CN103185110A - Shift gearbox for vehicle - Google Patents
Shift gearbox for vehicle Download PDFInfo
- Publication number
- CN103185110A CN103185110A CN2012105990297A CN201210599029A CN103185110A CN 103185110 A CN103185110 A CN 103185110A CN 2012105990297 A CN2012105990297 A CN 2012105990297A CN 201210599029 A CN201210599029 A CN 201210599029A CN 103185110 A CN103185110 A CN 103185110A
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- China
- Prior art keywords
- gear
- output shaft
- driving wheel
- manual transmission
- input shaft
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—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 disposition of the gears
- F16H3/093—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 disposition of the gears with two or more countershafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—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 disposition of the gears
- F16H3/093—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 disposition of the gears with two or more countershafts
- F16H2003/0931—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 disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The present invention relates to a shift gearbox for vehicles with a short structure, comprising an input shaft, a first output shaft and a second output shaft and a plurality of fixed wheels and driving wheels, wherein said fixed wheels is connected to the output shaft without relative rotation through the shift device. The driving wheel of a first forward gear is engaged with the driving wheel with a reverse gear, so that an intermediate shaft or an intermediate gear for realizing reversing is not required.
Description
Technical field
The present invention relates to a kind of manual transmission for the traffic tool, comprise input shaft, first output shaft and second output shaft, wherein, fixed wheel do not have be arranged on the described input shaft with relatively rotating and with the driving wheel engagement that is arranged on first output shaft or second output shaft.
Background technique
By patent documentation DE 41 16 189 C2 a kind of such manual transmission is disclosed for example.Described driving wheel can not have with first output shaft or second output shaft by the device that can shift gears with relatively rotating and is connected.Wherein, described device of shifting gears comprises first pair of retaining clutch and second pair of retaining clutch, and described two shift clutch are arranged on first output shaft.The 3rd-gear clutch and an other gear shift clutch are set in addition, and described gear shift clutch is arranged on second output shaft.By the gear train that in patent documentation DE 41 16 189 C2, proposes, can realize comprising the manual transmission of six forward gears and a reverse gear, described manual transmission compact structure and be constructed to short structure at the axial direction of input shaft.All dispose a driving wheel for each gear at this, when hanging corresponding gear, described driving wheel does not have with relatively rotating and is connected with first output shaft or second output shaft.In addition, each driving wheel of forward gear can correspond respectively to a fixed wheel on the input shaft, wherein, each fixed wheel respectively only with a direct interlock of driving wheel of forward gear.
According to patent documentation DE 41 16 189 C2, in order to realize reverse gear, the fixed wheel engagement of the gear of an additional jack shaft and manual transmission first forward gear.The gear of described jack shaft again with the engagement of the driving wheel of reverse gear, described driving wheel is disposed on one of them output shaft of two output shafts.Gear and jack shaft just mean extra structure input and need more space.In addition, have being associated property between reverse gear and forward gear, the driving wheel of forward gear meshes with fixed wheel as the gear of jack shaft.If for example only need to change the velocity ratio of reverse gear when improving speed changer, and do not need to change the velocity ratio of corresponding forward gear, this just may mean special structure consumes.
Summary of the invention
Therefore, the objective of the invention is to, a kind of manual transmission is provided, described manual transmission compact structure and be constructed to short structure in the axial direction, and more flexible aspect each velocity ratio of coordinating gear.
Purpose of the present invention is achieved by the described feature combination of claim 1.Preferred embodiment can be by drawing in the dependent claims.
Manual transmission according to claim 1 is characterised in that, the driving wheel of first forward gear and the engagement of the driving wheel of reverse gear.In a kind of preferred embodiment, the driving wheel of first forward gear is constructed to comprise than small gear and step shape gear than gearwheel.Described than gearwheel this can with input shaft on fixed wheel engagement, described than small gear then with the driving wheel engagement of reverse gear.Also possible situation is that described driving wheel than gearwheel and reverse gear meshes, and is described than the fixed wheel interlock on small gear and the input shaft.
