CN112283322A - Reverse gear structure and double-clutch transmission - Google Patents

Reverse gear structure and double-clutch transmission Download PDF

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Publication number
CN112283322A
CN112283322A CN201910668351.2A CN201910668351A CN112283322A CN 112283322 A CN112283322 A CN 112283322A CN 201910668351 A CN201910668351 A CN 201910668351A CN 112283322 A CN112283322 A CN 112283322A
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China
Prior art keywords
gear
output shaft
reverse
driven
shaft
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Granted
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CN201910668351.2A
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Chinese (zh)
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CN112283322B (en
Inventor
钟振远
王荣
凌晓明
张倍坚
周友
刘学武
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Guangzhou Automobile Group Co Ltd
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Guangzhou Automobile Group Co Ltd
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Priority to CN201910668351.2A priority Critical patent/CN112283322B/en
Publication of CN112283322A publication Critical patent/CN112283322A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • 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
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/085—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with more than one output shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H2003/0822—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the arrangement of at least one reverse gear

Abstract

The utility model provides a reverse gear structure and double clutch derailleur, reverse gear structure includes pivot, reverse gear selective joint the pivot is in reverse gear at least one side still is equipped with the gear, be equipped with thrust bearing between reverse gear and the gear. The reverse gear structure and the double-clutch transmission provided by the invention have the advantages that the reverse gear is separated from the gear, the processing is simpler, the precision is easy to guarantee, the three thrust bearings are arranged, so that the abrasion of the gears during relative rotation is reduced, the axial clearance can be controlled, and the working precision of the double-clutch transmission is improved.

