CN110578773A - eight-gear transmission - Google Patents
eight-gear transmission Download PDFInfo
- Publication number
- CN110578773A CN110578773A CN201810589231.9A CN201810589231A CN110578773A CN 110578773 A CN110578773 A CN 110578773A CN 201810589231 A CN201810589231 A CN 201810589231A CN 110578773 A CN110578773 A CN 110578773A
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- Prior art keywords
- gear
- transmission
- output shaft
- gear set
- synchronizer
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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
- F16H3/20—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear
- F16H3/22—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with gears shiftable only axially
- F16H3/30—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with gears shiftable only axially with driving and driven shafts not coaxial
- F16H3/32—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with gears shiftable only axially with driving and driven shafts not coaxial and an additional shaft
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
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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
- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight 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
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse 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
- F16H2200/2058—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with eleven engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
the invention relates to the technical field of transmissions, and provides an eight-gear transmission, wherein the eight-gear transmission comprises a first clutch, a second clutch, a first input shaft in transmission connection with the output end of the first clutch, a second input shaft in transmission connection with the output end of the second clutch, a first output shaft, a second output shaft, a two-gear set, a three-gear set, a four-gear set, a five-gear set, a six-gear set and a seven-gear set, and the eight-gear transmission can realize the transmission ratio of one gear to eight gears. In the eight-gear transmission provided by the embodiment of the invention, the transmission ratio of the first gear and the eight gears is realized by three gear sets from the second gear to the seventh gear, so that the number of the gear sets in the transmission is reduced, the axial length of the transmission can be reduced, and the structural design of the transmission is facilitated.
Description
Technical Field
the invention relates to the technical field of transmissions, in particular to an eight-gear transmission.
background
the Double Clutch Transmission (DCT) has the advantages of relatively smooth gear shifting, basically no power interruption and the like, and is widely applied to vehicles.
Due to the fact that the two clutches are arranged, the double-clutch transmission can be correspondingly provided with more gears, the transmission ratio difference between the adjacent gears is smaller, and gear shifting is smoother. In some existing dual clutch transmissions, due to excessive gears, a gear set (e.g., a gear set, a synchronizer, etc.) corresponding to each gear needs to be provided, so that the number of gear sets on an input shaft and an output shaft of the transmission is increased, the axial length is correspondingly increased, and the size requirement of the transmission is difficult to meet.
Disclosure of Invention
In view of the above, the present invention is directed to a transmission to solve the problem of an excessive axial length of the transmission.
In order to achieve the purpose, the technical scheme of the invention is realized as follows:
An eight-gear transmission comprises a first clutch, a second clutch, a first input shaft in transmission connection with the output end of the first clutch, a second input shaft in transmission connection with the output end of the second clutch, a first output shaft, a second output shaft, a two-gear set, a three-gear set, a four-gear set, a five-gear set, a six-gear set and a seven-gear set,
Wherein the first input shaft and the second input shaft are coaxially disposed,
The first input shaft can be respectively connected with the second output shaft through the three-gear set in a transmission manner to realize a three-gear transmission ratio, connected with the first output shaft through the five-gear set in a transmission manner to realize a five-gear transmission ratio, and connected with the second output shaft through the seven-gear set in a transmission manner to realize a seven-gear transmission ratio,
The second input shaft can be respectively connected with the first output shaft through the two-gear set in a transmission manner to realize a two-gear transmission ratio, connected with the second output shaft through the four-gear set in a transmission manner to realize a four-gear transmission ratio, and connected with the first output shaft through the six-gear set in a transmission manner to realize a six-gear transmission ratio,
The first input shaft can be connected to the first output shaft in a transmission mode through the three-gear set, the four-gear set and the two-gear set in sequence to achieve a first-gear transmission ratio; the second input shaft can be connected with the second output shaft in a transmission mode through the four-gear set, the three-gear set and the seven-gear set in sequence so as to achieve an eight-gear transmission ratio.
Further, the second input shaft is a hollow shaft, and the first input shaft penetrates through the second input shaft.
further, the first clutch and the second clutch are collectively formed as a double-sided clutch.
Furthermore, a third-gear synchronizer which can be in transmission connection with the third-gear set, a fourth-gear synchronizer which can be in transmission connection with the fourth-gear set and a seventh-gear synchronizer which can be in transmission connection with the seventh-gear set are arranged on the second output shaft.