Therefore according to the present invention, the driving wheel of first forward gear is used as for the intermediate gear of realizing reverse gear.Therefore, hang under the situation of reverse gear, torque-flow is delivered on the driving wheel of reverse gear from the fixed wheel of first forward gear driving wheel as intermediate gear by first forward gear.Hang under the situation of reverse gear, the driving wheel that has only reverse gear does not have connection with relevant output shaft with relatively rotating.Otherwise the driving wheel of first forward gear is not have to connect with relevant output shaft hanging under the situation of reverse gear with relatively rotating, but has only when extension first forward gear, just can not have relatively rotate with relevant output shaft connection.Also can use the driving wheel of another forward gear as the intermediate gear that is used for realizing reverse gear in principle.Yet, select the driving wheel of first forward gear to realize reverse gear as intermediate gear, be proved to be to being to meet purpose especially to require.
In a kind of preferred embodiment, the driving wheel of the driving wheel of first forward gear and second forward gear can not have by first pair-gear shift clutch with relatively rotating and is connected with first output shaft.Replacement scheme or additional project be, the driving wheel of the driving wheel of the 3rd forward gear and the 4th forward gear can not have by second pair-gear shift clutch with relatively rotating and is connected with first output shaft.
The driving wheel of reverse gear can not have by a shift clutch other, that preferably be constructed to list-gear shift clutch with relatively rotating and is connected with each output shaft.The driving wheel of the driving wheel of the 5th forward gear and the 6th forward gear can not have by the 3rd pair-shift clutch with relatively rotating and is connected with each output shaft.
Two-gear shift clutch is a kind of like this gear shift clutch, by described gear shift clutch can optionally make on the output shaft two in the axial direction the driving wheel of adjacent layout do not have with relatively rotating and connect.Two-shift clutch preferably has sliding sleeve, described sliding sleeve can be from the neutral position (on this neutral position two in the axial direction the less driving wheel in the driving wheel of adjacent layout do not have with relatively rotating be connected with output shaft) slide onto first active position, described sliding sleeve is responsible for one of driving wheel at this active position and is connected in relative rotation with nothing between one of output shaft.Otherwise on second active position, another driving wheel does not have with relatively rotating and is connected with output shaft.In list-gear shift clutch, have only an active position, therefore, can only hang into a gear rather than optionally hang two gears by list-gear shift clutch.
In a kind of preferred embodiment, first driver pinion does not have and is arranged on first output shaft and second driver pinion does not have and is arranged on second output shaft with relatively rotating with relatively rotating, wherein, first driver pinion has the diameter of different sizes and takes turns interlock with ring with second driver pinion.Described ring wheel is the part at this driven device that is not further illustrated, described driven device can have for will be from the torque distribution of the manual transmission differential mechanism to two axles of the traffic tool.Can influence each velocity ratio of the gear of manual transmission targetedly by the diameter of selecting first driver pinion and second driver pinion.
It seems from the axial direction of input shaft, step shape gear than small gear can be disposed in input shaft the clutch side the end and than between the gearwheel.Described also can be on the axial direction of input shaft than small gear further away from each other the end of the clutch side of input shaft arrange.Step shape gear can be constructed to single type, yet also can be made up of two gears of making separately.
In the cross section of manual transmission, observe, the spin axis of input shaft and two output shafts can be triangular in shape, wherein, the straight line of the spin axis that connects input shaft and the spin axis of first output shaft and be connected the spin axis of input shaft and the straight line of the spin axis of second output shaft between angle be 90 ° substantially.Basically allowing with accurate 90 ° of values at this has+/-5 ° deviation.In a kind of preferred embodiment, this angle is 88.5 °, therefore, further understands the concept of " basically " at this, and namely the span of angle is between 88 ° to 92 °.
