CN210003756U - Nine-gear transmission - Google Patents
Nine-gear transmission Download PDFInfo
- Publication number
- CN210003756U CN210003756U CN201920622088.9U CN201920622088U CN210003756U CN 210003756 U CN210003756 U CN 210003756U CN 201920622088 U CN201920622088 U CN 201920622088U CN 210003756 U CN210003756 U CN 210003756U
- Authority
- CN
- China
- Prior art keywords
- gear
- input shaft
- speed
- output shaft
- synchronizer
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Landscapes
- Structure Of Transmissions (AREA)
Abstract
The utility model relates to a derailleur field provides kind of nine speed transmissions, wherein, nine speed transmissions include clutch, second clutch, input shaft, second input shaft, output shaft, second output shaft, wherein, input shaft can loop through three-gear train, four keep off the gear train, keep off the gear train realize with between the output shaft keeps off drive ratio, the second input shaft can loop through four keep off gear train, three keep off gear train, seven keep off the gear train realize with nine keep off drive ratio between the second output shaft, nine speed transmissions, keep off and nine keep off drive ratio realize through two three combinations that keep off in to eight fender gear trains, have reduced the quantity of gear train to allow the derailleur to have less axial length, reduce occupation space, the structural design of being convenient for.
Description
Technical Field
The utility model relates to a technical field of derailleur, in particular to kind of nine keep off derailleurs.
Background
Dual Clutch Transmissions (DCTs) have the advantages of relatively smooth shifting, essentially no power interruption, etc., and have been used in vehicles at .
The conventional dual clutch transmissions, such as seven-speed transmissions, require gear sets (e.g., gear sets, synchronizers, etc.) corresponding to each gear due to excessive gears, resulting in an increased number of gear sets on the input and output shafts of the transmission, which are axially aligned on the input shaft, resulting in a corresponding increase in axial length, which makes it difficult to meet the size requirements of the transmission.
SUMMERY OF THE UTILITY MODEL
In view of this, the utility model aims at providing kind of nine keep off derailleurs to solve the too big, the big problem of occupation space of derailleur axial length.
In order to achieve the above purpose, the technical scheme of the utility model is realized like this:
A nine-gear speed changer, wherein the nine-gear speed changer comprises a clutch, a second clutch, a input shaft in transmission connection with the clutch output end, a second input shaft in transmission connection with the second clutch output end, a output shaft and a second output shaft, the input shaft and the second input shaft are coaxially arranged,
the nine-gear transmission comprises a five-gear set which can be in transmission connection with an th input shaft and a th output shaft, a three-gear set and a seven-gear set which can be in transmission connection with a th input shaft and a second output shaft respectively, a two-gear set and a six-gear set which can be in transmission connection with a second input shaft and a th output shaft respectively, a four-gear set and an eight-gear set which can be in transmission connection with a second input shaft and a second output shaft respectively, and a reverse gear which is arranged on the th output shaft and can be in transmission connection with the three-gear set,
the th input shaft can sequentially pass through the three-gear set, the four-gear set and the two-gear set to realize -gear transmission ratio between the second input shaft and the th output shaft, and the second input shaft can sequentially pass through the four-gear set, the three-gear set and the seven-gear set to realize nine-gear transmission ratio between the second input shaft and the second output shaft.
, the second input shaft is a hollow shaft, and the input shaft is disposed through the second input shaft.
, the clutch and the second clutch are collectively formed as a double-sided clutch.
, the two-gear set includes a two-gear driving gear coaxially connected to the second input shaft and a two-gear driven gear coaxially sleeved to the output shaft, the three-gear set includes a three-gear driving gear coaxially connected to the input shaft and a three-gear driven gear coaxially sleeved to the second output shaft, the four-gear set includes a four-gear driving gear coaxially connected to the second input shaft and a four-gear driven gear coaxially sleeved to the second output shaft, the five-gear set includes a five-gear driving gear coaxially connected to the input shaft and a five-gear driven gear coaxially sleeved to the output shaft, the six-gear set includes a six-gear driving gear coaxially connected to the second input shaft and a six-gear driven gear coaxially sleeved to the output shaft, the seven-gear set includes a seven-gear driving gear coaxially connected to the input shaft and a seven-gear driven gear coaxially sleeved to the second output shaft, the eight-gear set includes an eight-gear driving gear coaxially connected to the second input shaft and a eight-gear driven gear connected to the eight-gear driven gear, and the three-gear driven gear is coaxially connected to the third output shaft.
