CN202188084U - 6AT transmission - Google Patents
6AT transmission Download PDFInfo
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- CN202188084U CN202188084U CN2011202281571U CN201120228157U CN202188084U CN 202188084 U CN202188084 U CN 202188084U CN 2011202281571 U CN2011202281571 U CN 2011202281571U CN 201120228157 U CN201120228157 U CN 201120228157U CN 202188084 U CN202188084 U CN 202188084U
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 20
- 230000007246 mechanism Effects 0.000 claims abstract description 69
- 239000012530 fluid Substances 0.000 claims description 20
- 230000009471 action Effects 0.000 description 8
- 230000000694 effects Effects 0.000 description 4
- 230000009347 mechanical transmission Effects 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008450 motivation Effects 0.000 description 1
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Abstract
The utility model discloses a 6AT derailleur, it includes one set of ravigneaux planetary gear mechanism and one set of single row planetary gear mechanism, and wherein the ring gear output of ravigneaux planetary gear mechanism meets with the input of single row planetary gear mechanism ring gear, and single row planetary gear mechanism's planet carrier does have six and go forward the output device who keeps off an automatic gearbox that reverses gear. The utility model discloses an increase a single planetary gear mechanism on the basis of ravigneaux planetary gear mechanism, realize more fender position and wider transmission ratio scope, come the dynamic characteristic of full play engine to compact smooth transmission ratio links up the improvement that the proportion realized whole car dynamic nature and shift the travelling comfort more. The utility model discloses be fit for assembling before the engine on horizontal forerunner's vehicle for keep off the position speed governing more.
Description
Technical field
The utility model relates to a kind of vehicle arrangements for speed regulation, and specifically a kind of have a 6AT speed changer that six forward gears one reverse gear.
Background technique
The car that has automatic transmission for a long time is regarded as senior and luxurious sign always, and the general motor of discharge capacity more than 2.0L just considers to be equipped with the AT speed changer.Domestic AT starts late, and at the little moment of torsion 4 fast AT that are mostly of initial period exploitation, being used for discharge capacity is 1.6-1.8L natural aspiration and 1.4-1.6 turbosupercharging vehicle.In the independent brand, the 6AT of the many gears of high pulling torque is still waiting exploitation at home.
Existing La Weina 4AT mechanical transmission structure has that structure is compact, outside dimensions is little, in light weight, be easy to car load and carry advantages such as coupling; But can not realize wideer gear range and smooth more gear shift acceleration performance requirement; After mating with engine whole vehicle; Can't make full use of the dynamic property of motor, also there are obvious deficiency in car load power character and comfort level.
The model utility content
The technical problem that the utility model will solve; Provide a kind of 6AT speed changer that six forward gears one reverse gear that has; It is on the basis of La Weina mechanical transmission mechanism, to increase a single planetary mechanism; Realize more gear and the gear range of more widening, give full play to the dynamic property of motor, realize the raising of car load power character and shifting comfort with compact more smooth velocity ratio linking ratio.
For solving the problems of the technologies described above, the technological scheme that the utility model is taked is:
A kind of 6AT speed changer, it comprises a cover ravigneaux planetary gear mechanism and a cover simple planetary arrangement, wherein the planet carrier of simple planetary arrangement links to each other with transformer turbine, as the input of transmission assembly; The gear ring of single planetary mechanism is as the input of La Weina planetary mechanism; The gear ring of La Weina planetary mechanism drives the output of countershaft-gear as transmission assembly.