The summation of the outer diameter of the outer diameter of the swivel sleeve of list-gear shift clutch (can hang reverse gear by described swivel sleeve) and the driving wheel of first forward gear may be greater than the twice of the spacing between the spin axis of the spin axis of first output shaft and second output shaft.Therefore, will form correspondingly superimposed or coincidence between these assemblies, therefore described assembly must adjacent in the axial direction layout.
It seems that from the axial direction of input shaft the neutral position of the sliding sleeve of first pair-gear shift clutch can be disposed between the end of clutch side of the neutral position of sliding sleeve of list-gear shift clutch and input shaft.So just make manual transmission be configured to very compact and be short structure.
Description of drawings
Further set forth the present invention by the embodiment shown in the accompanying drawing.Wherein:
Fig. 1 is the sectional arrangement drawing according to manual transmission of the present invention; And
Fig. 2 is the cross-sectional views of the manual transmission of Fig. 1.
Embodiment
Fig. 1 shows whole with 1 manual transmission that indicates.Described manual transmission 1 has an input shaft 10 and two output shafts 30,50 that are arranged in parallel with described input shaft.Output shaft below occuping in the diagram of Fig. 1 is denoted as first output shaft 30 at this, and the output shaft above occuping in the diagram of Fig. 1 is denoted as second output shaft 50.
Arrange fixed wheel 11,12,13,14,15 and 16 at input shaft 10.Fixed wheel 11 is in this and driving wheel 31 engagements that are arranged on first output shaft 30.Arrange other driving wheel, i.e. driving wheel 32, driving wheel 33 and driving wheel 34 at first output shaft 30.Other driving wheel then is arranged on second output shaft 50, and what relate at this is driving wheel 51, driving wheel 52 and driving wheel 53.
First driving wheel 31 can be connected with first output shaft 30 by first pair-shift clutch, 35 nothings with second driving wheel 32 with relatively rotating.Described first pair-shift clutch 35 comprises the sliding sleeve that indicates with 39 at this, and described sliding sleeve can slide left and to the right along the spin axis 17 of input shaft 10 in other words along input shaft 10 in the diagram of Fig. 1.If described sliding sleeve 39 for example slides to the right and is positioned at so-called first active position, so just be connected in relative rotation forming nothing between first output shaft 30 and the driving wheel 31 by two-shift clutch 35.Hang the first forward gear I of described manual transmission 1 in this case.Therefore, described driving wheel 31 can be corresponding to the first forward gear I.Otherwise if sliding sleeve 39 is positioned at second active position, this sliding sleeve 39 is moved to the left in the diagram of Fig. 1 so, interconnects thereby make driving wheel 32 and first output shaft 30 not have with relatively rotating.Hang the second forward gear II in this case, wherein, torque-flow by input shaft 10 by fixed wheel 12, be delivered on first output shaft 30 with the driving wheel 32 of fixed wheel 12 engagements.
Except first pair-shift clutch 35, arrange second pair-shift clutch 36 at first output shaft 30. Driving wheel 33,34 can be connected with first output shaft 30 by this pair-shift clutch 36 nothings with relatively rotating.With the driving wheel 33 of fixed wheel 14 engagement on the input shaft 10 corresponding to the 3rd forward gear III, and with the driving wheel 34 of fixed wheel 15 engagements corresponding to the 4th forward gear IV.
Arrange the 3rd pair-shift clutch 54 at second output shaft 50. Driving wheel 52,53 can be connected with second output shaft 50 by described the 3rd pair-shift clutch 54.Described driving wheel 52,53 is corresponding to the 5th forward gear V and the 6th forward gear VI.The driving wheel 52 of described forward gear V, VI, 53 makes their observe the driving wheel 33,34 that surrounds on first output shaft 30 at the axial direction of input shaft 10 in this so in the axial direction space.
