CN214578738U - Eight-gear double-clutch transmission - Google Patents
Eight-gear double-clutch transmission Download PDFInfo
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- CN214578738U CN214578738U CN202120559836.0U CN202120559836U CN214578738U CN 214578738 U CN214578738 U CN 214578738U CN 202120559836 U CN202120559836 U CN 202120559836U CN 214578738 U CN214578738 U CN 214578738U
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Abstract
The utility model discloses an eight keep off two separation and reunion derailleurs, it belongs to derailleur technical field, include: a first clutch; the first input shaft is coaxially and fixedly provided with a three-gear driving gear and a seven-gear driving gear; a second clutch; the second input shaft is coaxially and fixedly provided with a second-gear driving gear and a fourth-gear driving gear; the first output shaft is provided with a second-gear driven gear, a sixth-gear driven gear, a fifth-gear driven gear and a seventh-gear driven gear which are sleeved; the second output shaft is provided with an idle reverse gear driven gear, a fourth gear driven gear and a third gear driven gear; the second output shaft is also provided with a third-fourth gear transition synchronizing device, and the third-fourth gear transition synchronizing device is used for controlling the separation and the engagement of the fourth-gear driven gear and the third-gear driven gear; the two-gear driven gear can be meshed with the two-gear driving gear and the reverse gear driven gear to form reverse gear transmission. The utility model discloses make eight keep off two separation and reunion derailleur control systems simple.
Description
Technical Field
The utility model relates to a derailleur technical field especially relates to an eight keep off two separation and reunion derailleurs.
Background
The dual clutch transmission is increasingly popular in the market based on the characteristics of fast gear shifting, uninterrupted power, low oil consumption and excellent comfort. The traditional transverse double-clutch automatic transmission mostly adopts a three-shaft structure, namely, an integrated double clutch is respectively connected with a nested double input shaft, and the two input shafts transmit power to two output shafts through gear gears. Because of the restriction of the arrangement space of the whole vehicle, generally 6-7 gears are arranged.
With the gradual increase of the market demands for the dynamic performance and the economic performance of the whole vehicle, the arrangement of more gears in a limited space becomes a new research direction. In the prior art, a pair of gear sets and synchronizers are added on an input shaft and an output shaft, so that one gear is added; or multiple groups of gear gears are reused, and a synchronizer is added to increase gears.
The gears are increased by adopting the structure, and hydraulic or electric control elements and the like are often required to be added to drive the added synchronizers while the gears are increased, so that the control system is more complex and the cost is increased.
SUMMERY OF THE UTILITY MODEL
An object of the utility model is to provide an eight keep off two separation and reunion derailleurs to solve the derailleur that exists among the prior art and still need increase control element and lead to more complicated, the technical problem of cost-push of control system when increasing the fender position.
As the conception, the utility model adopts the technical proposal that:
an eight speed dual clutch transmission comprising:
a first clutch;
the first input shaft is in transmission connection with the output end of the first clutch, and a three-gear driving gear and a seven-gear driving gear are coaxially and fixedly arranged on the first input shaft;
a second clutch disposed coaxially with the first clutch;
the second input shaft is in transmission connection with the output end of the second clutch and is coaxially nested with the first input shaft, and a second-gear driving gear and a fourth-gear driving gear are coaxially and fixedly arranged on the second input shaft;
the first output shaft is provided with a second-gear driven gear, a sixth-gear driven gear, a fifth-gear driven gear and a seventh-gear driven gear which are sleeved in an empty way, the second-gear driven gear can be in meshing transmission with the second-gear driving gear, the sixth-gear driven gear can be in meshing transmission with the fourth-gear driving gear, the fifth-gear driven gear can be in meshing transmission with the third-gear driving gear, and the seventh-gear driven gear can be in meshing transmission with the seventh-gear driving gear;
the second output shaft is provided with a reverse gear driven gear, a fourth gear driven gear and a third gear driven gear which are sleeved in an empty way, the reverse gear driven gear can be in meshing transmission with the second gear driving gear, the fourth gear driven gear can be in meshing transmission with the fourth gear driving gear, and the third gear driven gear can be in meshing transmission with the third gear driving gear;
the second output shaft is also provided with a third-fourth gear transition synchronizing device, and the third-fourth gear transition synchronizing device is used for controlling the separation and the engagement of the fourth-gear driven gear and the third-gear driven gear;
the two-gear driven gear can be meshed with the two-gear driving gear and the reverse gear driven gear to form reverse gear transmission.