Further, the eight-gear transmission comprises a transition synchronizer coaxially arranged on the second output shaft, and the three-gear set and the four-gear set can be in transmission connection through the transition synchronizer.
furthermore, a second gear synchronizer which can be in transmission connection with the second gear set, a fifth gear synchronizer which can be in transmission connection with the fifth gear set and a sixth gear synchronizer which can be in transmission connection with the sixth gear set are arranged on the first output shaft.
further, the three-gear synchronizer and the seven-gear synchronizer are jointly formed into a bilateral synchronizer, and the two-gear synchronizer and the six-gear synchronizer are jointly formed into a bilateral synchronizer.
Further, the five-gear set and the seven-gear set share a gear coaxially connected to the first input shaft.
further, the eight-gear transmission comprises a reverse gear idler shaft, and the second input shaft can be connected to the first output shaft through the reverse gear idler shaft in a transmission mode to achieve a reverse gear transmission ratio. Further, the eight speed transmission comprises a reverse gear idler shaft, and the first input shaft can be in transmission connection with the reverse gear idler shaft through a reverse gear driven gear coaxially arranged on the first output shaft so as to realize a reverse gear transmission ratio.
In the eight-gear transmission, the transmission ratio of the first gear and the eight gears is realized by three gears from the second gear to the seventh gear, so that the number of the gears in the transmission is reduced, the axial length of the transmission can be reduced, and the structural design of the transmission is facilitated.
additional features and advantages of the invention will be set forth in the detailed description which follows.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate an embodiment of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
FIG. 1 is a diagrammatic view of an eight speed transmission according to one embodiment of the present invention;
fig. 2 is a schematic diagram of an eight speed transmission according to another embodiment of the present invention.
description of reference numerals:
1-fifth-gear driven gear, 2-reverse-gear driven gear, 3-second reverse-gear, 4-reverse-gear idler shaft, 5-second-gear driven gear, 6-first reverse-gear, 7-gear driving gear, 8-third-gear driving gear, 9-sixth-gear driven gear, 10-sixth-gear driving gear, 11-first output gear, 12-first output shaft, 13-second clutch, 14-first clutch, 15-second input shaft, 16-first input shaft, 17-second output gear, 18-second output shaft, 19-differential gear ring, 20-differential output shaft, 21-seventh-gear driving gear, 22-fourth-gear driving gear, 23-fourth-gear driven gear, 24-third-gear driven gear, 25-seventh-gear driven gear, the automatic transmission comprises an A-seventh gear synchronizer, a B-third gear synchronizer, a C-transition synchronizer, a D-fourth gear synchronizer, an E-fifth gear synchronizer, an F-second reverse gear synchronizer, a G-second gear synchronizer, an H-sixth gear synchronizer and an I-first reverse gear synchronizer.
Detailed Description
In addition, the embodiments of the present invention and the features of the embodiments may be combined with each other without conflict.
The present invention will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.
the invention provides an eight-gear transmission, which comprises a first clutch 14, a second clutch 13, a first input shaft 16 in transmission connection with the output end of the first clutch 14, a second input shaft 15 in transmission connection with the output end of the second clutch 13, a first output shaft 12, a second output shaft 18, a two-gear set, a three-gear set, a four-gear set, a five-gear set, a six-gear set and a seven-gear set,
wherein the first input shaft 16 and the second input shaft 15 are coaxially arranged,
The first input shaft 16 is capable of being drivingly connected to the second output shaft 18 through the three-gear set to achieve a three-gear transmission ratio, drivingly connected to the first output shaft 12 through the five-gear set to achieve a five-gear transmission ratio, drivingly connected to the second output shaft 18 through the seven-gear set to achieve a seven-gear transmission ratio,
The second input shaft 15 can be respectively connected to the first output shaft 12 through the two-gear set to realize a two-gear transmission ratio, connected to the second output shaft 18 through the four-gear set to realize a four-gear transmission ratio, and connected to the first output shaft 12 through the six-gear set to realize a six-gear transmission ratio,
The first input shaft 16 can be connected to the first output shaft 12 in a transmission manner through the three-gear set, the four-gear set and the two-gear set in sequence to realize a first-gear transmission ratio; the second input shaft 15 can be connected to the second output shaft 18 in a transmission manner through the four-gear set, the three-gear set and the seven-gear set in sequence to realize an eight-gear transmission ratio.
