CN202165536U - Automatic transmission with six forward gears and reverse gear - Google Patents
Automatic transmission with six forward gears and reverse gear Download PDFInfo
- Publication number
- CN202165536U CN202165536U CN2011202281603U CN201120228160U CN202165536U CN 202165536 U CN202165536 U CN 202165536U CN 2011202281603 U CN2011202281603 U CN 2011202281603U CN 201120228160 U CN201120228160 U CN 201120228160U CN 202165536 U CN202165536 U CN 202165536U
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Abstract
The utility model discloses an automatic transmission with six forward gears and a reverse gear, which comprises a set of Ravigneaux planet gear mechanism and a set of single row planet gear mechanism, wherein a gear ring output end of the Ravigneaux planet gear mechanism is connected with a gear ring input end of the single row planet gear mechanism, and a planet carrier of the single row planet gear mechanism is an output device of the automatic transmission with six forward gears and the reverse gear. A single row planet gear mechanism is added based on the Ravigneaux planet gear mechanism, and more gears and wider transmission ranges are achieved so that power characteristics of an engine are fully expressed, and dynamic property and gear shift comfortableness of a whole car are improved by means of compacter and smoother transmission ratio cohesion proportion. The automatic transmission with six forward gears and the reverse gear is suitable for being assembled on forward driving vehicles with a transverse and front motor and used for multi-gear speed regulation.
Description
Technical field
The utility model relates to a kind of vehicle arrangements for speed regulation, and specifically a kind of have an automatic transmission 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 have compact structure, outside dimensions 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 gearshift 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 automatic transmission 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 have an automatic transmission that six forward gears one reverse gear; It comprises a cover ravigneaux planetary gear mechanism and a cover simple planetary arrangement; Wherein the input end of the gear ring output terminal of La Weina planetary mechanism and simple planetary arrangement gear ring joins, and the planet carrier of simple planetary arrangement is said output unit with automatic transmission that six forward gears one reverse gear.
As specializing of the utility model structure, said have the automatic transmission that six forward gears one reverse gear and comprise that motor passes through fluid torque converter, La Weina planetary mechanism, simple planetary arrangement, output differential that flywheel directly drives, particularly:
The turbine of fluid torque converter links to each other with input shaft through spline; Input shaft links to each other with the planet carrier of La Weina planetary mechanism, links to each other with the small sun gear of La Weina mechanism, links to each other with the big sun gear of La Weina planetary mechanism through clutch through clutch C2 through clutch C1; Meanwhile, planet carrier through overrunning clutch is connected with housing side by side with break B1, greatly sun gear passes through break B2 and is connected with housing; The gear ring of La Weina planetary mechanism is connected with simple planetary arrangement through output gear; The gear ring of simple planetary arrangement links to each other with the sun gear of simple planetary arrangement through clutch C4; The sun gear of simple planetary arrangement links to each other with case of transmission through break B3 again, and the planet carrier of simple planetary arrangement links to each other with differential mechanism through gear as jack shaft.
The utility model respectively to keep off power transmission process following:
[retaining]
Clutch C2, break B3 engage, and overrunning clutch works simultaneously.
Power arrives input shaft via fluid torque converter; C2 passes to small sun gear to power through oncoming clutch; Because through short planet wheel, long planet wheel, the gear ring of La Weina planetary system, the gear ring external gear of output gear and simple planetary arrangement meshes successively for the locking effect of overrunning clutch, power; Through the joint of B3, power outputs to differential assembly after via single planetary system.
[two retainings]
Clutch C2, C4 engage, and overrunning clutch works simultaneously.
Power arrives input shaft via fluid torque converter; C2 passes to small sun gear to power through oncoming clutch; Because through short planet wheel, long planet wheel, the gear ring of La Weina planetary system, the gear ring external gear of output gear and single planetary system meshes successively for the locking effect of overrunning clutch, power; Through the joint of C4, power outputs to differential assembly after via single planetary system.
[three retainings]
Clutch C2, break B2 engage with B3.