Optionally, the eight-gear double-clutch transmission further comprises a differential device, a main speed reduction driven gear is arranged on the differential device, a first output gear is arranged on the first output shaft, and the first output gear can be in meshed transmission with the main speed reduction driven gear.
Optionally, the eight-gear double-clutch transmission further comprises a differential device, a main speed reduction driven gear is arranged on the differential device, a second output gear is arranged on the second output shaft, and the second output gear can be in meshed transmission with the main speed reduction driven gear.
Optionally, a second-sixth gear synchronizer is coaxially and fixedly arranged on the first output shaft, and the second-sixth gear synchronizer is used for controlling the connection states of the second-gear driven gear and the sixth-gear driven gear with the first output shaft.
Optionally, a fifth-seventh gear synchronizer is coaxially and fixedly arranged on the first output shaft, and the fifth-seventh gear synchronizer is used for controlling the connection states of the fifth-gear driven gear and the seventh-gear driven gear with the first output shaft.
Optionally, the fifth-seventh gear synchronizing device comprises a fifth gear synchronizer and a seventh gear synchronizer, the fifth gear synchronizer is used for controlling the connection state of the fifth gear driven gear and the first output shaft, and the seventh gear synchronizer is used for controlling the connection state of the seventh gear driven gear and the first output shaft.
Optionally, a fourth reverse gear synchronizer is coaxially and fixedly arranged on the second output shaft, and the fourth reverse gear synchronizer is used for controlling the connection states of the reverse gear driven gear and the fourth gear driven gear with the second output shaft.
Optionally, the fourth reverse gear synchronizing device includes a fourth gear synchronizer and a reverse gear synchronizer, the fourth gear synchronizer is configured to control a connection state of the fourth gear driven gear and the second output shaft, and the reverse gear synchronizer is configured to control a connection state of the reverse gear driven gear and the second output shaft.
Optionally, a third-gear synchronizer is coaxially and fixedly arranged on the second output shaft and used for controlling the connection state of the third-gear driven gear and the second output shaft.
Optionally, the third gear synchronizer is a synchronizer.
When the eight-gear double-clutch transmission provided by the utility model works, the two-gear driving gear and the two-gear driven gear are meshed to form two-gear transmission; the three-gear driving gear is meshed with the three-gear driven gear to form three-gear transmission; the four-gear driving gear is meshed with the four-gear driven gear to form four-gear transmission; the three-gear driving gear is meshed with the five-gear driven gear to form five-gear transmission; the four-gear driving gear is meshed with the six-gear driven gear to form six-gear transmission; the seven-gear driving gear is meshed with the seven-gear driven gear to form seven-gear transmission.
The three-gear and four-gear transition synchronizing device controls the four-gear driven gear and the three-gear driven gear to be connected, so that the four-gear driven gear and the three-gear driven gear form a duplicate gear, and the three-gear set, the four-gear set and the two-gear set are sequentially matched for transmission to form first-gear transmission.
The three-gear and four-gear transition synchronizing device controls the four-gear driven gear and the three-gear driven gear to be connected, so that the four-gear driven gear and the three-gear driven gear form a duplicate gear, and the four-gear set, the three-gear set and the seven-gear set are sequentially matched for transmission to form eight-gear transmission.
Two keep off driven gear on the first output shaft simultaneously with keep off driving gear and reverse gear driven gear meshing, form the transmission of reversing gear.
Compared with a common seven-gear transmission, the seven-gear transmission reduces a pair of gear gears and saves the arrangement space; meanwhile, the original control element for controlling the connection or the separation of the third-gear driven gear and the second output shaft on the transmission is used for controlling the third-gear and the fourth-gear transition synchronizing device, and no control element is required to be added, so that the system is simple in structure and low in cost.