the first input shaft 16 and the second input shaft 15 may be disposed in parallel with the first output shaft 12 and the second output shaft 18, and parallel shaft transmission may be implemented by respective gear sets, and in one to eight gears transmission, the rotation direction of the first input shaft 16 and the second input shaft 15 may be opposite to the rotation direction of the first output shaft 12 and the second output shaft 18.
in the second-gear to seventh-gear transmission, each gear is driven by a gear set which is relatively independent, for example, the gear sets may generally include two gears which are coaxially disposed with the driving shaft and the driven shaft, respectively, so as to realize parallel shaft transmission. In the first-gear and eight-gear transmission, three of two-gear to seven-gear sets are adopted, and corresponding transmission ratios are realized through three-time transmission (each gear set is regarded as one-time transmission).
Because the first gear and the eight gear adopt the gear sets from the second gear to the seventh gear, the number of the gear sets can be reduced, thereby reducing the axial length, reducing the overall length of the transmission and facilitating the design of a space structure.
The second input shaft 15 is a hollow shaft, and the first input shaft 16 is disposed through the second input shaft 15. The first input shaft 16 and the second input shaft 15 are coaxially sleeved, so that the axial length occupied by the two input shafts can be reduced, and the internal space of the transmission is saved.
Further, the first clutch 14 and the second clutch 13 are collectively formed as a double-sided clutch. In the double-sided clutch, the first clutch 14 and the second clutch 13 have the same input end, and the double-sided clutch may be selected to output torque by the first clutch 14 or the second clutch 13, that is, selected to output torque by the first input shaft 16 or the second input shaft 15, and the first input shaft 16 and the second input shaft 15 cannot output torque at the same time, that is, the first input shaft 16 and the second input shaft 15 cannot be connected to the respective corresponding clutches at the same time. Two input shafts are coaxially sleeved, and the two clutches form bilateral clutches, so that the overall occupied axial space can be reduced, and the structural design of the transmission is facilitated.
Specifically, the second output shaft 18 is provided with a three-gear synchronizer B which can be in transmission connection with the three-gear set, a four-gear synchronizer D which can be in transmission connection with the four-gear set, and a seven-gear synchronizer a which can be in transmission connection with the seven-gear set.
the three-gear set comprises two gears which are meshed with each other, namely a three-gear driving gear 8 which is coaxially connected to the first input shaft 16 and a three-gear driven gear 24 which is coaxially arranged on the second output shaft 18, and the three-gear synchronizer B can synchronously drive and connect the three-gear driven gear 24 to the second output shaft 18, so that the driving connection of the first input shaft 16 and the second output shaft 18 is realized, and the three-gear transmission ratio can be realized.
The four-gear set includes two gears meshed with each other, that is, a four-gear driving gear 22 coaxially connected to the second input shaft 15 and a four-gear driven gear 23 coaxially disposed on the second output shaft 18, and the four-gear synchronizer D may connect the four-gear driven gear 23 to the second output shaft 18 in a synchronous transmission manner, so that the transmission connection between the second input shaft 15 and the second output shaft 18 is realized, and a four-gear transmission ratio is realized.
The seven-gear set comprises two gears which are meshed with each other, namely a seven-gear driving gear 21 which is coaxially connected to the first input shaft 16 and a seven-gear driven gear 25 which is coaxially arranged on the second output shaft 18, and the seven-gear synchronizer a can synchronously drive and connect the seven-gear driven gear 25 to the second output shaft 18, so that the transmission connection of the first input shaft 16 and the second output shaft 18 is realized, and the seven-gear transmission ratio can be realized.
In addition, the eight speed transmission includes a transition synchronizer C coaxially disposed at the second output shaft 18, and the three-gear set and the four-gear set can be drivingly connected through the transition synchronizer C. The transition synchronizer C may synchronously connect the third-gear driven gear 24 and the fourth-gear driven gear 23 to synchronously connect the third-gear set and the fourth-gear set so as to realize the first-gear transmission ratio and the eighth-gear transmission ratio described above.
Specifically, the first output shaft 12 is provided with a second-gear synchronizer G capable of being in transmission connection with the second-gear set, a fifth-gear synchronizer E capable of being in transmission connection with the fifth-gear set, and a sixth-gear synchronizer H capable of being in transmission connection with the sixth-gear set.