, the fifth gear driving gear and the seventh gear driving gear are the same gear, and the sixth gear driving gear and the eighth gear driving gear are the same gear.
, a fifth-gear synchronizer which can be in transmission connection with the fifth-gear driven gear, a reverse-gear synchronizer which can be in transmission connection with the reverse-gear, a second-gear synchronizer which can be in transmission connection with the second-gear driven gear and a sixth-gear synchronizer which can be in transmission connection with the sixth-gear driven gear are arranged on the output shaft.
, a seventh-gear synchronizer drivingly connectable to the seventh-gear driven gear, a third-gear synchronizer drivingly connectable to the third-gear driven gear, a fourth-gear synchronizer drivingly connectable to the fourth-gear driven gear, an eighth-gear synchronizer drivingly connectable to the eighth-gear driven gear, and a transition synchronizer synchronously connecting the third-gear driven gear and the fourth-gear driven gear are provided on the second output shaft.
, the fifth gear synchronizer and the reverse gear synchronizer together form a th bilateral synchronizer, the second gear synchronizer and the sixth gear synchronizer together form a second bilateral synchronizer, the third gear synchronizer and the seventh gear synchronizer together form a third bilateral synchronizer, and the fourth gear synchronizer and the eighth gear synchronizer together form a fourth bilateral synchronizer.
And , the fifth-gear driving gear, the third-gear driving gear, the second-gear driving gear, the fourth-gear driving gear and the sixth-gear driving gear are sequentially arranged along the axial direction.
, the nine speed transmission includes a th output gear coaxially connected to the th output shaft, a second output gear coaxially connected to the second output shaft, a differential output shaft, and a differential ring gear coaxially connected to the differential output shaft, the th output gear and the second output gear being in driving engagement with the differential ring gear, respectively.
Compared with the prior art, nine keep off derailleur have following advantage:
nine keep off derailleur, keep off and nine keep off the drive ratio and realize through keeping off two three combinations to eight fender gear sets in, reduced the quantity of gear train to allow the derailleur to have less axial length, reduce occupation space, the structural design of being convenient for.
Other features and advantages of the present invention will be described in detail in the detailed description which follows.
Drawings
The accompanying drawings, which form part of the present invention, are provided to provide an understanding of the present invention with respect to step , the exemplary embodiments of the present invention and their description are intended to explain the present invention without forming an undue limitation on the invention.
Fig. 1 is a schematic diagram of a nine-speed transmission according to an embodiment of the present invention.
Description of reference numerals:
1-fifth gear driving gear, 2-third gear driving gear, 3-fifth gear driven gear, 4- double-sided synchronizer, 5-reverse gear, 6-second gear driven gear, 7-second gear driving gear, 8-second double-sided synchronizer, 9-sixth gear driven gear, 10-sixth gear driving gear, 11- output gear, 12- output shaft, 13-second clutch, 14- clutch, 15-second input shaft, 16- input shaft, 18-second output shaft, 19-differential ring gear, 20-differential output shaft, 21-fourth double-sided synchronizer, 22-fourth gear driving gear, 23-fourth gear driven gear, 24-transition synchronizer, 25-third gear driven gear, 26-third double-sided synchronizer, 27-seventh gear driven gear, 28-eighth gear driven gear, a-seventh gear synchronizer, B-third gear synchronizer, C-fourth gear synchronizer, D-eighth gear synchronizer, E-fifth gear synchronizer, F-sixth gear synchronizer, H-second gear synchronizer, and fourth gear synchronizer.
Detailed Description
In the present invention, the embodiments and the features of the embodiments may be combined with each other without conflict.
The present invention will be described in detail with reference to the accompanying drawings in conjunction with embodiments.