Drawings
Fig. 1 is a schematic structural diagram of an eight-gear dual clutch transmission provided in an embodiment of the present invention.
In the figure:
10. a first clutch; 20. a first input shaft; 30. a second clutch; 40. a second input shaft; 50. a first output shaft; 501. a first output gear; 60. a second output shaft; 601. a second output gear;
21. a second gear driving gear; 22. a second driven gear;
31. a third gear drive gear; 32. a third-gear driven gear;
41. a fourth gear drive gear; 42. a fourth-gear driven gear;
52. a fifth-gear driven gear;
62. a six-gear driven gear;
71. a seven-gear driving gear; 72. a seven-speed driven gear;
92. a reverse driven gear;
100. a differential device; 301. a second-gear and a sixth-gear synchronizer; 302. a fifth gear and a seventh gear synchronizer; 303. a fourth reverse gear synchronizer; 304. a third gear synchronizer; 305. three-fourth gear transition synchronizer.
Detailed Description
In order to make the technical problem solved by the present invention, the technical solution adopted by the present invention and the technical effect achieved by the present invention clearer, the technical solution of the present invention will be further explained by combining the drawings and by means of the specific implementation manner. It is to be understood that the specific embodiments described herein are merely illustrative of the invention and are not limiting of the invention. It should be further noted that, for the convenience of description, only some but not all of the elements related to the present invention are shown in the drawings.
In the description of the present invention, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplification of description, but do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance. Wherein the terms "first position" and "second position" are two different positions.
In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection or a removable connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood in specific cases to those skilled in the art.
Referring to fig. 1, the present embodiment provides an eight speed dual clutch transmission including a first clutch 10, a first input shaft 20, a second clutch 30, a second input shaft 40, a first output shaft 50 and a second output shaft 60.
The first input shaft 20 is in transmission connection with the output end of the first clutch 10, and the first input shaft 20 is coaxially and fixedly provided with a third-gear driving gear 31 and a seventh-gear driving gear 71; the second clutch 30 is disposed coaxially with the first clutch 10; the second input shaft 40 is in transmission connection with the output end of the second clutch 30 and is coaxially nested with the first input shaft 20, and a second-gear driving gear 21 and a fourth-gear driving gear 41 are coaxially and fixedly arranged on the second input shaft 40; the first output shaft 50 is provided with a second-gear driven gear 22, a sixth-gear driven gear 62, a fifth-gear driven gear 52 and a seventh-gear driven gear 72 which are sleeved in an empty way, the second-gear driven gear 22 can be in meshed transmission with the second-gear driving gear 21, the sixth-gear driven gear 62 can be in meshed transmission with the fourth-gear driving gear 41, the fifth-gear driven gear 52 can be in meshed transmission with the third-gear driving gear 31, and the seventh-gear driven gear 72 can be in meshed transmission with the seventh-gear driving gear 71; the second output shaft 60 is provided with an empty reverse gear driven gear 92, a fourth gear driven gear 42 and a third gear driven gear 32, the reverse gear driven gear 92 can be in meshing transmission with the second gear driving gear 21, the fourth gear driven gear 42 can be in meshing transmission with the fourth gear driving gear 41, and the third gear driven gear 32 can be in meshing transmission with the third gear driving gear 31.
Further, a third-fourth gear transition synchronizing device 305 is arranged on the second output shaft 60, and the third-fourth gear transition synchronizing device 305 is used for controlling the separation and the engagement of the fourth-gear driven gear 42 and the third-gear driven gear 32; the second-gear driven gear 22 can be meshed with the second-gear driving gear 21 and the reverse driven gear 92 simultaneously to form reverse transmission.