Description

Reverse gear structure and double-clutch transmission
Technical Field
The invention relates to the technical field of vehicles, in particular to a reverse gear structure and a dual-clutch transmission.
Background
Main two separation and reunion derailleur's on the existing market reverse gear structure mostly increases a reverse shaft, increases whole two separation and reunion variable speed arrange the degree of difficulty, and derailleur radial dimension is great, and other annex arrange the difficulty, weight increase. In addition, the reverse gear and one of the gears are made into welding duplex teeth, the reverse rotation speed of the reverse gear is high during forward gear, abnormal abrasion is increased, and the precision of the reverse gear is difficult to guarantee due to welding deformation and the like.
The foregoing description is provided for general background information and is not admitted to be prior art.
Disclosure of Invention
The invention aims to provide a reverse gear structure capable of reducing abrasion among gears and a dual-clutch transmission.
The invention provides a reverse gear structure, which comprises a rotating shaft and a reverse gear, wherein the reverse gear is selectively jointed with the rotating shaft, a gear is also arranged on at least one side of the rotating shaft on the reverse gear, and a thrust bearing is arranged between the reverse gear and the gear.
Further, a reverse synchronizer is included through which the reverse gear selectively engages the rotary shaft.
The invention also provides a double-clutch transmission which comprises a first clutch, a second clutch, a first input shaft, a second input shaft, a first output shaft and a second output shaft; the first clutch is connected with the first input shaft, and the second clutch is connected with the second input shaft; the first input shaft, the second input shaft, the first output shaft and the second output shaft are respectively provided with a plurality of gears; the first gear on the second input shaft is meshed with the second gear of the second output shaft, the second gear of the second output shaft is meshed with the third gear of the first output shaft, the third gear of the first output shaft drives the fourth gear of the first output shaft, the fourth gear of the first output shaft is meshed with the fifth gear of the first input shaft, the fifth gear of the first input shaft drives the sixth gear of the first input shaft, the sixth gear of the first input shaft is meshed with the seventh gear of the second output shaft, the seventh gear of the second output shaft drives the eighth gear of the second output shaft, reverse gear is provided through the eighth gear output, the third gear of the first output shaft is a reverse gear, and a thrust bearing is arranged between the third gear of the first output shaft and the fourth gear of the first output shaft.
Further, the third gear of the first output shaft and the fourth gear of the first output shaft are connected through a synchronizer.
The invention also provides a double-clutch transmission which comprises a first clutch, a second clutch, a first input shaft, a second input shaft, a first output shaft and a second output shaft; the first clutch is connected with the first input shaft, and the second clutch is connected with the second input shaft; the first input shaft is provided with a fifth-seventh gear driving gear, a third gear driving gear and a first gear driving gear; the second input shaft is provided with a fourth and sixth-gear driving gear and a second-gear driving gear; the first output shaft is provided with a first output shaft main reduction gear, a sixth-gear driven gear, a reverse gear, a third-gear driven gear and a seventh-gear driven gear, and the sixth-gear driven gear, the reverse gear, the third-gear driven gear and the seventh-gear driven gear are selectively jointed to the first output shaft; a second output shaft main reduction gear, a fourth-gear driven gear, a second-gear driven gear, a first-gear driven gear, a fifth-gear driven gear and a parking gear are arranged on the second output shaft, and the fourth-gear driven gear, the second-gear driven gear, the first-gear driven gear and the fifth-gear driven gear are selectively jointed to the second output shaft; the second-gear driving gear on the second input shaft is meshed with the second-gear driven gear of the second output shaft, the second-gear driven gear of the second output shaft is meshed with the reverse gear of the first output shaft, the