As specializing of the utility model structure, said 6AT speed changer comprises that motivation passes through fluid torque converter, simple planetary arrangement, ravigneaux planetary gear mechanism, output differential that flywheel directly drives, wherein:
The turbine of fluid torque converter links to each other with input shaft through spline; Input shaft directly drives the planet carrier of simple planetary arrangement; And planet carrier links to each other with the sun gear of simple planetary arrangement through the C4 clutch, and sun gear links to each other with case of transmission through the B3 break again; The gear ring of simple planetary arrangement links to each other with the input shaft of ravigneaux planetary gear mechanism, and the input shaft of ravigneaux planetary gear mechanism links to each other with the planet carrier of ravigneaux planetary gear mechanism, links to each other with the small sun gear of ravigneaux planetary gear mechanism, links to each other with the big sun gear of ravigneaux planetary gear mechanism through the C3 clutch through the C2 clutch through the C1 clutch; Meanwhile, planet carrier through overrunning clutch is connected with housing side by side with the B1 break, greatly sun gear leads to the B2 break and is connected with housing; The gear ring of ravigneaux planetary gear mechanism is through the gear engagement on output gear and the jack shaft; Jack shaft links to each other with differential mechanism through gear engagement.
The utility model respectively to keep off power transmission process following:
[one grade]
C2 clutch, B3 brake engages, overrunning clutch works simultaneously.
Power is delivered on the input shaft via fluid torque converter; Through the joint of B3 break, power is input to ravigneaux planetary gear mechanism via single planetary system gear ring, passes to small sun gear to power through the C2 clutch that engages; Because the locking effect of overrunning clutch; Through short planet wheel, long planet wheel, the gear ring of La Weina planetary system, the gear engagement on output gear and the jack shaft outputs to differential assembly to power at last successively.
[second gear]
C2, C4 clutch, overrunning clutch works simultaneously.
Power is delivered on the input shaft by fluid torque converter; Through the joint of B3 break, power is input to ravigneaux planetary gear mechanism via single planetary system gear ring, passes to small sun gear to power through the C2 clutch that engages; Because the locking effect of overrunning clutch; Through short planet wheel, long planet wheel, the gear ring of La Weina planetary system, the gear engagement on output gear and the jack shaft outputs to differential assembly to power at last successively.
[third gear]
C2 clutch, B2 break, B3 brake engages.
Power is delivered on the input shaft by fluid torque converter, and through the joint of B3 break, power is input to ravigneaux planetary gear mechanism via single planetary system gear ring; C2 clutch through engaging is passed to small sun gear to power; Because the braking action of B2 break, big sun gear locking, power pass through common carrier, length planet wheel, the gear ring of La Weina planetary system successively; Gear engagement on output gear and the jack shaft outputs to differential assembly at last.
[fourth gear]
Clutch C1, C2, break B3 engage.
Power is delivered on the input shaft by fluid torque converter; Joint through the B3 break; Power is input to the La Weina planetary mechanism via single planetary system gear ring, and through the C1, the C2 clutch that engage, input shaft power directly directly outputs to output gear through the La Weina planetary system of whole locking; Gear engagement on output gear and the jack shaft outputs to differential assembly at last.
[five grades]
C1 clutch, B2 and B3 brake engages.
Power is delivered on the input shaft by fluid torque converter, and through the joint of B3 break, power is input to ravigneaux planetary gear mechanism via single planetary system gear ring; C1 clutch through engaging is passed to common carrier to power; Because the braking action of B2 break, big sun gear locking, power pass through common carrier, long planet wheel, the gear ring of La Weina planetary system successively; Gear engagement on output gear and the jack shaft outputs to differential assembly at last.
[six grades]
C1, C4 clutch, B2 brake engages simultaneously.
Transmission of power arrives input shaft via fluid torque converter; C1 clutch through engaging is passed to common carrier to power, since the braking action of B2 break, big sun gear locking; Power passes through common carrier, long planet wheel, the gear ring of La Weina planetary system successively; The engagement of the gear ring external gear of output gear and single planetary system, through the joint of C4 clutch, power outputs to differential assembly after via single planetary system.
[reverse gear]
C1 and C4 clutch, B2 brake engages.