When the eight-gear double-clutch transmission provided by the embodiment works, the second-gear driving gear 21 and the second-gear driven gear 22 are meshed to form second-gear transmission; the three-gear driving gear 31 is meshed with the three-gear driven gear 32 to form three-gear transmission; the four-gear driving gear 41 is meshed with the four-gear driven gear 42 to form four-gear transmission; the third-gear driving gear 31 is meshed with the fifth-gear driven gear 52 to form fifth-gear transmission; the four-gear driving gear 41 is meshed with the six-gear driven gear 62 to form six-gear transmission; the seven-gear driving gear 71 is meshed with the seven-gear driven gear 72 to form seven-gear transmission.
Three keep off gear train, four keep off gear train and two keep off the gear train and cooperate in proper order and form a fender transmission, specifically do: the third-fourth gear transition synchronizing device 305 controls the fourth-gear driven gear 42 and the third-gear driven gear 32 to be connected, so that the fourth-gear driven gear 42 and the third-gear driven gear 32 form a duplicate gear, the third-gear driving gear 31 on the first input shaft 20 is in meshing transmission with the third-gear driven gear 32, the third-gear driven gear 32 drives the fourth-gear driven gear 42 to rotate, the fourth-gear driven gear 42 is in meshing transmission with the fourth-gear driving gear 41 on the second input shaft 40 so as to drive the second input shaft 40 to rotate, the second input shaft 40 drives the second-gear driving gear 21 to rotate, the second-gear driving gear 21 is in meshing engagement with the second-gear driven gear 22, and finally, first-gear transmission is formed.
Four keep off gear train, three keep off gear train and seven keep off gear train and cooperate in proper order and form eight and keep off the transmission, specifically do: the third-fourth gear transition synchronizing device 305 controls the fourth-gear driven gear 42 and the third-gear driven gear 32 to be connected, so that the fourth-gear driven gear 42 and the third-gear driven gear 32 form a duplicate gear, the fourth-gear driving gear 41 on the second input shaft 40 is in meshing transmission with the fourth-gear driven gear 42, the fourth-gear driven gear 42 drives the third-gear driven gear 32 to be in meshing transmission, the third-gear driven gear 32 is in meshing transmission with the third-gear driving gear 31 to further drive the first input shaft 20 to rotate, the first input shaft 20 drives the seventh-gear driving gear 71 to rotate, the seventh-gear driving gear 71 is meshed with the seventh-gear driven gear 72, and finally eight-gear transmission is formed.
The second-gear driven gear 22 on the first output shaft 50 is simultaneously meshed with the second-gear driving gear 21 and the reverse gear driven gear 92 to form reverse gear transmission.
Specifically, the third-fourth gear transition synchronizer 305 is a transition synchronizer.
According to the eight-gear double-clutch transmission provided by the embodiment, the three-fourth-gear transition synchronizing device 305 is arranged, and when the three-fourth-gear transition synchronizing device 305 controls the four-gear driven gear 42 and the three-gear driven gear 32 to be engaged, the four-gear driven gear 42 and the three-gear driven gear 32 form a duplicate gear, so that power is transmitted between the three-gear set and the four-gear set, and when the power is combined with the two-gear set, first-gear transmission can be formed; the transmission device can form eight-gear transmission when being matched with a seven-gear set, and compared with a common seven-gear transmission, the transmission device reduces a pair of gear gears (a first-gear driving gear and a first-gear driven gear) and saves arrangement space; meanwhile, the original control element for controlling the engagement or disengagement of the third-gear driven gear 32 and the second output shaft 60 is used for controlling the third-fourth-gear transition synchronizing device 305, and no control element is required to be added, so that the system is simple in structure and low in cost.
Further, the eight-gear double-clutch transmission further comprises a differential device 100, wherein a main speed reduction driven gear is arranged on the differential device 100, a first output gear 501 is arranged on the first output shaft 50, and the first output gear 501 can be meshed with the main speed reduction driven gear to form a main speed reduction ratio. The second output shaft 60 is provided with a second output gear 601, and the second output gear 601 can be meshed with a main reduction driven gear to form a main reduction ratio.
Further, a second-sixth gear synchronizer 301 is coaxially and fixedly arranged on the first output shaft 50, and the second-sixth gear synchronizer 301 is used for controlling the connection state of the second-gear driven gear 22 and the sixth-gear driven gear 62 with the first output shaft 50.