In order to realize reverse gear, list-two gear gear shift sleeves are set, can be connected in relative rotation forming between driving wheel 51 and second output shaft 50 not have by described list-two gear gear shift sleeves.Driving wheel 31 engagements of described driving wheel 51 on this and first output shaft 30.Described driving wheel 31 is constructed to step shape gear at this, and this step shape gear has than small gear 31a with than gearwheel 31b.Described step shape gear 31 than small gear 31a in 51 engagements of this and driving wheel, than gearwheel 31b (than the diameter of gearwheel 31b greater than the diameter than small gear 31a) then with first input shaft 10 on fixed wheel 11 engagements.If the sliding sleeve 58 that hang now the first reverse gear R, that is to say list-gear gear shift sleeve moves right in the diagram of Fig. 1 or is positioned at its active position, namely driving wheel 51 is connected with second output shaft 50 on sense of rotation regularly.So the moment of torsion of input shaft 10 by fixed wheel 11 be delivered to step shape driving wheel 31 than on the gearwheel 31b.Make moment of torsion by arriving second output shaft 50 than small gear 31a by driving wheel 51 than small gear 31a with being connected in relative rotation than the nothing between the gearwheel 31b.Under the situation of hanging reverse gear R, the sliding sleeve 39 of first pair-gear shift clutch 35 is positioned at the neutral position, makes step shape driving wheel 31 can not have and is connected with first output shaft 30 with relatively rotating.
Moment of torsion is delivered on the ring wheel 70 by first output shaft 30 by the driver pinion 37 that nothing is connected with first output shaft 30 with relatively rotating.In addition, there be not second driver pinion 56 and described ring wheel 70 engagements that is arranged on second output shaft 50 with relatively rotating.In the embodiment as Fig. 1, the diameter of second driver pinion 56 is greater than the diameter of first driver pinion 37 on first output shaft 30.
Therefore, it seems from the end 16 of clutch side that aim at the axial position of each driving wheel, gear is following order: reverse gear R, forward gear I, II, V, III, IV, VI.In the present embodiment, each fixed wheel 11 to 15 only meshes with a driving wheel respectively.The fixed wheel that does not exist any while and two driving wheels directly to mesh.Therefore, between forward gear, there is not any relevance.In fact, because there is not indirect association in step shape gear 31 yet between the first forward gear I and reverse gear R.
Fig. 2 has schematically shown the drawing in side sectional elevation of the manual transmission among Fig. 1.Can see, the spin axis 17 of input shaft 10 and output shaft 30,50 spin axis 38,57 form a triangle, wherein, be connected the angle that straight line 3 holds into approximate 90 ° of sizes between the spin axis 57 that is connected straight line and spin axis 17 and second output shaft 50 between the spin axis 38 of the spin axis 17 of input shaft 10 and first output shaft 30.Can also see driver pinion 37,56 and around ring wheel 70 engagements of spin axis 71 rotation.
Fig. 2 shows the outer diameter D of sliding sleeve 58
58And the outer diameter D of driving wheel 31
31, the outer diameter than gearwheel 31b of step shape driving wheel 31 more precisely.Can see diameter D
31, D
58Intersect along the connection straight line 4 between output shaft 30,50 the spin axis 38,57.List-gear gear shift sleeve 55 and then correspondingly arrange in the dislocation of the axial direction of input shaft 10 than gearwheel 31b.As shown in Figure 1, compare the end 16 of first active position more close described clutch side on the axial direction of input shaft 10 of the sliding sleeve 39 of first pair-gear shift clutch 35 with the active position of the sliding sleeve 58 of list-gear gear shift sleeve 55.