The utility model provides an kind of nine speed transmissions, wherein, nine speed transmissions include clutch 14, second clutch 13, transmission connect in the input shaft 16 of clutch 14 output, transmission connect in the second input shaft 15 of second clutch 13 output, output shaft 12, second output shaft 18, input shaft 16 with second input shaft 15 sets up coaxially,
the nine-gear transmission comprises a five-gear set which can be in transmission connection with the input shaft 16 and the output shaft 12, a three-gear set and a seven-gear set which can be in transmission connection with the input shaft 16 and the output shaft 18 respectively, a two-gear set and a six-gear set which can be in transmission connection with the second input shaft 15 and the output shaft 12 respectively, a four-gear set and an eight-gear set which can be in transmission connection with the second input shaft 15 and the second output shaft 18 respectively, and a reverse gear 5 which is arranged on the output shaft 12 and can be in transmission connection with the three-gear set,
the th input shaft 16 can sequentially pass through the three-gear set, the four-gear set and the two-gear set to realize a -gear transmission ratio with the th output shaft 12, and the second input shaft 15 can sequentially pass through the four-gear set, the three-gear set and the seven-gear set to realize a nine-gear transmission ratio with the second output shaft 18.
the output shaft 12 and the output shaft 18 may be parallel to the th input shaft 16 or the second input shaft 15, respectively, wherein the th input shaft 16 may realize a fifth gear transmission ratio with the th output shaft 12 through a fifth gear set, the th input shaft 16 may realize a seventh gear transmission ratio with the second output shaft 18 through a seventh gear set, the th input shaft 16 may realize a third gear transmission ratio with the second output shaft 18 through a third gear set, the second input shaft 15 may realize a second gear transmission ratio with the th output shaft 12 through a second gear set, the second input shaft 15 may realize a sixth gear transmission ratio with the th output shaft 12 through a sixth gear set, the second input shaft 15 may realize a fourth gear transmission ratio with the second output shaft 18 through a fourth gear set, the second input shaft 15 may realize an eighth gear transmission ratio with the second output shaft 18 through an eighth gear set, and the th input shaft 16 may realize a reverse gear transmission ratio with the th output shaft 12 through a third gear set and the reverse gear 5.
Particularly, the input shaft 16 can sequentially pass through the three-gear set, the four-gear set and the two-gear set to realize a -gear transmission ratio with the output shaft 12, and the second input shaft 15 can sequentially pass through the four-gear set, the three-gear set and the seven-gear set to realize a nine-gear transmission ratio with the second output shaft 18, that is, the -gear transmission ratio and the nine-gear transmission ratio are realized through three of the two-gear-eight-gear set, and no corresponding gear set is additionally arranged, so that the number of gears is reduced, the size of the transmission in the axial direction of the input shaft is reduced, and the space structure design is facilitated.
In this transmission, the transmission of the second to eighth gears is realized only by gear sets, i.e., a second gear set, a third gear set, a fourth gear set, a fifth gear set, a sixth gear set, a seventh gear set, and an eighth gear set, for example, these gear sets may generally include two gears coaxially disposed with a driving shaft and a driven shaft, respectively, so as to realize a parallel shaft transmission, and gear transmission ratio and nine gear transmission ratio are transmitted by means of the above gear sets, and since the rotation direction of the shaft is changed when each gear set is transmitted, gear transmission ratio and nine gear transmission ratio are transmitted by three gear sets, respectively, so as to ensure the same direction as the torque finally output from the second to eighth gear transmission ratio, and the reverse gear transmission ratio is realized by two gear sets, i.e., a gear set formed by a driven gear and a reverse gear from the third gear set and the third gear set, so that the output torque is opposite to the torque from to nine gear.
Alternatively, the second input shaft 15 is a hollow shaft and the th input shaft 16 is disposed through the second input shaft 15, as shown in FIG. 1, the second input shaft 5 is coaxially sleeved over the th input shaft 20, reducing the axial length space occupied by the input shaft as a whole, thereby allowing the transmission to have a smaller axial dimension.