reverse gear of the first output shaft drives the third-gear driven gear of the first output shaft, the third-gear driving gear of the first input shaft drives the first-gear driving gear of the first input shaft, the first-gear driven gear of the first output shaft is meshed with the first-gear driving gear of the first input shaft, the first-gear driving gear of the first input shaft is meshed with the first-gear driven gear of the second output shaft, the first-gear driven gear of the second output shaft drives the second-output-shaft driving reduction gear of the second output shaft, and the reverse gear is provided through the output of the second-output-shaft driving; and a thrust bearing is arranged on the first output shaft between the reverse gear and the third driven gear.
Furthermore, a sixth-gear synchronizer used for enabling the sixth-gear driven gear to be selectively engaged with the first output shaft is further arranged on the first output shaft corresponding to the sixth-gear driven gear, and a reverse-gear synchronizer used for enabling the reverse gear to be selectively engaged with the first output shaft is arranged corresponding to the reverse gear.
Further, a thrust bearing is arranged between the six-gear synchronizer and the reverse gear.
Further, a pseudo-gear synchronizer enabling the first output shaft to selectively engage the third-gear driven gear and the seventh-gear driven gear is further arranged between the third-gear driven gear and the seventh-gear driven gear on the first output shaft.
Furthermore, a thrust bearing is arranged between the third-gear driven gear and the seventh-gear driven gear on the first output shaft.
Further, a second fourth-gear synchronizer for selectively connecting the second output shaft with the fourth-gear driven gear and the second-gear driven gear is arranged between the fourth-gear driven gear and the second-gear driven gear on the second output shaft, and a first fifth-gear synchronizer for selectively connecting the second output shaft with the first-gear driven gear and the fifth-gear driven gear is arranged between the first-gear driven gear and the fifth-gear driven gear on the second output shaft.
The reverse gear structure and the double-clutch transmission provided by the invention have the advantages that the reverse gear is separated from the gear, the processing is simpler, the precision is easy to guarantee, the three thrust bearings are arranged, so that the abrasion of the gears during relative rotation is reduced, the axial clearance can be controlled, and the working precision of the double-clutch transmission is improved.
Drawings
FIG. 1 is a schematic representation of a dual clutch transmission and associated components according to an embodiment of the present invention.
FIG. 2 is a schematic representation of a reverse configuration in the dual clutch transmission of FIG. 1.
FIG. 3 is a reverse power flow diagram of the dual clutch transmission of FIG. 1 and associated components.
FIG. 4 is a schematic first gear power flow diagram of the dual clutch transmission of FIG. 1 and associated components.
Detailed Description
The following detailed description of embodiments of the present invention is provided in connection with the accompanying drawings and examples. The following examples are intended to illustrate the invention but are not intended to limit the scope of the invention.
As shown in fig. 1 to 4, the dual clutch transmission in the present embodiment includes a first clutch 2, a second clutch 3, a first input shaft 8, a second input shaft 7, a first output shaft 4, and a second output shaft 5. The first clutch 2 and the second clutch 3 form a double clutch, one end of the double clutch is connected with the engine 1, and the other end of the double clutch is connected with the first input shaft 8 and the second input shaft 7 respectively. The second input shaft 7 is a hollow shaft structure, also called an outer input shaft. The first input shaft 8 passes through the second input shaft 7, also called inner input shaft.
The first input shaft 8 is provided with a fifth-seventh gear driving gear 8.1, a third gear driving gear 8.2 and a first gear driving gear 8.3 in sequence along the axial direction.
The second input shaft 7 is provided with a fourth-sixth gear driving gear 7.1 and a second-sixth gear driving gear 7.2 in sequence along the axial direction.