Power arrives input shaft via fluid torque converter; C2 passes to small sun gear to power through oncoming clutch, since the braking action of break B2, big sun gear locking; Power passes through common carrier, length 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, power outputs to differential assembly after via single planetary system.
[four retainings]
Clutch C1 engages with C2, break B3.
Power arrives input shaft via fluid torque converter; Through oncoming clutch C1, C2; Input shaft power directly outputs to output gear through the La Weina planetary system of integral body; The engagement of the gear ring external gear of output gear and single planetary system and since the joint locking of B3 the sun gear of single planetary system, power outputs to differential assembly after via single planetary system.
[five retainings]
Clutch C1, break B2 engage with B3.
This moment, the transmission of power of speed changer arrived input shaft via fluid torque converter; C1 passes to common carrier to power through oncoming clutch, since the braking action of break B2, 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 B3, power outputs to differential assembly after via single planetary system.
[six retainings]
Clutch C1 engages with C4, break B2.
Power arrives input shaft via fluid torque converter; C1 passes to common carrier to power through oncoming clutch, since the braking action of break B2, 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, power outputs to differential assembly after via single planetary system.
[reversing gear]
Clutch C3, break B1 engage with B3.
Power arrives input shaft via fluid torque converter; Pass to big sun gear to power through oncoming clutch C3; Because through big sun gear, long planet wheel, the gear ring of La Weina planetary system, the gear ring external gear of output gear and single planetary system meshes successively for the locking effect of break B1, power; Through the joint of B3, power outputs to differential assembly after via single planetary system.
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-simple planetary arrangement, 22-differential mechanism.
Embodiment
Embodiment
Shown in Figure 1 is a kind of automatic transmission that six forward gears one reverse gear that has; It comprises a cover ravigneaux planetary gear mechanism and a cover single planetary row 21; Wherein the input end of the gear ring output terminal of La Weina planetary mechanism and simple planetary arrangement 21 gear rings joins, and the planet carrier of simple planetary arrangement 21 is the output unit of this automatic transmission.Particularly:
This automatic transmission comprises that motor passes through the direct fluid torque converter that drives of flywheel, ravigneaux planetary gear mechanism, simple planetary arrangement 21, output differential 22 etc.
The turbine 5 of fluid torque converter links to each other with input shaft 2 through spline; Input shaft 2 links to each other with the planet carrier of La Weina planetary mechanism, links to each other with the small sun gear 15 of La Weina planetary mechanism, links to each other with the big sun gear 16 of La Weina planetary 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 La Weina planetary mechanism is connected with simple planetary arrangement 21 through output gear 20; The gear ring of simple planetary arrangement 21 links to each other with the sun gear of simple planetary arrangement 21 through C4 clutch 10; The sun gear of simple planetary arrangement links to each other with case of transmission through B3 break 13 again, and the planet carrier of simple planetary arrangement links to each other with differential mechanism 22 through gear as jack shaft 3.
The utility model respectively to keep off power transmission process following:
[retaining]
C2 clutch 8, B3 break 13 engage, and overrunning clutch 14 works simultaneously.
Power arrives input shaft 2 via fluid torque converter; C2 clutch 8 through engaging is passed to small sun gear 15 to power; Because through short planet wheel 17, long planet wheel 18, the gear ring of La Weina planetary system, output gear 20 meshes with the gear ring external gear of simple planetary arrangement 21 successively for the locking effect of overrunning clutch 14, power; Through the joint of B3 break 13, power outputs to differential mechanism 22 assemblies after via simple planetary arrangement 21.
[two retainings]
C2 clutch 8 all engages with C4 clutch 10, and overrunning clutch 14 works simultaneously.
Power arrives input shaft 2 via fluid torque converter; C2 clutch 8 through engaging is passed to small sun gear 15 to power; Because through short planet wheel 17, long planet wheel 18, the gear ring of La Weina planetary system, output gear 20 meshes with the gear ring external gear of simple planetary arrangement 21 successively for the locking effect of overrunning clutch 14, power; Through the joint of C4 clutch 10, power outputs to differential mechanism 22 assemblies after via simple planetary arrangement 21.