, the clutch 14 and the clutch 13 are both formed as double-side clutches, wherein the clutch 14 and the clutch 13 have the same input end, and the double-side clutch can be selected to output the torque of the clutch 14 or the clutch 13, i.e. the input shaft 16 or the second input shaft 15, and the input shaft 16 and the second input shaft 15 can not output the torque at the same time, i.e. the input shaft 16 and the second input shaft 15 can not be connected with the corresponding clutches at the same time.
Specifically, the second gear set includes a second gear driving gear 7 coaxially connected to the second input shaft 15 and a second gear driven gear 6 coaxially sleeved on the output shaft 12, the third gear set includes a third gear driving gear 2 coaxially connected to the input shaft 16 and a third gear driven gear 25 coaxially sleeved on the second output shaft 18, the fourth gear set includes a fourth gear driving gear 22 coaxially connected to the second input shaft 15 and a fourth gear driven gear 23 coaxially sleeved on the second output shaft 18, the fifth gear set includes a fifth gear driving gear 1 coaxially connected to the input shaft 16 and a fifth gear driven gear 3 coaxially sleeved on the output shaft 12, the sixth gear set includes a sixth gear driving gear 10 coaxially connected to the second input shaft 15 and a sixth gear driven gear 9 coaxially sleeved on the output shaft 12, the seventh gear set includes a seventh gear driving gear coaxially connected to the input shaft 16 and a seventh gear driven gear 27 coaxially sleeved on the second output shaft 18, and the eighth gear set includes a seventh gear driving gear 28 coaxially connected to the second input shaft 16 and an eighth gear driven gear 25, and the eighth gear set includes a third gear driven gear driving gear driven gear 25 coaxially connected to the second input shaft 15 and an eighth gear driven gear 28.
The th input shaft 16 is provided with a fifth-gear driving gear 1, a third-gear driving gear 2 and a seventh-gear driving gear, correspondingly, a th output shaft is provided with a fifth-gear driven gear 3, a second output shaft 18 is provided with a third-gear driven gear 25 and a seventh-gear driven gear 27 to respectively realize a fifth-gear transmission ratio, a third-gear transmission ratio and a seventh-gear transmission ratio, the second input shaft 15 is provided with a second-gear driving gear 7, a fourth-gear driving gear 22, a sixth-gear driving gear 9 and an eighth-gear driving gear, correspondingly, the th output shaft 12 is provided with a second-gear driven gear 6, the second output shaft 18 is provided with a fourth-gear driven gear 23, the th output shaft 12 is provided with a sixth-gear driven gear 9, and the second output shaft 18 is provided with an eighth-gear driven gear 28 to respectively realize a second-gear, a fourth-gear, a sixth-gear and an eighth-gear transmission ratio.
, the five-gear driving gear 1 and the seven-gear driving gear are the same gears, and the six-gear driving gear 10 and the eight-gear driving gear are the same gears as shown in fig. 1, the same gears are used as driving gears for the five-gear driving gear 1, and similarly, the same gears are used as driving gears for the six-gear driving gear 10, and the two gears on the same input shaft or the same output shaft are combined into the same gears, so that the number of gears on the shaft can be reduced, and the axial size of the transmission can be reduced.
The th output shaft 12 is provided with a fifth-gear synchronizer E drivingly connectable to the fifth-gear driven gear 3, a reverse-gear synchronizer F drivingly connectable to the reverse-gear 5, a second-gear synchronizer G drivingly connectable to the second-gear driven gear 6, and a sixth-gear synchronizer H drivingly connectable to the sixth-gear driven gear 9. as described above, the fifth-gear driven gear 3, the reverse-gear 5, the second-gear driven gear 6, and the sixth-gear driven gear 9 are freely fitted to the th output shaft 12 and are freely rotatable with respect to the th output shaft 12, and the fifth-gear synchronizer E, the reverse-gear synchronizer F, the second-gear synchronizer G, and the sixth-gear synchronizer H are respectively allowed to lock the above-mentioned gear to the th output shaft 12 to achieve synchronous rotation, and further to achieve driving between the th output shaft 12 and other shafts.