The reference character table
1 manual transmission
2 connect straight line
3 connect straight line
4 connect straight line
10 input shafts
11 fixed wheels
12 fixed wheels
13 fixed wheels
14 fixed wheels
15 fixed wheels
17 spin axiss
30 first output shafts
31 driving wheels
31a is than small gear
31b is than gearwheel
32 driving wheels
33 driving wheels
34 driving wheels
35 pairs-gear shift clutch
36 pairs-gear shift clutch
37 first driver pinions
38 spin axiss
39 sliding sleeves
50 second output shafts
51 driving wheels
52 driving wheels
53 driving wheels
54 the 3rd pairs-the gear shift clutch
55 list-gear shift clutch
56 second driver pinions
57 spin axiss
70 ring wheels
71 spin axiss
Claims (11)
1. manual transmission (1) that is used for the traffic tool comprising:
Input shaft (10);
First output shaft (30) and second output shaft (50);
Do not have the fixed wheel be arranged on the described input shaft (10) with relatively rotating (10 ..., 16);
Be arranged in that described first output shaft (30) or second output shaft (50) are gone up and with described fixed wheel (10 ..., 16) driving wheel (31,32,33,34,51,52,53) of engagement;
Be used for making driving wheel (31,32,33,34,51,52,53) not have the gearshift that is connected with first output shaft (30) or second output shaft (50) with relatively rotating;
Forward gear (I ..., VI) and reverse gear (R), wherein, give each gear (I ..., VI, R) in the described driving wheel of configuration, when hanging corresponding gear, this driving wheel and first output shaft or second output shaft (30,50) do not have connection with relatively rotating;
Described gearshift has the first and second pairs-gear shift clutch (35 that is arranged on first output shaft (30), 36) and the 3rd pair-gear shift clutch (54) and the gear shift clutch that preferably is constructed to list-gear gear shift sleeve (55), described list-gear gear shift sleeve is arranged on second output shaft (50), and
Each fixed wheel (10 ..., 16) respectively only with a driving wheel (31,32,33,34,51,52, the 53) engagement of forward gear,
It is characterized in that,
The driving wheel (31) of first forward gear (I) and the engagement of the driving wheel (51) of reverse gear (R).
2. manual transmission according to claim 1 (1), it is characterized in that, the driving wheel (31) of described first forward gear (I) is constructed to have than small gear (31a) with than the step shape gear of gearwheel (31b), and is described than fixed wheel (11) engagement on gearwheel (31b) and the input shaft (10) and described than driving wheel (51) engagement of small gear (31a) with reverse gear (R).
3. manual transmission according to claim 1 and 2 (1), it is characterized in that the driving wheel (31) of first forward gear (1) and the driving wheel (32) of second forward gear (II) can be connected with first output shaft (30) nothing by first pair-gear shift clutch (35) with relatively rotating.
4. according to each described manual transmission (1) in the claim 1 to 3, it is characterized in that the driving wheel (33) of the 3rd forward gear (III) and the driving wheel (34) of the 4th forward gear (IV) can be connected with first output shaft (30) nothing by second pair-gear shift clutch (36) with relatively rotating.
5. according to each described manual transmission (1) in the claim 1 to 4, it is characterized in that the driving wheel (51) of described reverse gear (R) can be connected with second output shaft (50) nothing by gear shift clutch (55) with relatively rotating.
6. according to each described manual transmission (1) in the claim 1 to 5, it is characterized in that the driving wheel (52) of the 5th forward gear (V) and the driving wheel (53) of the 6th forward gear (VI) can be connected with second output shaft (50) nothing by the 3rd pair-gear shift clutch (54) with relatively rotating.
7. according to each described manual transmission (1) in the claim 1 to 6, it is characterized in that, one first driver pinion (37) nothing is arranged on first output shaft (30) with relatively rotating, one second driver pinion (56) nothing is arranged on second output shaft (50) with relatively rotating, first driver pinion and second driver pinion (37,56) have the diameter of different sizes and mesh with a ring wheel (70).
8. according to each described manual transmission (1) in the claim 2 to 7, it is characterized in that, described input shaft (10) has the end (16) of clutch side, axial direction at input shaft (10) is observed, the end (16) of the described clutch side that is disposed in input shaft (10) than small gear (31a) and described than between the gearwheel (31b).
9. according to each described manual transmission (1) in the claim 1 to 8, it is characterized in that, in the cross section of described manual transmission, observe, input shaft (10) and two output shafts (30,50) spin axis (17,38,57) form triangle, the spin axis (17 of the spin axis of input shaft (10) and first output shaft (30), angle (α) between the connection straight line (3) between the spin axis (17,57) of the connection straight line (2) 38) and the spin axis of input shaft (10) and second output shaft (50) is 90 ° substantially.