Power is delivered on the input shaft via fluid torque converter, and through the joint of C4 clutch, power is input to the La Weina planetary mechanism via single planetary system gear ring; C1 passes to common carrier to power through oncoming clutch; Because the braking action of B2 break, big sun gear locking, power pass through common carrier, long planet wheel, the gear ring of La Weina planetary system successively; Gear engagement on output gear and the jack shaft outputs to differential assembly at last.
Owing to adopted above-mentioned technological scheme; The utility model compared with prior art; Institute's acquisition of technology progress is: on the basis of La Weina mechanical transmission mechanism, increase a single planetary mechanism; Thereby realizing having has the purpose that six forward gears and reverse gear; The gear range that makes the automatic transmission that is provided have more gear and more widen is given full play to the dynamic property of motor, realizes the raising of car load power character and shifting comfort with compact more smooth velocity ratio linking ratio.The utility model is fit to be assemblied on horizontal forerunner's before the motor the vehicle, is used for the speed governing of many gears.
The utility model below will combine Figure of description and specific embodiment to do further explain.
Description of drawings
Fig. 1 is the utility model embodiment's an overall structure schematic representation;
The schematic representation of the radial position relationship during Fig. 2 is embodiment illustrated in fig. 1 between input shaft, jack shaft, differential mechanism.
Among the figure: 2-input shaft, 3-jack shaft, 4-turbine, 7～10-C1～C4 clutch; 11～13-B1～B3 break, 14-overrunning clutch, 15-small sun gear, 16-big sun gear; 17-short planet wheel, 18-long planet wheel, 19-gear ring; 20-output gear, 21-single planetary row, 22-differential mechanism.
Embodiment
Embodiment
Shown in Figure 1 is a kind of 6AT speed changer, and it comprises a cover ravigneaux planetary gear mechanism and a cover single planetary row 21, and wherein the planet carrier of single planetary row 21 mechanisms links to each other with transformer turbine 4, as the input of transmission assembly; The gear ring of single planetary row 21 mechanisms is as the input of La Weina planetary mechanism; The gear ring of ravigneaux planetary gear mechanism drives the output of countershaft-gear as transmission assembly.Particularly:
This automatic transmission comprises that motor passes through the direct fluid torque converter that drives of flywheel, single planetary row 21, ravigneaux planetary gear mechanism, output differential 22 etc.
The turbine 5 of fluid torque converter links to each other with input shaft 2 through spline; Input shaft 2 directly drives the planet carrier of single planetary row 21; And planet carrier links to each other with the sun gear of single planetary row 21 through C4 clutch 10, and sun gear links to each other with case of transmission through B3 break 13 again; The gear ring of single planetary row 21 links to each other with the input shaft 2 of ravigneaux planetary gear mechanism, and the input shaft 2 of La Weina planetary mechanism links to each other with the planet carrier of ravigneaux planetary gear mechanism, links to each other with the small sun gear 15 of ravigneaux planetary gear mechanism, links to each other with the big sun gear 16 of La Weina mechanism through C3 clutch 9 through C2 clutch 8 through C1 clutch 7; Meanwhile, planet carrier through overrunning clutch 14 is connected with housing side by side with B1 break 11, greatly sun gear 16 passes through B2 break 12 and is connected with housing; The gear ring 19 of ravigneaux planetary gear mechanism is through the gear engagement on output gear 20 and the jack shaft 3; Jack shaft 3 links to each other with differential mechanism 22 through gear engagement.
The utility model respectively to keep off power transmission process following:
[one grade]
Power is delivered on the input shaft 2 via fluid torque converter; Through the joint of B3 break 13, power is input to ravigneaux planetary gear mechanism via the gear ring of single planetary row 21, passes to small sun gear 15 to power through the C2 clutch 8 that engages; Because the locking effect of overrunning clutch 14; Through short planet wheel 17, long planet wheel 18, the gear ring 19 of La Weina planetary system, the gear engagement on output gear 20 and the jack shaft 3 outputs to differential mechanism 22 to power at last successively.