The two-gear set comprises two gears which are meshed with each other, namely a two-gear driving gear 7 which is coaxially connected to the second input shaft 15 and a two-gear driven gear 5 which is coaxially arranged on the first output shaft 12, and the two-gear synchronizer G can synchronously drive and connect the two-gear driven gear 5 to the first output shaft 12, so that the transmission connection of the second input shaft 15 and the first output shaft 12 is realized, and the two-gear transmission ratio is realized.
the fifth-gear set comprises two gears which are meshed with each other, namely a seventh-gear driving gear 21 which is coaxially connected to the first input shaft 16 and a fifth-gear driven gear 1 which is coaxially arranged on the first output shaft 12, and the fifth-gear synchronizer E can synchronously drive and connect the fifth-gear driven gear 1 to the first output shaft 12, so that the first input shaft 16 is in transmission connection with the first output shaft 12, and a fifth-gear transmission ratio is realized.
The six-gear set comprises two gears which are meshed with each other, namely a six-gear driving gear 10 which is coaxially connected to the second input shaft 15 and a six-gear driven gear 9 which is coaxially arranged on the first output shaft 12, and the six-gear synchronizer H can synchronously drive and connect the six-gear driven gear 9 to the first output shaft 12, so that the transmission connection of the second input shaft 15 and the first output shaft 12 is realized, and the six-gear transmission ratio is realized.
further, the three-gear synchronizer B and the seven-gear synchronizer a are jointly formed as a bilateral synchronizer, and the two-gear synchronizer G and the six-gear synchronizer H are jointly formed as a bilateral synchronizer. When two synchronizers form a double-sided synchronizer, a part of the structure can be shared, the number of integral parts can be reduced, and particularly, the axial length can be reduced. For example, the synchronizer may include a spline hub and a joint sleeve coaxial with the first output shaft 12 or the second output shaft 18, the joint sleeve may be simultaneously engaged with the spline hub and other gears in the axial direction by moving the joint sleeve, so that the spline hub and other gears are synchronously rotated, so that a synchronizing function is achieved, and in the bilateral synchronizer, one spline hub and joint sleeve may be shared by two synchronizers, of course, the structures of different types of synchronizers are different, but there is still a part that can be shared.
in addition, the fifth-gear set and the seventh-gear set share a gear coaxially connected to the first input shaft 16. As shown in fig. 1 and 2, each of the fifth gear set and the seventh gear set includes a seventh gear driving gear 21 coaxially connected to the first input shaft 16, and the number of gears provided on the first input shaft 16 can be reduced by sharing the same driving gear, and the axial length can be further reduced.
Furthermore, the eight speed transmission can also realize reverse gear transmission ratio, for example, by providing the reverse gear idler shaft 4, and realizing the reverse gear transmission ratio through two transmissions between the input shaft (the first input shaft 16 or the second input shaft 15), the reverse gear idler shaft 4 and the output shaft (the first output shaft 12 or the second output shaft 18). In the above first-gear to eighth-gear transmission, primary transmission or tertiary transmission is provided, in which each transmission (gear transmission) can realize direction change of torque, and in the reverse transmission, secondary transmission is provided, thereby realizing torque output opposite to the first-gear to eighth-gear transmission.
in addition, according to one embodiment of the present invention, the eight speed transmission comprises a reverse gear idler shaft 4, and the second input shaft 15 can be connected to the first output shaft 12 through the reverse gear idler shaft 4 to realize a reverse gear transmission ratio. As shown in fig. 1, the second input shaft 15 is provided with a fourth gear driving gear 22, the fourth gear driving gear 22 can be in transmission connection with the first reverse gear 6 of the reverse gear idler shaft 4, the second input shaft 15 can transmit power to the reverse gear idler shaft 4, the second reverse gear 3 coaxially connected to the reverse gear idler shaft 4 can be in transmission connection with the reverse gear driven gear 2 coaxially provided to the first output shaft 12, and the first reverse synchronizer I provided to the first output shaft 12 can synchronously transmit the reverse gear driven gear 2 to the first output shaft 12, so that a reverse gear transmission ratio is realized, that is, the reverse gear torque is output by transmitting the reverse gear driven gear 2 from the second input shaft 15 to the reverse gear idler shaft 4 and then to the first output shaft 12.