Specifically, the second-sixth gear synchronizing device 301 includes a second gear synchronizer and a sixth gear synchronizer, and the second gear synchronizer is used for controlling the connection state of the second gear driven gear 22 and the first output shaft 50; the sixth-speed synchronizer is used to control the connection state of the sixth-speed driven gear 62 and the first output shaft 50.
Further, a fifth-seventh gear synchronizer 302 is coaxially and fixedly arranged on the first output shaft 50, and the fifth-seventh gear synchronizer 302 is used for controlling the connection state of the fifth-gear driven gear 52 and the seventh-gear driven gear 72 with the first output shaft 50.
Specifically, the fifth-seventh speed synchronizing device 302 includes a fifth-speed synchronizer for controlling a connection state of the fifth-speed driven gear 52 with the first output shaft 50 and a seventh-speed synchronizer; the seven-speed synchronizer is used to control the connection state of the seven-speed driven gear 72 and the first output shaft 50.
Further, a four-reverse synchronizing device 303 is coaxially and fixedly arranged on the second output shaft 60, and the four-reverse synchronizing device 303 is used for controlling the connection state of the reverse driven gear 92 and the four-gear driven gear 42 with the second output shaft 60.
Specifically, the four reverse synchronization device 303 includes a four-gear synchronizer for controlling a connection state of the fourth-gear driven gear 42 with the second output shaft 60 and a reverse synchronizer; the reverse synchronizer is used to control the connection state of the reverse driven gear 92 with the second output shaft 60.
Further, a third-gear synchronizer 304 is coaxially and fixedly arranged on the second output shaft 60, the third-gear synchronizer 304 is a one-side synchronizer, and the third-gear synchronizer 304 is used for controlling the connection state of the third-gear driven gear 32 and the second output shaft 60.
Specifically, the three-gear synchronizer 304 and the three-fourth-gear transitional synchronizer 305 are simultaneously controlled using the original control element that controls the engagement or disengagement of the third-gear driven gear 32 with or from the second output shaft 60.
Specifically, the third gear synchronizer 304 is a synchronizer.
The above embodiments have been described only the basic principles and features of the present invention, and the present invention is not limited by the above embodiments, and is not departing from the spirit and scope of the present invention. The scope of the invention is defined by the appended claims and equivalents thereof.
Claims (10)
1. An eight speed dual clutch transmission comprising:
a first clutch (10);
the first input shaft (20) is in transmission connection with the output end of the first clutch (10), and a third-gear driving gear (31) and a seventh-gear driving gear (71) are coaxially and fixedly arranged on the first input shaft (20);
a second clutch (30) disposed coaxially with the first clutch (10);
the second input shaft (40) is in transmission connection with the output end of the second clutch (30) and is coaxially nested with the first input shaft (20), and a second-gear driving gear (21) and a fourth-gear driving gear (41) are coaxially and fixedly arranged on the second input shaft (40);
the first output shaft (50) is provided with a second-gear driven gear (22), a sixth-gear driven gear (62), a fifth-gear driven gear (52) and a seventh-gear driven gear (72) which are sleeved in an empty mode, the second-gear driven gear (22) can be in meshing transmission with the second-gear driving gear (21), the sixth-gear driven gear (62) can be in meshing transmission with the fourth-gear driving gear (41), the fifth-gear driven gear (52) can be in meshing transmission with the third-gear driving gear (31), and the seventh-gear driven gear (72) can be in meshing transmission with the seventh-gear driving gear (71);
the second output shaft (60) is provided with a reverse gear driven gear (92), a fourth gear driven gear (42) and a third gear driven gear (32) which are sleeved in an empty way, the reverse gear driven gear (92) can be in meshing transmission with the second gear driving gear (21), the fourth gear driven gear (42) can be in meshing transmission with the fourth gear driving gear (41), and the third gear driven gear (32) can be in meshing transmission with the third gear driving gear (31);
a third-fourth gear transition synchronizing device (305) is further arranged on the second output shaft (60), and the third-fourth gear transition synchronizing device (305) is used for controlling the separation and the engagement of the fourth-gear driven gear (42) and the third-gear driven gear (32);
the two-gear driven gear (22) can be meshed with the two-gear driving gear (21) and the reverse gear driven gear (92) to form reverse gear transmission.