As shown in fig. 2, a first output shaft main reduction gear 4.1, a sixth-gear driven gear 4.2, a sixth-gear synchronizer 4.3, a reverse gear 4.5, a reverse synchronizer 4.6, a third-gear driven gear 4.8, a pseudo-ginseng gear synchronizer 4.10 and a seventh-gear driven gear 4.11 are sequentially arranged on the first output shaft 4 along the axial direction. The sixth and reverse synchronizers 4.3, 4.6 are used to selectively engage the sixth and reverse driven gears 4.2, 4.5, respectively, with the first output shaft 4. The pseudo-gear synchronizer 4.10 is used to selectively engage the first output shaft 4 with the third gear driven gear 4.8 and the seventh gear driven gear 4.11. Thrust bearings 4.4, 4.7 and 4.9 are respectively arranged on the first output shaft 4 and between the sixth-gear synchronizer 4.3 and the reverse gear 4.5, between the reverse gear 4.5 and the third-gear driven gear 4.8 and between the third-gear driven gear 4.8 and the seventh-gear driven gear 4.11.
And a second output shaft main reducing gear 5.1, a fourth-gear driven gear 5.2, a second-fourth-gear synchronizer 5.3, a second-gear driven gear 5.4, a first-gear driven gear 5.5, a first-fifth-gear synchronizer 5.6, a fifth-gear driven gear 5.7 and a parking gear 5.8 are sequentially arranged on the second output shaft 5 along the axial direction. A second-fourth synchronizer 5.3 is used to selectively engage the second output shaft 5 with the second-fourth driven gear 5.4 and the fourth driven gear 5.2, and a fifth synchronizer 5.6 is used to selectively engage the second output shaft 5 with the first driven gear 5.5 and the fifth driven gear 5.7.
The first output shaft main reduction gear 4.1 and the second output shaft main reduction gear 5.1 are meshed with a main reduction driven gear 9.1, and the main reduction driven gear 9.1 transmits torque to wheels 6 through a differential assembly 9, so that the vehicle is pushed to move forwards or backwards.
The five-seventh gear driving gear 8.1 is meshed with the five-gear driven gear 5.7 and the seven-gear driven gear 4.11; the third gear driving gear 8.2 is meshed with the third gear driven gear 4.8; the first-gear driving gear 8.3 is meshed with the first-gear driven gear 5.5; the four-sixth gear driving gear 7.1 is meshed with the four-fourth gear driven gear 5.2 and the six-sixth gear driven gear 4.2; the second gear driving gear 7.2 is meshed with the second gear driven gear 5.4.
As shown in fig. 3, the first-gear function is implemented as follows: the engine 1 is selectively jointed with the first clutch 2, the first clutch 2 is connected with the first input shaft 8, the first input shaft 8 drives the first-gear driving gear 8.3 to rotate, the first-gear driving gear 8.3 is meshed with the first-gear driven gear 5.5, the second output shaft 5 is selectively jointed with the first-gear driven gear 5.5 through the fifth-gear synchronizer 5.6, so that the second output shaft 5 is driven to rotate, the second output shaft main reduction gear 5.1 is driven to rotate, and the first gear is provided through the output of the second output shaft main reduction gear 5.1. The output mode is that the main reducing gear 5.1 is meshed with the main reducing driven gear 9.1 through the second output shaft, the torque is transmitted to the wheels 6 through the differential assembly 9, and the vehicle is pushed to move forward in the first gear.
The other forward gear function implementation is similar to the first gear, and will not be described herein again.
As shown in fig. 4, the reverse function is realized by: the second input shaft 7 is connected through the second clutch 3, a second-gear driving gear 7.2 on the second input shaft 7 is meshed with a second-gear driven gear 5.4 of the second output shaft 5, the second-gear driven gear 5.4 of the second output shaft 5 is meshed with a reverse gear 4.5 of the first output shaft 4, the reverse gear 4.5 of the first output shaft 4 drives a third-gear driven gear 4.8 of the first output shaft 4, the third-gear driven gear 4.8 of the first output shaft 4 is meshed with a third-gear driving gear 8.2 of the first input shaft 8, the third-gear driving gear 8.2 drives a first-gear driving gear 8.3, the first-gear driving gear 8.3 is meshed with a first-gear driven gear 5.5 of the second output shaft 5, the first-gear driven gear 5.5 of the second output shaft 5 drives a second output shaft main reducing gear 5.1 of the second output shaft 5, and a reverse gear is provided through the output of the second output shaft main reducing gear 5.1. The output mode is that the main reducing gear 5.1 is meshed with the main reducing driven gear 9.1 through the second output shaft, the torque is transmitted to the wheels 6 through the differential assembly 9, and the vehicle is pushed to move backwards.