According to another embodiment of the invention, the eight speed transmission comprises a reverse idler shaft 4, the first input shaft 16 being drivingly connectable to the reverse idler shaft 4 via a reverse driven gear 2 coaxially arranged to the first output shaft 12 for achieving a reverse gear transmission ratio. In this embodiment, the reverse driven gear 2 coaxially disposed on the first output shaft 12 may be in transmission connection with the second reverse gear 3 coaxially disposed on the reverse idler shaft 4, and the second reverse synchronizer F disposed on the reverse idler shaft 4 may be in synchronous transmission connection with the second reverse gear 3 on the reverse idler shaft 4, that is, the first input shaft 16 is in transmission connection with the second reverse gear 3 through the three-gear driving gear 8 and the reverse driven gear 2, and the reverse idler shaft 4 realizes torque output through the first reverse gear 6, thereby realizing a reverse transmission ratio.
The drive paths for the first to eighth gears and the reverse gear (R gear) of the eight speed transmission will be described in detail below.
A first gear transmission route:
The first clutch 14 → the first input shaft 16 → the third-gear drive gear 8 → the third-gear driven gear 24 → the transitional synchronizer C → the fourth-gear driven gear 23 → the fourth-gear drive gear 22 → the second input shaft 15 → the second-gear drive gear 7 → the second-gear driven gear 5 → the second synchronizer G → the first output shaft 12 → the first output gear 11 → the differential ring gear 19 → the differential output shaft 20;
A second-gear transmission route:
Second clutch 13 → second input shaft 15 → second drive gear 7 → second driven gear 5 → second synchronizer G → first output shaft 12 → first output gear 11 → differential ring gear 19 → differential output shaft 20;
A third gear transmission route:
the first clutch 14 → the first input shaft 16 → the third-gear drive gear 8 → the third-gear driven gear 24 → 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 D → 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 first clutch 14 → the first input shaft 16 → the seven-speed drive gear 21 → the five-speed driven gear 1 → the five-speed synchronizer E → the first output shaft 12 → the first 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 gear driving gear 10 → the sixth gear driven gear 9 → the sixth gear synchronizer H → the first output shaft 12 → the first output gear 11 → the differential ring gear 19 → the differential output shaft 20;
A seven-gear transmission route:
The first clutch 14 → the first input shaft 16 → the seven-speed drive gear 21 → the seven-speed driven gear 25 → 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 fourth-gear drive gear 22 → the fourth-gear driven gear 23 → the transitional synchronizer C → the third-gear driven gear 24 → the third-gear drive gear 8 → the first input shaft 16 → the seventh-gear drive gear 21 → the seventh-gear driven gear 25 → 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;
reverse gear drive path (shown in fig. 1):
The second clutch 13 → the second input shaft 15 → the fourth-gear driving gear 22 → the first reverse gear 6 → the reverse idler shaft 4 → the second reverse gear 3 → the reverse driven gear 2 → the first reverse synchronizer I → the first output shaft 12 → the first output gear 11 → the differential ring gear 19 → the differential output shaft 20;
Reverse gear drive path (shown in fig. 2):
The first clutch 14 → the first input shaft 16 → the third drive gear 8 → the reverse driven gear 2 → the second reverse gear 3 → the second reverse synchronizer F → the reverse idler shaft 4 → the first reverse gear 6 → the differential ring gear 19 → the differential output shaft 20.
wherein the third gear driving gear 8 and the seventh gear driving gear 21 are coaxially connected to the first input shaft 16, i.e. can rotate synchronously with the first input shaft 16, the fourth gear driving gear 22, the second gear driving gear 7 and the sixth gear driving gear 10 are coaxially connected to the second input shaft 15, i.e. can rotate synchronously with the second input shaft 15, the first reverse gear 6 and the second reverse gear 3 in fig. 1 are coaxially connected to the reverse idler shaft 4, i.e. can rotate synchronously with the reverse idler shaft 4, the second reverse gear 3 in fig. 2 can rotate relative to the reverse idler shaft 4, the fifth gear driven gear 1, the reverse driven gear 2, the second gear driven gear 5 and the sixth gear driven gear 9 are coaxially arranged to the first output shaft 12, i.e. can rotate relative to the first output shaft 12, the seventh gear driven gear 25, the third gear driven gear 24 and the fourth gear driven gear 23 are coaxially arranged to the second output shaft 18, i.e. rotatable relative to the second output shaft 18.
the above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.