10. according to each described manual transmission (1) in the claim 1 to 9, it is characterized in that the outer diameter (D of the swivel sleeve (58) of gear shift clutch (55)
58) with the outer diameter (D of the driving wheel (31) of first forward gear (I)
31) summation greater than the twice of the spacing between the spin axis (57) of the spin axis (38) of first output shaft (30) and second output shaft (50).
11. manual transmission according to claim 10 (1), it is characterized in that, axial direction at input shaft (10) is observed, and the neutral position of the sliding sleeve (39) of first pair-gear shift clutch (35) is disposed between the end (16) of clutch side of the neutral position of sliding sleeve (58) of list-gear gear shift sleeve (55) and input shaft (10).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102011055610.9A DE102011055610B4 (en) | 2011-11-22 | 2011-11-22 | Manual transmission for vehicles |
| DE102011055610.9 | 2011-11-22 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103185110A true CN103185110A (en) | 2013-07-03 |
| CN103185110B CN103185110B (en) | 2017-04-05 |
Family
ID=48221789
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210599029.7A Active CN103185110B (en) | 2011-11-22 | 2012-11-21 | For the manual transmission of the vehicles |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN103185110B (en) |
| DE (1) | DE102011055610B4 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105202158A (en) * | 2014-06-23 | 2015-12-30 | 广州汽车集团股份有限公司 | Input shaft locating structure and manual transmission |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102013224742B4 (en) | 2013-12-03 | 2021-04-22 | Zf Friedrichshafen Ag | Spur gear for a motor vehicle |
| CN110360278A (en) * | 2019-08-14 | 2019-10-22 | 陈奇 | Space of tractor double engaging powers shift assemblies in parallel |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4116189A1 (en) * | 1990-05-25 | 1991-11-28 | Volkswagen Ag | Gearbox for transverse- engine car - incorporates two layshafts to give compact layout |
| DE19750593A1 (en) * | 1996-11-20 | 1998-05-28 | Volvo Ab | Automatic vehicle gear transmission |
| CN101082363A (en) * | 2006-05-30 | 2007-12-05 | 三菱自动车工业株式会社 | Double clutch transmission |
| CN101832369A (en) * | 2009-03-09 | 2010-09-15 | 格特拉克·福特传动系统有限公司 | Dual-clutch transmission |
| CN102230520A (en) * | 2011-07-21 | 2011-11-02 | 安徽江淮汽车股份有限公司 | Transmission device for manual shift transmission |
-
2011
- 2011-11-22 DE DE102011055610.9A patent/DE102011055610B4/en active Active
-
2012
- 2012-11-21 CN CN201210599029.7A patent/CN103185110B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4116189A1 (en) * | 1990-05-25 | 1991-11-28 | Volkswagen Ag | Gearbox for transverse- engine car - incorporates two layshafts to give compact layout |
| DE19750593A1 (en) * | 1996-11-20 | 1998-05-28 | Volvo Ab | Automatic vehicle gear transmission |
| CN101082363A (en) * | 2006-05-30 | 2007-12-05 | 三菱自动车工业株式会社 | Double clutch transmission |
| CN101832369A (en) * | 2009-03-09 | 2010-09-15 | 格特拉克·福特传动系统有限公司 | Dual-clutch transmission |
| CN102230520A (en) * | 2011-07-21 | 2011-11-02 | 安徽江淮汽车股份有限公司 | Transmission device for manual shift transmission |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105202158A (en) * | 2014-06-23 | 2015-12-30 | 广州汽车集团股份有限公司 | Input shaft locating structure and manual transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102011055610A1 (en) | 2013-05-23 |
| CN103185110B (en) | 2017-04-05 |
| DE102011055610B4 (en) | 2018-06-21 |
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