In other embodiments, a reverse mechanism may be provided in a dual clutch transmission of other configurations. It is only necessary to engage the second gear (corresponding to the second-gear driven gear 5.4 in this embodiment) of the second output shaft 5 through the first gear (corresponding to the second-gear driving gear 7.2 in this embodiment) on the second input shaft 7, the second gear of the second output shaft 5 engages the third gear (corresponding to the reverse gear 4.5 in this embodiment) of the first output shaft 4, the third gear of the first output shaft 4 drives the fourth gear (corresponding to the third-gear driven gear 4.8 in this embodiment) of the first output shaft 4, the fourth gear of the first output shaft 4 engages the fifth gear (corresponding to the third-gear driving gear 8.2 in this embodiment) of the first input shaft 8, the fifth gear of the first input shaft drives the sixth gear (corresponding to the first-gear driving gear 8.3 in this embodiment) of the first input shaft 8, the sixth gear of the first input shaft 8 engages the seventh gear (corresponding to the first-gear driven gear 5.5 in this embodiment) of the second output shaft 5, the seventh gear of the second output shaft 5 drives the eighth gear of the second output shaft 5 (corresponding to the second output shaft main reduction gear 5.1 in this embodiment), and the reverse gear 4.5 can be arranged on the first output shaft 4 by outputting the eighth gear to provide a reverse gear, so that the reverse gear function can be realized by using the existing rotating shaft, the accessories such as the reverse gear shaft and the like are reduced, the space arrangement is facilitated, and the weight of the whole box is reduced.
In the embodiment, the gear synchronizer is connected with the gear and the reverse gear to form the duplex gear, so that the problem of insufficient precision of welding the duplex gear is solved. Of course, in other embodiments, a welded double-linkage tooth structure may be used, as desired.
In the embodiment, the three thrust bearings are adopted on the first output shaft provided with the reverse gear, so that the abrasion of the opposite reverse axial end surfaces in the operation process is avoided, and the minimum axial clearance in the whole reverse gear structure can be ensured. Of course, in other embodiments, thrust bearings may not be provided, as desired.
Therefore, the reverse gear structure of the embodiment of the invention separates the reverse gear from the gear, the processing is simpler, the precision is easy to guarantee, the three thrust bearings are arranged, the purpose is to reduce the abrasion when the gears rotate relatively, in addition, the axial clearance can be controlled, and the working precision of the double-coupling gear is improved. The double-clutch transmission provided by the embodiment of the invention has the advantages that the reasonable layout and power flow transmission route are adopted in the double-clutch transmission, the high-efficiency transmission efficiency can be realized, the integration level of the whole system is high, the size is small, the weight is light, and the arrangement is simple.
The double-clutch transmission and the main speed reduction driven gear form a gearbox.
In this document, the terms "upper", "lower", "front", "rear", "left", "right", "top", "bottom", "inner", "outer", "vertical", "horizontal", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for the purpose of clarity and convenience of description of the technical solutions, and thus, should not be construed as limiting the present invention.
As used herein, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, including not only those elements listed, but also other elements not expressly listed.
As used herein, the ordinal adjectives "first", "second", etc., used to describe an element are merely to distinguish between similar elements and do not imply that the elements so described must be in a given sequence, either temporally, spatially, in ranking, or in any other manner.
The above description is only for the specific embodiments of the present invention, but the scope of the present invention is not limited thereto, and any person skilled in the art can easily conceive of the changes or substitutions within the technical scope of the present invention, and all the changes or substitutions should be covered within the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the appended claims.