Claims (10)
1. An eight-gear transmission is characterized by comprising a first clutch (14), a second clutch (13), a first input shaft (16) in transmission connection with the output end of the first clutch (14), a second input shaft (15) in transmission connection with the output end of the second clutch (13), a first output shaft (12), a second output shaft (18), a two-gear set, a three-gear set, a four-gear set, a five-gear set, a six-gear set and a seven-gear set,
Wherein the first input shaft (16) and the second input shaft (15) are arranged coaxially,
The first input shaft (16) can be respectively in transmission connection with the second output shaft (18) through the three-gear set to realize a three-gear transmission ratio, in transmission connection with the first output shaft (12) through the five-gear set to realize a five-gear transmission ratio, and in transmission connection with the second output shaft (18) through the seven-gear set to realize a seven-gear transmission ratio,
The second input shaft (15) can be respectively connected with the first output shaft (12) through the two-gear set in a transmission manner to realize a two-gear transmission ratio, connected with the second output shaft (18) through the four-gear set in a transmission manner to realize a four-gear transmission ratio, and connected with the first output shaft (12) through the six-gear set in a transmission manner to realize a six-gear transmission ratio,
The first input shaft (16) can be connected to the first output shaft (12) in a transmission manner sequentially through the three-gear set, the four-gear set and the two-gear set so as to realize a first-gear transmission ratio; the second input shaft (15) can be connected to the second output shaft (18) in a transmission mode through the four-gear set, the three-gear set and the seven-gear set in sequence to achieve an eight-gear transmission ratio.
2. The eight speed transmission according to claim 1, wherein the second input shaft (15) is a hollow shaft and the first input shaft (16) is arranged through the second input shaft (15).
3. Eight speed transmission according to claim 2, characterized in that the first clutch (14) and the second clutch (13) are jointly formed as a double-sided clutch.
4. the eight speed transmission according to claim 1, characterized in that the second output shaft (18) is provided with a three speed synchronizer (B) which is drivingly connectable with the three speed gear set, a four speed synchronizer (D) which is drivingly connectable with the four speed gear set and a seven speed synchronizer (a) which is drivingly connectable with the seven speed gear set.
5. the eight speed transmission according to claim 4, characterized in that it comprises a transition synchronizer (C) coaxially arranged to said second output shaft (18), said three and said four gear wheel sets being drivingly connectable by said transition synchronizer (C).
6. the eight speed transmission according to claim 5, wherein the first output shaft (12) is provided with a second gear synchronizer (G) which is drivingly connectable with the second gear set, a fifth gear synchronizer (E) which is drivingly connectable with the fifth gear set, and a sixth gear synchronizer (H) which is drivingly connectable with the sixth gear set.
7. The eight speed transmission according to claim 6, wherein the three speed synchronizer (B) and the seven speed synchronizer (A) are collectively formed as a double sided synchronizer, and the two speed synchronizer (G) and the six speed synchronizer (H) are collectively formed as a double sided synchronizer.
8. the eight speed transmission according to claim 5, wherein the five and seven speed gear sets share a gear coaxially connected to the first input shaft (16).
9. The eight speed transmission according to claim 6, characterized in that it comprises a reverse idler shaft (4), said second input shaft (15) being drivingly connectable to said first output shaft (12) through said reverse idler shaft (4) to achieve a reverse gear transmission ratio.
10. the eight speed transmission according to claim 6, characterized in that it comprises a reverse idler shaft (4), said first input shaft (16) being drivingly connectable to said reverse idler shaft (4) through a reverse driven gear (2) coaxially arranged to said first output shaft (12) to achieve a reverse gear transmission ratio.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810589231.9A CN110578773A (en) | 2018-06-08 | 2018-06-08 | eight-gear transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810589231.9A CN110578773A (en) | 2018-06-08 | 2018-06-08 | eight-gear transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN110578773A true CN110578773A (en) | 2019-12-17 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810589231.9A Pending CN110578773A (en) | 2018-06-08 | 2018-06-08 | eight-gear transmission |
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| Country | Link |
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| CN (1) | CN110578773A (en) |
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| CN113915298A (en) * | 2020-07-08 | 2022-01-11 | 广州汽车集团股份有限公司 | Vehicle automatic gearbox and vehicle |
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Application publication date: 20191217 |
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