[three retainings]
C2 clutch 8 engages with B2 break 12, B3 break 13.
Power arrives input shaft 2 via fluid torque converter; C2 clutch 8 through engaging is passed to small sun gear 15 to power, since the braking action of B2 break 12, big sun gear 16 lockings; Power passes through common carrier, length planet wheel 17 and 18, the gear ring of La Weina planetary system successively; The gear ring external gear engagement of output gear 20 and simple planetary arrangement 21, through the joint of C4 clutch 10, power outputs to differential mechanism 22 assemblies after via simple planetary arrangement 21.
[four retainings]
C1 clutch 7, C2 clutch 8, B3 break 13 engage.
Power arrives input shaft 2 via fluid torque converter; Through the C1 clutch 7 and C2 clutch 8 that engages; Input shaft 2 power directly output to output gear 20 through the La Weina planetary system of integral body; The gear ring external gear engagement of output gear 20 and simple planetary arrangement 21 and since the joint locking of B3 break 13 sun gear of simple planetary arrangement 21, power outputs to differential mechanism 22 assemblies after via simple planetary arrangement 21.
[five retainings]
C1 clutch 7, B2 break 12, B3 break 13 engage.
Power arrives input shaft 2 via fluid torque converter; Pass to common carrier to power through the C1 clutch that engages 7, 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 of La Weina planetary system successively; The gear ring external gear engagement of output gear 20 and simple planetary arrangement 21, through the joint of B3 break 13, power outputs to differential mechanism 22 assemblies after via simple planetary arrangement 21.
[six retainings]
C1 clutch 7 engages with C4 clutch 10, B2 break 12.
Power arrives input shaft 2 via fluid torque converter; Pass to common carrier to power through the C1 clutch that engages 7, 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 of La Weina planetary system successively; The gear ring external gear engagement of output gear 20 and simple planetary arrangement 21, through the joint of C4 clutch 10, power outputs to differential mechanism 22 assemblies after via simple planetary arrangement 21.
[reversing gear]
C3 clutch 9, B1 break 11, B3 clutch 13 engage.
Power arrives input shaft 2 via fluid torque converter; Pass to big sun gear 16 to power through oncoming clutch 9; Because through big sun gear 16, long planet wheel 18, the gear ring of La Weina planetary system, output gear 20 meshes with the gear ring external gear of simple planetary arrangement 21 successively for the locking effect of B1 break 11, power; Through the joint of B3 break 13, power outputs to differential mechanism 22 assemblies after via simple planetary arrangement 21.
Claims (2)
1. one kind has the automatic transmission that six forward gears one reverse gear; It is characterized in that: it comprises a cover ravigneaux planetary gear mechanism and a cover simple planetary arrangement; Wherein the input end of the gear ring output terminal of La Weina planetary mechanism and single planetary mechanism gear ring joins, and the planet carrier of simple planetary arrangement is said output unit with automatic transmission that six forward gears one reverse gear.