Claims (10)

1. A reverse gear structure is characterized by comprising a rotating shaft (4) and a reverse gear (4.5), wherein the reverse gear (4.5) is selectively connected with the rotating shaft (4), the rotating shaft (4) is further provided with gear gears (4.2, 4.8) on at least one side of the reverse gear (4.5), and a thrust bearing (4.7) is arranged between the reverse gear (4.5) and the gear gears (4.8).
2. The reverse arrangement according to claim 1, further comprising a reverse synchronizer (4.6), the reverse gear (4.5) selectively engaging the rotary shaft (4) through the reverse synchronizer (4.6).
3. A dual clutch transmission is characterized by comprising a first clutch (2), a second clutch (3), a first input shaft (8), a second input shaft (7), a first output shaft (4) and a second output shaft (5); the first clutch (2) is connected with the first input shaft (8), and the second clutch (3) is connected with the second input shaft (7); the first input shaft (8), the second input shaft (7), the first output shaft (4) and the second output shaft (5) are respectively provided with a plurality of gears; the first gear (7.2) on the second input shaft (7) is meshed with the second gear (5.4) of the second output shaft (5), the second gear (5.4) of the second output shaft (5) is meshed with the third gear (4.5) of the first output shaft (4), the third gear (4.5) of the first output shaft (4) drives the fourth gear (4.8) of the first output shaft (4), the fourth gear (4.8) of the first output shaft (4) is meshed with the fifth gear (8.2) of the first input shaft (8), the fifth gear (8.2) of the first input shaft (8) drives the sixth gear (8.3) of the first input shaft (8), the sixth gear (8.3) of the first input shaft (8) is meshed with the seventh gear (5.5) of the second output shaft (5), the seventh gear (5.5) of the second output shaft (5) drives the eighth gear (5.5) of the second output shaft (5), and the eighth reverse gear (1.5) is provided, the third gear (4.5) of the first output shaft (4) is a reverse gear (4.5), and a thrust bearing (4.7) is arranged between the third gear (4.5) of the first output shaft (4) and the fourth gear (4.8) of the first output shaft (4).
4. Double-clutch transmission according to claim 3, characterised in that the third gear wheel (4.5) of the first output shaft (4) is connected via a synchronizer (4.6).
5. A dual clutch transmission is characterized by comprising a first clutch (2), a second clutch (3), a first input shaft (8), a second input shaft (7), a first output shaft (4) and a second output shaft (5); the first clutch (2) is connected with the first input shaft (8), and the second clutch (3) is connected with the second input shaft (7); a fifth-seventh gear driving gear (8.1), a third gear driving gear (8.2) and a first gear driving gear (8.3) are arranged on the first input shaft (8); a fourth and sixth-gear driving gear (7.1) and a second-gear driving gear (7.2) are arranged on the second input shaft (7); a first output shaft main reduction gear (4.1), a six-gear driven gear (4.2), a reverse gear (4.5), a third-gear driven gear (4.8) and a seventh-gear driven gear (4.11) are arranged on the first output shaft (4), and the six-gear driven gear (4.2), the reverse gear (4.5), the third-gear driven gear (4.8) and the seventh-gear driven gear (4.11) are selectively jointed to the first output shaft (4); a second output shaft main reduction gear (5.1), a fourth-gear driven gear (5.2), a second-gear driven gear (5.4), a first-gear driven gear (5.5), a fifth-gear driven gear (5.7) and a parking gear (5.8) are arranged on the second output shaft (5), and the fourth-gear driven gear (5.2), the second-gear driven gear (5.4), the first-gear driven gear (5.5) and the fifth-gear driven gear (5.7) are selectively jointed to the second output shaft (5); the second-gear driving gear (7.2) on the second input shaft (7) is meshed with the second-gear driven gear (5.4) of the second output shaft (5), the second-gear driven gear (5.4) of the second output shaft (5) is meshed with the reverse gear (4.5) of the first output shaft (4), the reverse gear (4.5) of the first output shaft (4) drives the third-gear driven gear (4.8) of the first output shaft (4), the third-gear driven gear (4.8) of the first output shaft (4) is meshed with the third-gear driving gear (8.2) of the first input shaft (8), the third-gear driving gear (8.2) of the first input shaft (8) drives the first-gear driving gear (8.3) of the first input shaft (8) is meshed with the first-gear driven gear (5.5) of the second output shaft (5), the first-gear driven gear (5.5) of the second output shaft (5) drives the second output shaft (5) to reduce the second output shaft (5) by 1.5), reverse gear is provided through the output of the second output shaft main reduction gear (5.1); and a thrust bearing (4.7) is arranged on the first output shaft (4) between the reverse gear (4.5) and the third-gear driven gear (4.8).
6. Double-clutch transmission according to claim 5, characterised in that the first output shaft (4) is also provided with a sixth-gear synchronizer (4.3) for selectively engaging the sixth-gear driven gear (4.2) with the first output shaft (4) in correspondence with the sixth-gear driven gear (4.2), and a reverse synchronizer (4.6) for selectively engaging the reverse gear (4.5) with the first output shaft (4) in correspondence with the reverse gear (4.5).
7. Double-clutch transmission according to claim 6, characterised in that a thrust bearing (4.4) is provided between the sixth synchronizer (4.3) and the reverse gear (4.5).
8. Double-clutch transmission according to claim 5, characterized in that a pseudo-gear synchronizer (4.10) is also provided on the first output shaft (4) between the third (4.8) and seventh (4.11) driven gears, which enables the first output shaft (4) to selectively engage the third (4.8) and seventh (4.11) driven gears.
9. Double-clutch transmission according to claim 8, characterised in that a thrust bearing (4.9) is provided on the first output shaft (4) between the third (4.8) and seventh (4.11) driven gears.
10. Double-clutch transmission according to claim 5, characterised in that a second four-gear synchronizer (5.3) is provided on the second output shaft (5) between the fourth-gear driven gear (5.2) and the second-gear driven gear (5.4) for the second output shaft (5) to selectively engage the fourth-gear driven gear (5.2) and the second-gear driven gear (5.4), and a fifth-gear synchronizer (5.6) is provided between the first-gear driven gear (5.5) and the fifth-gear driven gear (5.7) for the second output shaft (5) to selectively engage the first-gear driven gear (5.5) and the fifth-gear driven gear (5.7).
CN201910668351.2A 2019-07-23 2019-07-23 Reverse gear structure and double-clutch transmission Active CN112283322B (en)

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CN201910668351.2A CN112283322B (en) 2019-07-23 2019-07-23 Reverse gear structure and double-clutch transmission

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CN112283322B CN112283322B (en) 2022-01-18

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CN108397523A (en) * 2018-05-11 2018-08-14 广州汽车集团股份有限公司 Double-clutch speed changer

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