[second gear]
Power is delivered on the input shaft 2 by fluid torque converter; Through the joint of B3 break 13, power is input to ravigneaux planetary gear mechanism via the gear ring of single planetary row 21, passes to small sun gear 15 to power through the C2 clutch 8 that engages; Because the locking effect of overrunning clutch 14; Through short planet wheel 17, long planet wheel 18, the gear ring 19 of La Weina planetary system, the gear engagement on output gear 20 and the jack shaft 3 outputs to differential mechanism 22 to power at last successively.
[third gear]
Power is delivered on the input shaft 2 by fluid torque converter, and through the joint of break 13, power is input to the La Weina planetary mechanism via the gear ring of single planetary row 21; C2 clutch 8 through engaging is passed to small sun gear 15 to power; Because the braking action of B2 break 12, big sun gear 16 lockings, power pass through common carrier, length planet wheel 17 and 18, the gear ring 19 of La Weina planetary system successively; Gear engagement on output gear 20 and the jack shaft 3 outputs to differential mechanism 22 at last.
[fourth gear]
C1 clutch 7 engages with C2 clutch 8, B3 break 13.
Power is delivered on the input shaft 2 by fluid torque converter; Joint through B3 break 13; Power is input to ravigneaux planetary gear mechanism via the gear ring of single planetary row 21, and through the C1 clutch 7 and the C2 clutch 8 that engage, the power of input shaft 2 directly directly outputs to output gear 20 through the La Weina planetary system of whole locking; Gear engagement on output gear 20 and the jack shaft 3 outputs to differential mechanism 22 at last.
[five grades]
C1 clutch 7, B2 break 12 engage with B3 break 13.
Power is delivered on the input shaft 2 by fluid torque converter, and through the joint of B3 break 13, power is input to ravigneaux planetary gear mechanism via the gear ring of single planetary row 21; Pass to common carrier to power through the C1 clutch that engages 7; Because the braking action of B2 break 12, big sun gear 16 lockings, power pass through common carrier, long planet wheel 18, the gear ring 19 of La Weina planetary system successively; Gear engagement on output gear 20 and the jack shaft 3 outputs to differential mechanism 22 at last.
[six grades]
C1 clutch 7 engages with C4 clutch 10, B2 break 12.
Transmission of power arrives input shaft 2 via fluid torque converter; Close device 7 from C1 and pass to common carrier to power through what engage, since the braking action of B2 break 12, big sun gear 16 lockings; Power passes through common carrier, long planet wheel 18, the gear ring 19 of La Weina planetary system successively; The gear ring external gear engagement of output gear 20 and single planetary row 21, through the joint of C4 clutch 10, power outputs to differential mechanism 22 after via single planetary row 21.
[reverse gear]
Power is delivered on the input shaft 2 via fluid torque converter, and through the joint of C4 clutch 10, power is input to ravigneaux planetary gear mechanism via the gear ring of single planetary row 21; Pass to common carrier to power through the C1 clutch that engages 7; Because the braking action of B2 break 12, big sun gear 16 lockings, power pass through common carrier, long planet wheel 18, the gear ring 19 of La Weina planetary system successively; Gear engagement on output gear 20 and the jack shaft 3 outputs to differential mechanism 22 at last.
Claims (2)
1. 6AT speed changer,
It is characterized in that:It comprises a cover ravigneaux planetary gear mechanism and a cover simple planetary arrangement, and wherein the planet carrier of simple planetary arrangement links to each other with transformer turbine, as the input of transmission assembly; The gear ring of single planetary mechanism is as the input of La Weina planetary mechanism; The gear ring of La Weina planetary mechanism drives the output of countershaft-gear as transmission assembly.