2. according to claim 1 have an automatic transmission that six forward gears one reverse gear; It is characterized in that: said have the automatic transmission that six forward gears one reverse gear and comprise fluid torque converter, ravigneaux planetary gear mechanism, simple planetary arrangement, output differential, wherein:
The turbine of fluid torque converter links to each other with input shaft through spline;
Input shaft links to each other with the planet carrier of La Weina planetary mechanism through clutch C1;
Input shaft links to each other with the small sun gear of La Weina planetary mechanism through clutch C2;
Input shaft links to each other with the big sun gear of La Weina planetary mechanism through clutch C3, and meanwhile, planet carrier is connected with housing with break B1 through overrunning clutch side by side;
Big sun gear is connected with housing through break B2; The gear ring of La Weina planetary mechanism is connected with simple planetary arrangement through output gear;
The gear ring of simple planetary arrangement links to each other with the sun gear of single planetary mechanism through clutch C4;
The sun gear of simple planetary arrangement links to each other with case of transmission through break B3 again;
The planet carrier of simple planetary arrangement links to each other with differential mechanism through gear as jack shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011202281603U CN202165536U (en) | 2011-06-30 | 2011-06-30 | Automatic transmission with six forward gears and reverse gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011202281603U CN202165536U (en) | 2011-06-30 | 2011-06-30 | Automatic transmission with six forward gears and reverse gear |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202165536U true CN202165536U (en) | 2012-03-14 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011202281603U Expired - Fee Related CN202165536U (en) | 2011-06-30 | 2011-06-30 | Automatic transmission with six forward gears and reverse gear |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202165536U (en) |
Cited By (21)
| 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 |
| CN102878259A (en) * | 2012-09-28 | 2013-01-16 | 长城汽车股份有限公司 | Multispeed automatic transmission and power assembly |
| CN102913598A (en) * | 2012-10-30 | 2013-02-06 | 顺德职业技术学院 | Planetary gear type manual transmission |
| CN102927221A (en) * | 2012-10-31 | 2013-02-13 | 长城汽车股份有限公司 | Automatic transmission and vehicle applying same |
| CN102927222A (en) * | 2012-10-29 | 2013-02-13 | 长城汽车股份有限公司 | Automatic transmission |
| CN103148182A (en) * | 2013-03-28 | 2013-06-12 | 长城汽车股份有限公司 | Automobile and speed changer thereof |
| CN104769326A (en) * | 2012-09-07 | 2015-07-08 | 德纳有限公司 | Ball type CVT including a direct drive mode |
| CN103195886B (en) * | 2013-03-28 | 2015-09-09 | 长城汽车股份有限公司 | Automobile and speed changer thereof |
| CN104936808A (en) * | 2012-10-22 | 2015-09-23 | Avl里斯脱有限公司 | Transmission and a method for operating same |
| US9556941B2 (en) | 2012-09-06 | 2017-01-31 | Dana Limited | Transmission having a continuously or infinitely variable variator drive |
| US9556943B2 (en) | 2012-09-07 | 2017-01-31 | Dana Limited | IVT based on a ball-type CVP including powersplit paths |
| US9599204B2 (en) | 2012-09-07 | 2017-03-21 | Dana Limited | Ball type CVT with output coupled powerpaths |
| US9638301B2 (en) | 2013-03-14 | 2017-05-02 | Dana Limited | Ball type continuously variable transmission |
| US9644530B2 (en) | 2013-02-08 | 2017-05-09 | Dana Limited | Internal combustion engine coupled turbocharger with an infinitely variable transmission |
| US9689477B2 (en) | 2012-09-07 | 2017-06-27 | Dana Limited | Ball type continuously variable transmission/infinitely variable transmission |
| US9777815B2 (en) | 2013-06-06 | 2017-10-03 | Dana Limited | 3-mode front wheel drive and rear wheel drive continuously variable planetary transmission |
| CN108167415A (en) * | 2018-01-16 | 2018-06-15 | 吉孚汽车技术(浙江)有限公司 | Automatic transmission |
| US10030751B2 (en) | 2013-11-18 | 2018-07-24 | Dana Limited | Infinite variable transmission with planetary gear set |
| US10030748B2 (en) | 2012-11-17 | 2018-07-24 | Dana Limited | Continuously variable transmission |