Similarly, the second output shaft 18 is provided with a seven-gear synchronizer a capable of being in transmission connection with the seven-gear driven gear 27, a three-gear synchronizer B capable of being in transmission connection with the three-gear driven gear 25, a four-gear synchronizer C capable of being in transmission connection with the four-gear driven gear 23, an eight-gear synchronizer D capable of being in transmission connection with the eight-gear driven gear 28, and a transition synchronizer 24 capable of being in synchronization connection with the three-gear driven gear 25 and the four-gear driven gear 23, the seven-gear driven gear 27, the three-gear driven gear 25, the four-gear driven gear 23 and the eight-gear driven gear 28 are freely sleeved on the second output shaft 18 and can freely rotate relative to the second output shaft 18, and the seven-gear synchronizer a, the three-gear synchronizer B, the four-gear synchronizer C and the eight-gear synchronizer D can respectively lock the above gears to the second output shaft 18 correspondingly to realize synchronous rotation, so as to realize transmission between the second output shaft 18 and other shafts, and the transition synchronizer 24 can realize three-gear driven gear 25 and four-gear driven gear 23, so as to realize a transmission ratio between the three-gear set and a specific transmission path and a specific transmission ratio between the above gear set .
Alternatively, the fifth gear synchronizer and the reverse gear synchronizer may together form a th bilateral synchronizer 4, the second gear synchronizer G and the sixth gear synchronizer H together form a second bilateral synchronizer 8, the third gear synchronizer B and the seventh gear synchronizer a together form a third bilateral synchronizer 26, the fourth gear synchronizer C and the eighth gear synchronizer D together form a fourth bilateral synchronizer 21, two synchronizers form a bilateral synchronizer may share part structures, reducing the number of integral parts, particularly reducing the axial length.
Specifically, the fifth-gear driving gear 1, the third-gear driving gear 2, the second-gear driving gear 7, the fourth-gear driving gear 22 and the sixth-gear driving gear 10 are sequentially arranged in the axial direction, correspondingly, referring to fig. 1, the gears on the th output shaft 12 are also arranged in a corresponding order, the gears on the second output shaft 18 are also arranged in a corresponding order, and the number of the axial gears is 5, that is, the same gears are shared as the driving gears, and -gear and nine-gear transmission ratios are realized by using other gear sets, so that the number of the axial gears in the transmission can be reduced to 5, and the axial size of the transmission is reduced.
In addition, the nine-speed transmission comprises a output gear 11 coaxially connected with the output shaft 12, a second output gear 17 coaxially connected with the second output shaft 18, a differential output shaft 20 and a differential ring gear 19 coaxially connected with the differential output shaft, wherein the output gear 11 and the second output gear 17 are respectively in transmission engagement with the differential ring gear 19, the output shaft 12 and the second output shaft 18 are both in transmission connection with the differential output shaft 20, and finally output torque through the differential output shaft 20 in different transmission ratios.
The drive paths from to nine gears and the reverse gear of the nine speed transmission will be described in detail below.
Gear drive route:
the th clutch 14 → the th input shaft 16 → the three-speed drive gear 2 → the three-speed driven gear 25 → the transitional synchronizer 24 → the four-speed driven gear 23 → the four-speed drive gear 22 → the second input shaft 15 → the two-speed drive gear 7 → the two-speed driven gear 6 → the two-speed synchronizer G → the th output shaft 12 → the th output gear 11 → the differential ring gear 19 → the differential output shaft 20;
a second-gear transmission route:
a third gear transmission route:
the th clutch 14 → the th input shaft 16 → the third gear drive gear 2 → the third gear driven gear 25 → the third gear synchronizer B → the second output shaft 18 → the second output gear 17 → the differential ring gear 19 → the differential output shaft 20;
a fourth gear transmission route:
the second clutch 13 → the second input shaft 15 → the fourth-gear driving gear 22 → the fourth-gear driven gear 23 → the fourth-gear synchronizer C → the second output shaft 18 → the second output gear 17 → the differential ring gear 19 → the differential output shaft 20;
a fifth gear transmission route:
the clutch 14 → the input shaft 16 → the five-speed drive gear 1 → the five-speed driven gear 3 → the five-speed synchronizer E → the output shaft 12 → the output gear 11 → the differential ring gear 19 → the differential output shaft 20;
a six-gear transmission route:
