, and the odd-numbered stage input shaft 2 is integrally connected with the first, third, fifth, seventh, ninth, and reverse gear drive gears. For the odd gears, the power is transmitted to the first, third, fifth, seventh, ninth and reverse driven gears on the corresponding intermediate shafts through the first, third, fifth, seventh, 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 24 through the second, third, fourth and eighth gear reduction driving gears 30 and the fifth, sixth, ninety and reverse reduction driving gears 18, so that the power is output. 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 even gears, power is transmitted to two, four, six and eight-gear driven gears on corresponding intermediate shafts by 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 a synchronizer, and then the power is transmitted to the output shaft 24 through a two, three, four and eight-gear reduction driving gear 30 and a five, six, ninety reverse gear reduction driving gear 18 to be output. For the reverse gear, when the clutch C2 is combined, power is transmitted to the idle gear 8 on the reverse gear idle gear shaft 9 by the odd-numbered gear input shaft 1 and the reverse gear driving gear 16 which are integrally connected with the odd-numbered gear input shaft, and then transmitted to the intermediate shaft 19 by the reverse gear 6 and the synchronizer 7, and is transmitted to the output shaft 24 through the five-six-ninety reverse gear reduction driving gear 18 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 (1)
1. The utility model provides a novel ten keep off dual clutch type automatic gearbox comprises input shaft assembly, two three eight keep off jackshaft assemblies, five six ninety reverse gear jackshaft assemblies, output shaft assembly, idler shaft assembly, 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, and the even-numbered gear input shaft is sleeved on the odd-numbered gear input shaft;
the second reverse gear driving gear, the fourth and sixth gear driving gear and the eighty gear driving gear are sequentially connected to the even gear input shaft from front to back; the three-gear driving gear, the five-gear driving gear, the first-gear driving gear and the nine-gear driving gear are sequentially connected to the odd-gear 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;
a second-gear driven gear, a fourth-gear driven gear, an eighth-gear driven gear, a third-gear driven gear, a first-gear driven gear and a reduction driving gear are sequentially arranged on the second-gear, third-gear and fourth-gear intermediate shaft from front to back, a second-gear and fourth-gear synchronizer is arranged between the second-gear driven gear and the fourth-gear driven gear, and a third-gear and eighth-gear synchronizer is arranged between the eighth-gear driven gear and the third-gear driven gear; the first-gear driven gear is provided with a first-gear synchronizer; the front end and the rear end of the two-three-four-eight-gear intermediate shaft are supported on the transmission shell through ball bearings, and the middle section of the two-three-four-eight-gear intermediate shaft is supported through a column bearing;
a reverse gear driven gear, a six-gear driven gear, a ten-gear driven gear, a five-gear driven gear, a parking gear, a nine-gear driven gear and a reduction driving gear are sequentially arranged on the five-six ninety reverse gear intermediate shaft from front to back, a six-reverse gear synchronizer is arranged between the reverse gear driven gear and the six-gear driven gear, and a fifty-gear synchronizer is arranged between the ten-gear driven gear and the five-gear driven gear; ball bearings are supported at the front end, the rear end and the middle position of the five-six ninety-reverse gear intermediate shaft;
the front speed reduction driven gear and the rear speed reduction driven gear on the output shaft are respectively meshed with a two, three, four and eight-gear speed reduction driving gear on a two, three, four and eight-gear intermediate shaft and a five, six, ninety and reverse speed reduction driving gear on a five, six, ninety and reverse speed intermediate shaft, and the output shaft is supported by two conical bearings; a seven-nine-gear synchronizer is arranged between the speed reduction driven gear and the nine-gear driving gear;
an idler wheel is arranged on an idler wheel shaft, a driving idler wheel and a driven idler wheel of the idler wheel are of a duplex gear structure, the idler wheel shaft is fixed on a transmission shell, and the driven idler wheel of the idler wheel is meshed with a reverse gear driven gear;
the four-gear and six-gear driving gear is meshed with the six-gear driven gear and the four-gear driven gear, the two-gear reverse gear driving gear is meshed with the two-gear driven gear and the idler gear, the eighty-gear driving gear is meshed with the ten-gear driven gear and the eight-gear driven gear, the three-gear driving gear is meshed with the three-gear driven gear, the five-gear driving gear is meshed with the five-gear driven gear, the first-gear driving gear is meshed with the first-gear driven gear, and the nine-gear driving gear is meshed with the nine-gear driven gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611258184.7A CN106763549B (en) | 2016-12-30 | 2016-12-30 | Novel ten-gear double-clutch type automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611258184.7A CN106763549B (en) | 2016-12-30 | 2016-12-30 | Novel ten-gear double-clutch type automatic transmission |
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| Publication Number | Publication Date |
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| CN106763549A CN106763549A (en) | 2017-05-31 |
| CN106763549B true CN106763549B (en) | 2023-08-25 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201611258184.7A Active CN106763549B (en) | 2016-12-30 | 2016-12-30 | Novel ten-gear double-clutch type automatic transmission |
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Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107165988B (en) * | 2017-06-23 | 2024-01-30 | 上海粒沣传动技术有限公司 | Two keep off dead axle formula gearbox |
| CN113685506B (en) * | 2020-05-18 | 2024-03-22 | 广州汽车集团股份有限公司 | Ten-gear double-clutch transmission and vehicle |
| CN113685501B (en) * | 2020-05-18 | 2024-03-22 | 广州汽车集团股份有限公司 | Ten-gear double-clutch transmission and vehicle |
| CN113775706A (en) * | 2020-06-10 | 2021-12-10 | 广州汽车集团股份有限公司 | Ten-speed dual-clutch transmission and vehicle |
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| CN203548732U (en) * | 2013-08-19 | 2014-04-16 | 吉孚动力技术(中国)有限公司 | Double-clutch gearbox with short idler shaft and dual gears |
| CN203627689U (en) * | 2013-12-10 | 2014-06-04 | 中国重汽集团济南动力有限公司 | Twelve-shift helical teeth speed changer for heavy-duty truck |
| 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 |
| CN204025555U (en) * | 2014-08-29 | 2014-12-17 | 广州汽车集团股份有限公司 | Ten fast double-clutch automatic gearboxes |
| CN105370821A (en) * | 2014-08-29 | 2016-03-02 | 广州汽车集团股份有限公司 | Ten-gear dual clutch automatic transmission |
| CN104989798A (en) * | 2015-07-02 | 2015-10-21 | 北京理工大学 | Ten-speed double-clutch gearbox |
| CN206439351U (en) * | 2016-12-30 | 2017-08-25 | 中国第一汽车股份有限公司 | A kind of ten new gear double-clutch automatic transmissions |
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