2. The eight speed dual clutch transmission according to claim 1, characterized in that it further comprises a differential device (100), on which differential device (100) a main reduction driven gear is arranged, on which first output shaft (50) a first output gear (501) is arranged, which first output gear (501) is capable of driving in mesh with the main reduction driven gear.
3. The eight speed dual clutch transmission according to claim 1, characterized in that it further comprises a differential device (100), on which differential device (100) a main reduction driven gear is arranged, on which second output shaft (60) a second output gear (601) is arranged, which second output gear (601) is capable of driving in mesh with the main reduction driven gear.
4. The eight-speed double-clutch transmission according to claim 1, characterized in that a second-sixth speed synchronizing device (301) is coaxially fixed to the first output shaft (50), and the second-sixth speed synchronizing device (301) is used for controlling the connection state of the second-speed driven gear (22) and the sixth-speed driven gear (62) with the first output shaft (50).
5. The eight-speed double-clutch transmission according to claim 1, characterized in that a fifth-seventh speed synchronizer (302) is coaxially fixed on the first output shaft (50), and the fifth-seventh speed synchronizer (302) is used for controlling the connection state of the fifth-speed driven gear (52) and the seventh-speed driven gear (72) with the first output shaft (50).
6. The eight-speed double-clutch transmission according to claim 5, characterized in that the five-seven speed synchronizing means (302) comprises a five-speed synchronizer for controlling the connection state of the fifth-speed driven gear (52) and the first output shaft (50) and a seven-speed synchronizer for controlling the connection state of the seventh-speed driven gear (72) and the first output shaft (50).
7. The eight-gear double-clutch transmission according to claim 1, characterized in that a four-reverse synchronization device (303) is coaxially fixed to the second output shaft (60), and the four-reverse synchronization device (303) is used for controlling the connection state of the reverse driven gear (92) and the four-gear driven gear (42) with the second output shaft (60).
8. The eight-speed double clutch transmission according to claim 7, characterized in that the four-reverse synchronization device (303) comprises a four-speed synchronizer for controlling the connection state of the four-speed driven gear (42) with the second output shaft (60) and a reverse synchronizer for controlling the connection state of the reverse driven gear (92) with the second output shaft (60).
9. The eight-speed double clutch transmission according to claim 1, characterized in that a three-speed synchronizer (304) is coaxially fixed to the second output shaft (60), and the three-speed synchronizer (304) is used for controlling the connection state of the three-speed driven gear (32) and the second output shaft (60).
10. The eight speed dual clutch transmission according to claim 9, wherein the three speed synchronizer (304) is a synchronizer.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202120559836.0U CN214578738U (en) | 2021-03-18 | 2021-03-18 | Eight-gear double-clutch transmission |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202120559836.0U CN214578738U (en) | 2021-03-18 | 2021-03-18 | Eight-gear double-clutch transmission |
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| CN214578738U true CN214578738U (en) | 2021-11-02 |
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| CN202120559836.0U Active CN214578738U (en) | 2021-03-18 | 2021-03-18 | Eight-gear double-clutch transmission |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114294383A (en) * | 2021-12-31 | 2022-04-08 | 中国第一汽车股份有限公司 | Double-clutch transmission |
| CN115045963A (en) * | 2022-06-13 | 2022-09-13 | 中国第一汽车股份有限公司 | Multi-gear double-clutch transmission |
-
2021
- 2021-03-18 CN CN202120559836.0U patent/CN214578738U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114294383A (en) * | 2021-12-31 | 2022-04-08 | 中国第一汽车股份有限公司 | Double-clutch transmission |
| CN115045963A (en) * | 2022-06-13 | 2022-09-13 | 中国第一汽车股份有限公司 | Multi-gear double-clutch transmission |
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