the second clutch 13 → the second input shaft 15 → the sixth drive gear 10 → the sixth driven gear 9 → the sixth synchronizer H → the th output shaft 12 → the th output gear 11 → the differential ring gear 19 → the differential output shaft 20;
a seven-gear transmission route:
the clutch 14 → the input shaft 16 → the five-speed drive gear 1 → the seven-speed driven gear 27 → the seven-speed synchronizer a → the second output shaft 18 → the second output gear 17 → the differential ring gear 19 → the differential output shaft 20;
eight-gear transmission route:
the second clutch 13 → the second input shaft 15 → the sixth-gear drive gear 10 → the eighth-gear driven gear 28 → the eighth-gear synchronizer D → the second output shaft 18 → the second output gear 17 → the differential ring gear 19 → the differential output shaft 20;
a nine-gear transmission route:
the second clutch 13 → the second input shaft 15 → the fourth-gear drive gear 22 → the fourth-gear driven gear 23 → the transitional synchronizer 24 → the third-gear driven gear 25 → the third-gear drive gear 2 → the input shaft 16 → the fifth-gear drive gear 1 → the seventh-gear driven gear 27 → the seventh-gear synchronizer a → the second output shaft 18 → the second output gear 17 → the differential ring gear 19 → the differential output shaft 20;
a reverse gear transmission route:
the th clutch 14 → the th input shaft 16 → the three-speed drive gear 2 → the three-speed driven gear 25 → the reverse gear 5 → the reverse synchronizer F → the th output shaft 12 → the th output gear 11 → the differential ring gear 19 → the differential output shaft 20.
The above description is only a preferred embodiment of the present invention, and should not be taken as limiting the invention, and any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (10)
- A nine-gear transmission is characterized in that the nine-gear transmission comprises a clutch (14), a second clutch (13), a input shaft (16) in transmission connection with the output end of the clutch (14), a second input shaft (15) in transmission connection with the output end of the second clutch (13), a output shaft (12) and a second output shaft (18), wherein the input shaft (16) and the second input shaft (15) are coaxially arranged,the nine-gear transmission comprises a five-gear set which can be in transmission connection with an input shaft (16) and a output shaft (12), a three-gear set and a seven-gear set which can be in transmission connection with a input shaft (16) and a 3518 output shaft respectively, a two-gear set and a six-gear set which can be in transmission connection with a second input shaft (15) and a output shaft (12) respectively, a four-gear set and an eight-gear set which can be in transmission connection with a second input shaft (15) and a second output shaft (18) respectively, and a reverse gear (5) which is arranged on the output shaft (12) and can be in transmission connection with the three-gear set,the input shaft (16) can sequentially pass through the three-gear set, the four-gear set and the two-gear set to realize a -gear transmission ratio between the 8932 input shaft and the output shaft (12), and the second input shaft (15) can sequentially pass through the four-gear set, the three-gear set and the seven-gear set to realize a nine-gear transmission ratio between the second input shaft and the second output shaft (18).
- 2. The nine speed transmission of claim 1, wherein the second input shaft (15) is a hollow shaft, and the input shaft (16) is disposed through the second input shaft (15).
- 3. The nine speed transmission of claim 2, wherein the th clutch (14) and the second clutch (13) are collectively formed as a double-sided clutch.
- 4. A nine speed transmission according to claim 3, wherein said second gear set comprises a second gear driving gear (7) coaxially connected to said second input shaft (15) and a second gear driven gear (6) idly engaged with said second output shaft (12), said third gear set comprises a third gear driving gear (2) coaxially connected to said input shaft (16) and a third gear driven gear (25) idly engaged with said second output shaft (18), said fourth gear set comprises a fourth gear driving gear (22) coaxially connected to said second input shaft (15) and a fourth gear driven gear (23) idly engaged with said second output shaft (18), said fifth gear set comprises a fifth gear driving gear (1) coaxially connected to said input shaft (16) of said fourth gear set and a fifth gear driven gear (3) idly engaged with said output shaft (12) of said fifth , said sixth gear set comprises a sixth gear driving gear (10) coaxially connected to said second input shaft (15) and a sixth gear driving gear (57) coaxially engaged with said sixth gear (57) of said second gear set ), said seventh gear set comprises a seventh gear driving gear (28) and an eighth gear driven gear (28) coaxially connected to said second input shaft (18) and said seventh gear driven gear (28).