| US10030594B2 (en) | 2015-09-18 | 2018-07-24 | Dana Limited | Abuse mode torque limiting control method for a ball-type continuously variable transmission |
| US10088022B2 (en) | 2013-11-18 | 2018-10-02 | Dana Limited | Torque peak detection and control mechanism for a CVP |
-
2011
- 2011-06-30 CN CN2011202281603U patent/CN202165536U/en not_active Expired - Fee Related
Cited By (33)
| 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 |
| US9556941B2 (en) | 2012-09-06 | 2017-01-31 | Dana Limited | Transmission having a continuously or infinitely variable variator drive |
| US9689477B2 (en) | 2012-09-07 | 2017-06-27 | Dana Limited | Ball type continuously variable transmission/infinitely variable transmission |
| US9638296B2 (en) | 2012-09-07 | 2017-05-02 | Dana Limited | Ball type CVT including a direct drive mode |
| US10088026B2 (en) | 2012-09-07 | 2018-10-02 | Dana Limited | Ball type CVT with output coupled powerpaths |
| CN104769326B (en) * | 2012-09-07 | 2017-04-19 | 德纳有限公司 | Ball type CVT including a direct drive mode |
| CN104769326A (en) * | 2012-09-07 | 2015-07-08 | 德纳有限公司 | Ball type CVT including a direct drive mode |
| US10006527B2 (en) | 2012-09-07 | 2018-06-26 | Dana Limited | Ball type continuously variable transmission/infinitely variable transmission |
| US9599204B2 (en) | 2012-09-07 | 2017-03-21 | Dana Limited | Ball type CVT with output coupled powerpaths |
| US9556943B2 (en) | 2012-09-07 | 2017-01-31 | Dana Limited | IVT based on a ball-type CVP including powersplit paths |
| CN102878259B (en) * | 2012-09-28 | 2015-11-11 | 长城汽车股份有限公司 | A kind of many gears automatic transmission and power assembly |
| CN102878259A (en) * | 2012-09-28 | 2013-01-16 | 长城汽车股份有限公司 | Multispeed automatic transmission and power assembly |
| CN104936808A (en) * | 2012-10-22 | 2015-09-23 | Avl里斯脱有限公司 | Transmission and a method for operating same |
| CN104936808B (en) * | 2012-10-22 | 2018-01-23 | Avl里斯脱有限公司 | Speed changer and the method for operating the speed changer |
| CN102927222B (en) * | 2012-10-29 | 2016-01-06 | 长城汽车股份有限公司 | Automatic transmission |
| CN102927222A (en) * | 2012-10-29 | 2013-02-13 | 长城汽车股份有限公司 | Automatic transmission |
| CN102913598B (en) * | 2012-10-30 | 2016-03-23 | 顺德职业技术学院 | Planetary gear type manual transmission |
| CN102913598A (en) * | 2012-10-30 | 2013-02-06 | 顺德职业技术学院 | Planetary gear type manual transmission |
| CN102927221B (en) * | 2012-10-31 | 2015-05-13 | 长城汽车股份有限公司 | Automatic transmission and vehicle applying same |
| CN102927221A (en) * | 2012-10-31 | 2013-02-13 | 长城汽车股份有限公司 | Automatic transmission and vehicle applying same |
| US10030748B2 (en) | 2012-11-17 | 2018-07-24 | Dana Limited | Continuously variable transmission |
| US9644530B2 (en) | 2013-02-08 | 2017-05-09 | Dana Limited | Internal combustion engine coupled turbocharger with an infinitely variable transmission |
| US9638301B2 (en) | 2013-03-14 | 2017-05-02 | Dana Limited | Ball type continuously variable transmission |
| US9689482B2 (en) | 2013-03-14 | 2017-06-27 | Dana Limited | Ball type continuously variable transmission |
| CN103195886B (en) * | 2013-03-28 | 2015-09-09 | 长城汽车股份有限公司 | Automobile and speed changer thereof |
| CN103148182B (en) * | 2013-03-28 | 2016-01-27 | 长城汽车股份有限公司 | Automobile and speed changer thereof |
| CN103148182A (en) * | 2013-03-28 | 2013-06-12 | 长城汽车股份有限公司 | Automobile and speed changer thereof |
| US9777815B2 (en) | 2013-06-06 | 2017-10-03 | Dana Limited | 3-mode front wheel drive and rear wheel drive continuously variable planetary transmission |
| US10030751B2 (en) | 2013-11-18 | 2018-07-24 | Dana Limited | Infinite variable transmission with planetary gear set |
| US10088022B2 (en) | 2013-11-18 | 2018-10-02 | Dana Limited | Torque peak detection and control mechanism for a CVP |
| US10030594B2 (en) | 2015-09-18 | 2018-07-24 | Dana Limited | Abuse mode torque limiting control method for a ball-type continuously variable transmission |
| 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 |
Granted publication date: 20120314 Termination date: 20170630 |
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| CF01 | Termination of patent right due to non-payment of annual fee |