2. 6AT speed changer according to claim 1,
It is characterized in that:Said have the automatic transmission that six forward gears one reverse gear and comprise that motor passes through fluid torque converter, simple planetary arrangement, ravigneaux planetary gear mechanism, output differential that flywheel directly drives, wherein:
The turbine of fluid torque converter links to each other with input shaft through spline; Input shaft directly drives the planet carrier of simple planetary arrangement; And planet carrier links to each other with the sun gear of simple planetary arrangement through the C4 clutch, and sun gear links to each other with case of transmission through the B3 break again; The gear ring of simple planetary arrangement links to each other with the input shaft of ravigneaux planetary gear mechanism, and the input shaft of ravigneaux planetary gear mechanism links to each other with the planet carrier of ravigneaux planetary gear mechanism, links to each other with the small sun gear of ravigneaux planetary gear mechanism, links to each other with the big sun gear of ravigneaux planetary gear mechanism through the C3 clutch through the C2 clutch through the C1 clutch; Meanwhile, planet carrier through overrunning clutch is connected with housing side by side with the B1 break, greatly sun gear leads to the B2 break and is connected with housing; The gear ring of ravigneaux planetary gear mechanism is through the gear engagement on output gear and the jack shaft; Jack shaft links to each other with differential mechanism through gear engagement.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011202281571U CN202188084U (en) | 2011-06-30 | 2011-06-30 | 6AT transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011202281571U CN202188084U (en) | 2011-06-30 | 2011-06-30 | 6AT transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202188084U true CN202188084U (en) | 2012-04-11 |
Family
ID=45919536
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011202281571U Expired - Fee Related CN202188084U (en) | 2011-06-30 | 2011-06-30 | 6AT transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202188084U (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102808906A (en) * | 2012-08-17 | 2012-12-05 | 长城汽车股份有限公司 | Automatic transmission and motor vehicle |
| CN102927222A (en) * | 2012-10-29 | 2013-02-13 | 长城汽车股份有限公司 | Automatic transmission |
| CN103291863A (en) * | 2013-06-27 | 2013-09-11 | 长城汽车股份有限公司 | Automatic transmission and vehicles with same |
| CN103453104A (en) * | 2013-07-22 | 2013-12-18 | 北京理工大学 | Four-segment hydraulic mechanical composite transmission device |
| CN103195886B (en) * | 2013-03-28 | 2015-09-09 | 长城汽车股份有限公司 | Automobile and speed changer thereof |
| CN108167415A (en) * | 2018-01-16 | 2018-06-15 | 吉孚汽车技术(浙江)有限公司 | Automatic transmission |
-
2011
- 2011-06-30 CN CN2011202281571U patent/CN202188084U/en not_active Expired - Fee Related
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102808906A (en) * | 2012-08-17 | 2012-12-05 | 长城汽车股份有限公司 | Automatic transmission and motor vehicle |
| CN102808906B (en) * | 2012-08-17 | 2016-06-08 | 长城汽车股份有限公司 | A kind of automatic transmission and motor vehicles |
| CN102927222A (en) * | 2012-10-29 | 2013-02-13 | 长城汽车股份有限公司 | Automatic transmission |
| CN102927222B (en) * | 2012-10-29 | 2016-01-06 | 长城汽车股份有限公司 | Automatic transmission |
| CN103195886B (en) * | 2013-03-28 | 2015-09-09 | 长城汽车股份有限公司 | Automobile and speed changer thereof |
| CN103291863A (en) * | 2013-06-27 | 2013-09-11 | 长城汽车股份有限公司 | Automatic transmission and vehicles with same |
| CN103291863B (en) * | 2013-06-27 | 2016-04-13 | 长城汽车股份有限公司 | Automatic transmission and there is the vehicle of this automatic transmission |
| CN103453104A (en) * | 2013-07-22 | 2013-12-18 | 北京理工大学 | Four-segment hydraulic mechanical composite transmission device |
| CN103453104B (en) * | 2013-07-22 | 2015-12-02 | 北京理工大学 | Four-segment hydraulic mechanical composite transmission device |
| CN108167415A (en) * | 2018-01-16 | 2018-06-15 | 吉孚汽车技术(浙江)有限公司 | Automatic transmission |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20120411 Termination date: 20170630 |