- 5. The nine speed transmission of claim 4, wherein the five speed drive gear (1) and the seven speed drive gear are the same gear and the six speed drive gear (10) and the eight speed drive gear are the same gear.
- 6. The nine-speed transmission according to claim 5, wherein the output shaft is provided with a fifth-speed synchronizer (E) drivingly connectable to the fifth-speed driven gear (3), a reverse-speed synchronizer (F) drivingly connectable to the reverse-speed gear, a second-speed synchronizer (G) drivingly connectable to the second-speed driven gear (6), and a sixth-speed synchronizer (H) drivingly connectable to the sixth-speed driven gear (9).
- 7. The nine-speed transmission according to claim 6, wherein the second output shaft (18) is provided with a seven-speed synchronizer (A) which is drivingly connectable to the seven-speed driven gear (27), a three-speed synchronizer (B) which is drivingly connectable to the three-speed driven gear (25), a four-speed synchronizer (C) which is drivingly connectable to the four-speed driven gear (23), an eight-speed synchronizer (D) which is drivingly connectable to the eight-speed driven gear (28), and a transition synchronizer (24) which is synchronously connectable to the three-speed driven gear (25) and the four-speed driven gear (23).
- 8. The nine speed transmission according to claim 7, wherein the fifth and reverse synchronizers together form an th bilateral synchronizer (4), the second and sixth synchronizers (G, H) together form a second bilateral synchronizer (8), the third and seventh synchronizers (B, A) together form a third bilateral synchronizer (26), and the fourth and eighth synchronizers (C, D) together form a fourth bilateral synchronizer (21).
- 9. The nine speed transmission according to claim 5, wherein the five speed drive gear (1), the three speed drive gear (2), the two speed drive gear (7), the four speed drive gear (22), and the six speed drive gear (10) are arranged in order in an axial direction.
- 10. The nine speed transmission of claim 1, comprising a output gear (11) coaxially connected to the output shaft (12), a second output gear (17) coaxially connected to the second output shaft (18), a differential output shaft (20), and a differential ring gear (19) coaxially connected to the differential output shaft, the output gear (11) and the second output gear (17) being in driving engagement with the differential ring gear (19), respectively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920622088.9U CN210003756U (en) | 2019-04-30 | 2019-04-30 | Nine-gear transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920622088.9U CN210003756U (en) | 2019-04-30 | 2019-04-30 | Nine-gear transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN210003756U true CN210003756U (en) | 2020-01-31 |
Family
ID=69305761
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201920622088.9U Active CN210003756U (en) | 2019-04-30 | 2019-04-30 | Nine-gear transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN210003756U (en) |
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113492667A (en) * | 2020-03-20 | 2021-10-12 | 广州汽车集团股份有限公司 | Hybrid power driving system and vehicle |
| CN113685510A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113682126A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Hybrid power driving system and vehicle |
| CN113685497A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Ten keep off two separation and reunion derailleurs and vehicle |
| CN113685503A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Ten keep off two separation and reunion derailleurs and vehicle |
| CN113685499A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113685509A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113864407A (en) * | 2020-06-30 | 2021-12-31 | 比亚迪股份有限公司 | Transmission, power system and vehicle |
| CN114294383A (en) * | 2021-12-31 | 2022-04-08 | 中国第一汽车股份有限公司 | Double-clutch transmission |
| CN114321294A (en) * | 2021-12-31 | 2022-04-12 | 中国第一汽车股份有限公司 | Multi-gear double-clutch transmission |
| CN114763824A (en) * | 2021-01-12 | 2022-07-19 | 广州汽车集团股份有限公司 | Nine-speed double-clutch automatic transmission and vehicle |
| 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 |
| CN115126831A (en) * | 2022-05-19 | 2022-09-30 | 中国第一汽车股份有限公司 | Multi-gear double-clutch transmission, transmission method and automobile |
| CN114763824B (en) * | 2021-01-12 | 2024-06-07 | 广州汽车集团股份有限公司 | Nine-speed double-clutch automatic transmission and vehicle |
-
2019
- 2019-04-30 CN CN201920622088.9U patent/CN210003756U/en active Active
Cited By (22)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113492667A (en) * | 2020-03-20 | 2021-10-12 | 广州汽车集团股份有限公司 | Hybrid power driving system and vehicle |
| CN113492667B (en) * | 2020-03-20 | 2024-04-12 | 广州汽车集团股份有限公司 | Hybrid power driving system and vehicle |
| CN113685497B (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 |
| CN113685510B (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 |
| CN113685503A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Ten keep off two separation and reunion derailleurs and vehicle |
| CN113685499A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113685509A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113685497A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Ten keep off two separation and reunion derailleurs and vehicle |
| CN113685510A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113682126B (en) * | 2020-05-18 | 2024-04-12 | 广州汽车集团股份有限公司 | Hybrid power driving system and vehicle |
| CN113685509B (en) * | 2020-05-18 | 2024-03-29 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113685503B (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 |
| CN113685499B (en) * | 2020-05-18 | 2024-03-22 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113682126A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Hybrid power driving system and vehicle |
| CN113864407A (en) * | 2020-06-30 | 2021-12-31 | 比亚迪股份有限公司 | Transmission, power system and vehicle |
| CN114763824A (en) * | 2021-01-12 | 2022-07-19 | 广州汽车集团股份有限公司 | Nine-speed double-clutch automatic transmission and vehicle |
| CN114763824B (en) * | 2021-01-12 | 2024-06-07 | 广州汽车集团股份有限公司 | Nine-speed double-clutch automatic transmission and vehicle |
| WO2023124765A1 (en) * | 2021-12-31 | 2023-07-06 | 中国第一汽车股份有限公司 | Dual clutch transmission |
| CN114321294A (en) * | 2021-12-31 | 2022-04-12 | 中国第一汽车股份有限公司 | Multi-gear double-clutch transmission |
| CN114294383A (en) * | 2021-12-31 | 2022-04-08 | 中国第一汽车股份有限公司 | Double-clutch transmission |
| CN115126831A (en) * | 2022-05-19 | 2022-09-30 | 中国第一汽车股份有限公司 | Multi-gear double-clutch transmission, transmission method and automobile |
| 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 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN210003756U (en) | Nine-gear transmission | |
| CN110985613B (en) | Multi-gear double-clutch transmission | |
| US8056429B2 (en) | Multi-speed dual clutch transmission with countershaft gearing arrangement | |
| US7353724B2 (en) | Multi-speed transmission with Hi-Lo output torque-transmitting mechanisms and gear sets | |
| US9022891B2 (en) | Triple clutch multi-speed transmission | |
| KR101679967B1 (en) | Multi-speed transmission | |
| US8747274B2 (en) | Triple clutch multi-speed transmission | |
| US20150040705A1 (en) | Triple input clutch transmission | |
| CN210003758U (en) | Seven-gear transmission | |
| KR101063654B1 (en) | Powertrain of Double Clutch Transmission | |
| CN111623092B (en) | Double-clutch transmission and vehicle | |
| KR20200043571A (en) | Dual clutch transmission for vehicle | |
| CN214578738U (en) | Eight-gear double-clutch transmission | |
| JP4877196B2 (en) | transmission | |
| US10018251B2 (en) | Multi-speed dual clutch transmission | |
| CN110578773A (en) | eight-gear transmission | |
| CN113883238B (en) | Transmission and vehicle | |
| CN112065935B (en) | Multi-gear double-clutch transmission | |
| JP2008291893A (en) | Dual clutch type transmission | |
| CN112343980B (en) | Ten-speed double-clutch type automatic transmission and vehicle | |
| KR101063616B1 (en) | Double Clutch Transmission Powertrain | |
| CN210135210U (en) | Transmission and vehicle | |
| US10309489B2 (en) | Multi-speed dual clutch transmission | |
| CN218031281U (en) | Multi-gear transmission and vehicle | |
| CN214578647U (en) | Dual clutch transmission |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |