CN103423386A - Six-speed dual-clutch transmission drive device - Google Patents
Six-speed dual-clutch transmission drive device Download PDFInfo
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- CN103423386A CN103423386A CN201310321291XA CN201310321291A CN103423386A CN 103423386 A CN103423386 A CN 103423386A CN 201310321291X A CN201310321291X A CN 201310321291XA CN 201310321291 A CN201310321291 A CN 201310321291A CN 103423386 A CN103423386 A CN 103423386A
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- gear
- synchronizer
- clutch
- double planetary
- planetary gear
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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
- F16H3/006—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
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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
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing orbital gears
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Abstract
The invention discloses a six-speed dual-clutch transmission drive device. The six-speed dual-clutch transmission drive device comprises a first dual-row planetary gear train and a second dual-row planetary gear train, and one of the first dual-row planetary gear train and the second dual-row planetary gear train is composed of a front planetary row and a back planetary row. In the front planetary row, a front sun gear and a back planetary carrier are connected into a whole and fixedly connected with a shell through a first frequently-meshed synchronizer or clutches. A dual planetary gear structure is adopted for the back planetary row, a front gear ring and a back gear ring are connected into a whole, and power can be transmitted to the back sun gear or the back gear ring through a second synchronizer or a third synchronizer or the clutches and is output by a front planetary carrier. A Simpson type gear speed change mechanism is adopted for the other dual-row planetary gear train, the front sun gear and the back sun gear are connected into a whole and connected with a second outer shaft sleeve, and the front gear ring is connected with a second intermediate shaft. According to the six-speed dual-clutch transmission drive device, the Simpson type gear speed change mechanism and a novel dual planetary row gear speed change mechanism are combined, more speed ratio gears are achieved, and the size of a transmission is reduced.
Description
Technical field
The present invention relates to the automotive transmission technical field, specifically relate to a kind of six fast transmission device of dual-clutch transmissions.
Background technique
The automotive transmission transmission device, by train pattern difference used, has two kinds of axis jointing type speed changer (parallel shaft transmission) and axis rotary speed gears (planetary transmission).Quantity by clutch can be divided into single clutch speed changer and double-clutch speed changer.The actuating unit of the double-clutch speed changer of application is parallel shaft transmission at present, power transmission is divided into two lines, the one, odd number shelves transfer route, the 2nd, even number shelves transfer route, article two, power transmission line connects first, second input shaft by first, second clutch respectively, by the driving gear on the driven shaft corresponding with two input shafts, output power again, double-clutch speed changer controls by the coordination of two clutches and each synchronizer is controlled, can realize in the situation that do not cut off the power transmission ratio, thereby shorten shift time.Yet the parallel-axis type double-clutch speed changer must adopt independent reverse gear shaft and reverse gear.When adopting an output shaft, the speed changer axial dimension is large; While adopting two output shafts, the speed changer radial dimension is large, takes up room large, is unfavorable for the topology layout design of automobile.The current double-clutch speed changer of application, speed ratio changes greatly, and the engine speed variation greatly, makes the smoothness of automobile poor during gear shift like this.
Summary of the invention
The technical problem to be solved in the present invention is, provides that a kind of structure is more compact by six fast transmission device of dual-clutch transmissions of brand new, and what reduce speed changer axially reaches radial dimension, to overcome the deficiencies in the prior art.
For solving the problems of the technologies described above, the technical solution used in the present invention is: six fast transmission device of dual-clutch transmissions, comprise the first clutch and the first corresponding input shaft, the second clutch and the second corresponding input shaft, a plurality of synchronizers, output shaft, the sheathed setting of described first and second input shaft, also comprise first, second double planetary gear train, intermeshing the first gear and the second gear and the 3rd gear and the 4th gear; The double planetary gear train of one of them of described first, second double planetary gear train is comprised of front and back two rows of planetary rows, and in front planet row, front sun gear is connected with rear planet carrier, by the first normal synchronizer or clutch and housing of meshing, fixes; Rear planet row adopts the dual planetary gear structure, and front ring gear is connected with rear gear ring, power can by the second synchronizer or the 3rd synchronizer or clutch outer shaft after first be delivered to rear sun gear or after gear ring, and exported by front planet carrier; The double planetary gear train of another of described first, second double planetary gear train adopts the Simpson gear shift, and front sun gear is connected with rear sun gear and is connected with the second external axle sleeve, and front ring gear is connected with the second jack shaft.
The described second double planetary gear train adopts the Simpson gear shift, the front sun gear of described Simpson gear shift is connected with the second jack shaft and the 4th gear, and the front planet carrier of described Simpson gear shift is connected with rear gear ring and the second gear.
The described first normal engagement synchronizer is located between the first front external axle sleeve of double planetary gear train first and housing, the second synchronizer is arranged between the rear gear ring and the 3rd synchronizer of the first double planetary gear train, and described the 3rd synchronizer is arranged between the first rear external axle sleeve and the second input shaft.
The 4th synchronizer is arranged between the rear planet carrier and the second external axle sleeve of the second double planetary gear train, the 5th synchronizer is arranged between the second normal engagement synchronizer and the second external axle sleeve of the second double planetary gear train, and the second normal engagement synchronizer is arranged between the second jack shaft of the 4th gear and the second double planetary gear train.
The described first double planetary gear train adopts the Simpson gear shift, and the second normal engagement synchronizer and the 5th synchronizer are placed on the right side of the first double planetary gear train.
Described pair of clutch component is placed on the right side of the first double planetary gear train, and the described pair of clutch component and output shaft are at homonymy not and not at same axis.
The described first normal engagement synchronizer is placed on the right side of the second double planetary gear train, and two clutch components and output shaft are at homonymy not and not at same axis.
Described output shaft is placed on the left side of the first double planetary gear train, and two clutch components and output shaft are at homonymy not but on same axis.
The first gear or the second gear and the engagement of main reducing gear driven gear, main reducing gear driven gear connected with differential.
Compared with prior art, the present invention has the following advantages: the present invention is on the basis of existing dual-clutch transmission, by adopting the combination of Simpson gear shift and novel double-row star toothrow wheel gear, and coordinate two clutches, a plurality of synchronizers use, make it both can reach with few gear logarithm realize more the purpose of multiple gear ratios gear, can realize the shift property of dual-clutch transmission again, and can reduce the axial and radial dimension of speed changer, make the size of speed changer controlled, the vehicle structure layout design is more flexible, owing to reducing production costs.Simultaneously transmission gear ratio changes littlely, and the engine speed variation is less during gear shift like this, and the gear shift smoothness is improved.
The accompanying drawing explanation
Fig. 1 is the fast transmission device of dual-clutch transmission first embodiment's power-transmitting unit schematic diagram of the present invention six.
The power-transmitting unit schematic diagram that Fig. 2 is second embodiment of the invention.
The power-transmitting unit schematic diagram that Fig. 3 is third embodiment of the invention.
The power-transmitting unit schematic diagram that Fig. 4 is fourth embodiment of the invention.
The power-transmitting unit schematic diagram that Fig. 5 is fifth embodiment of the invention.
The structural representation that the output form that Fig. 6 is the present invention's six fast transmission device of dual-clutch transmissions changes.
Embodiment
The double planetary gear train of the present invention first and the second double planetary gear train adopt novel double-row star toothrow wheel gear or Simpson gear shift.Can obtain multiple six speed transmission transmission scheme by combination.
Below, in conjunction with Figure of description and specific embodiment, technological scheme of the present invention is further described.
The first embodiment
Referring to Fig. 1, double clutch of the present invention comprises two clutch components 1 (comprise first clutch 2 and second clutch 3, distinguish the first input shaft 4, second input shaft 5 of corresponding two clutches), the double planetary gear train 182 of the first double planetary gear train 181, second, output shaft 6 and a plurality of synchronizer.The first double planetary gear train and the second double planetary gear train are with upper and lower structural configuration, the first double planetary gear train adopts novel double-row star toothrow wheel gear, the second double planetary gear train adopts the Simpson gear shift, the first double planetary gear train comprises the first planet row X1 and the second planet row X2, and the second double planetary gear train comprises third planet row X3 and fourth planet row X4.
The front sun gear 105 of the first double planetary gear train, rear planet carrier 106 are connected with the first front external axle sleeve 115, front ring gear 103 is connected with rear gear ring 107, front planet carrier 102 is connected with the first gear 161, rear planet row X2 adopts dual planetary gear structural type, layman's star-wheel 108 and expert's star-wheel 109 are intermeshing, and rear sun gear is connected with the first rear external axle sleeve 114.
The front sun gear 134 of the second double planetary gear train is connected with the second jack shaft 143 and the 4th gear 164, and front planet carrier 131 is connected with rear gear ring 136 and the second gear 162.Front sun gear 134 is connected with rear sun gear 139 and is connected with the second external axle sleeve 143, and front ring gear 132 is connected with the second jack shaft 142.
First input shaft 4 the other ends are connected with the 3rd gear 183, the three gears 163 and the 4th gear 164 engagements, the first gear 161 and the second gear 162 engagements, and the second gear 162 is connected with output shaft 6, and output shaft 6 and double clutch assembly 1 are in the same side.
The first normal engagement synchronizer 101 is located between the first front external axle sleeve 115 of double planetary gear train 181 first and housing, and the second synchronizer (fourth gear synchronizer 112) is arranged between the rear gear ring 107 and the 3rd synchronizer (two, six grades of synchronizers 113) of the first double planetary gear train 181.The 3rd synchronizer (two, six grades of synchronizers 113) is arranged between the first rear external axle sleeve 114 and the second input shaft 5.
The 4th synchronizer (one, third gear synchronizer 138) is arranged between the rear planet carrier 137 and the second external axle sleeve 143 of the second double planetary gear train 182.The 5th synchronizer (Five-gear synchronizer 140) is arranged between the second normal engagement synchronizer 141 and the second external axle sleeve 143 of the second double planetary gear train 182.The second normal engagement synchronizer 141 is arranged between the second jack shaft 142 of the 4th gear 164 and the second double planetary gear train 182.
The double-clutch speed changer of the present embodiment can be realized six fast forward gearss and a fast reverse gear.The first double planetary gear train 181 is realized two, four, six gears controls.The second double planetary gear train 182 realizes that one, three, five grade and reverse gear control.
Action at each gear synchronizer and clutch is as follows:
During neutral state, as shown in Figure 1, the first normal engagement synchronizer 101 links together the front external axle sleeve 115 of the first double planetary gear train first to maintain static with housing, the second normal engagement synchronizer 141 links together the second jack shaft 142 of the 4th gear 164 and the second double planetary gear train 182, one, third gear synchronizer 138 mediates, fourth gear synchronizer 112 and two, six grades of synchronizers 113 and Five-gear synchronizer 140 on right side in jointing state not.
One grade: one, third gear synchronizer 138 moves to left, and the rear planet carrier 137 in the second double planetary gear train 182 is maintained static with housing, and the such second double planetary gear train 182 forms restriction relation.First clutch 2 engages simultaneously.Power passes to the first input shaft 4, the three gear 163, the four gears 164 through first clutch 2, then arrives output shaft through the second double planetary gear train 182.Now second clutch 3 is in separated state, the position of all the other synchronizers when neutral state.
Second gear: two, six grades of synchronizers 113 move to left, and the first rear external axle sleeve 114 is connected with the second input shaft 5, and power is input to rear sun gear 110.First clutch 2 separates, and second clutch 3 engages simultaneously, and power passes to the second input shaft 5 through first clutch 2, through the first double planetary gear train 182, the first gear 161, the second gears 162, then by output shaft 6 outputs.
Third gear: one, third gear synchronizer 137 moves to right, and the second external axle sleeve 143 is fixing.Second clutch 3 separates, and first clutch 2 engages, and realizes the third gear transmission of power.
Fourth gear: fourth gear synchronizer 112 moves to left, and rear gear ring 107 is connected with two, six grades of synchronizers 113.First clutch 2 separates, and second clutch 3 engages, and realizes the fourth gear transmission of power.Power passes to the second input shaft 5 through second clutch 2, through the first double planetary gear train 181, the first gear 161, the second gears 162, then by output shaft 8 outputs.
Five grades: Five-gear synchronizer 140 moves to left, and the second normal engagement synchronizer 141 is connected with axle sleeve 143 in the middle of second.Second clutch 3 separates, and first clutch 2 engages, and realizes five grades of transmission of power.
Six grades: the first normal engagement synchronizer 101 moves to right, and two, six grades of synchronizers 113, fourth gear synchronizers 112 move to left simultaneously.First clutch 2 separates, and second clutch 3 engages, and realizes six grades of shelves transmission of power.Power passes to the second input shaft 5 through second clutch 2, through the first double planetary gear train 181, the first gear 161, the second gears 162, then by output shaft 8 outputs.
Reverse gear: second normal engagement synchronizer 141 right sides, Five-gear synchronizer 140 moves to left, and one, third gear synchronizer 138 moves to left.Second clutch 3 separates, and first clutch 2 engages, and realizes the reverse gear transmission of power.
Double-clutch speed changer in this invention can be realized multiple transforming gear pattern:
The order shift mode:
The order upgrade, take one grade be raised to second gear as example, before shifting commands sends, speed changer is in a gear working state.Prepare to implement to need in advance two, six grades of synchronizers 113 to be moved to left the first rear external axle sleeve 114 is connected with the second input shaft 5 before gearshift, now first clutch 2 and second clutch 3 are still respectively in engaging and separated state.When control system is sent shifting commands and is raised to second gear by one grade, all synchronizer hold modes are motionless, first clutch 2 progressively separates, second clutch 3 progressively engages simultaneously, until first clutch 2 separates fully, second clutch 3 engages fully, and control one, third gear synchronizer 137 gets back to neutral position, the irrelevant synchronizer of all the other and a grade and second gear also is failure to actuate.The order of other gears upgrades and order lowers category also knows by inference with same method.
The jump shift mode:
Odd gear is changed to the jump lifting shelves of even number gear, be raised to fourth gear or five grades and drop to second gear etc. as one grade, the even number gear is changed to the jump lifting shelves of odd gear, upgrade five grades or six grades and drop to third-class as two, its gear changing mode is the same with the controlling method that order upgrades, and can use the same method and know by inference.
The jump that odd gear is changed to odd gear upgrades, take one grade rise third gear as example, before shifting commands sends, speed changer is in a gear working state.Before prepare implementing gearshift, first clutch 2 separates, one, third gear synchronizer 137 first gets back to neutral position, then move to right by the second double planetary gear train second in the middle of axle sleeve 143 with housing, fix.First clutch 2 is rejoined, and completes one grade of control that rises third gear.In this process, second clutch 3 is always in separated state, and the irrelevant synchronizer of all the other and a grade and third gear also is failure to actuate.The jump that the jump lifting shelves that the jump that odd gear is changed to odd gear lowers category and the even number gear is changed to the even number gear and odd gear the are changed to odd gear controlling method that upgrades is the same, can use the same method and know by inference.
The setting of each gear velocity ratio can be by each planet row a value (a equal planet row the ratio of the gear ring number of teeth and the sun gear number of teeth), the velocity ratio a of the first gear 161 and the second gear 162 and the 3rd gear 163 and the 4th gear 164 velocity ratio a set.For example establish the first double planetary gear train and comprise the first planet row X1 and the second planet row X2, the second double planetary gear train comprises that a value of third planet row X3 and fourth planet row X4 is respectively a1.7, a2.0, a1.5, a4.2, a1, a1.25, obtain the action of each gear velocity ratio shown in table 1, ratio level and gear shift executive component.From numerical value, the velocity ratio of each gear, rationally more appropriate than level, obtain gear ratio characteristic preferably.
The action schedule of table 1 gear shift executive component, each grade of transmission are when than level figure
Annotate: " zero " means that clutch engages or the synchronizer action
The second embodiment
Referring to Fig. 2, on the first embodiment's basis, location swap by the first double planetary gear train and the second double planetary gear train, the second normal engagement synchronizer 141 and Five-gear synchronizer 140 are placed on the right side of the first double planetary gear train, all the other position of components are constant, power is by output gear 7 outputs that are connected with the front planet carrier 102 of the second double planetary gear train, and two clutch components 1 and output shaft gear 7 be not in the same side and at same axis.The velocity ratio that needs appropriate change the first gear 261 and the second gear 262, the 3rd gear 263 and the 4th gear 264 is set according to the gear velocity ratio, and a value of each planet row.The such first double planetary gear train 181 is realized 1.3.5 and reverse gear, and the second double planetary gear train 182 is realized the 2.4.6 shelves.
The 3rd embodiment
Referring to Fig. 3, on the first embodiment's basis, two clutch components 1 are placed on to the right side of the first double planetary gear train, all the other position of components are constant, and two clutch components 1 and output shaft 6 are at homonymy not and not at same axis.The velocity ratio that needs appropriate change the first gear 261 and the second gear 262, the 3rd gear 263 and the 4th gear 264 is set according to the gear velocity ratio, and a value of each planet row.The such first double planetary gear train 181 is realized the 2.4.6 shelves, and the second double planetary gear train 182 is realized 1.3.5 and reverse gear.
The 4th embodiment
Referring to Fig. 4, on the 3rd embodiment's basis, location swap by the first double planetary gear train and the second double planetary gear train, and often mesh by first the right side that synchronizer 101 is placed on the second double planetary gear train, all the other position of components are constant, and two clutch components 1 and output shaft 6 are at homonymy not and not at same axis.The velocity ratio that needs appropriate change the first gear 261 and the second gear 262, the 3rd gear 263 and the 4th gear 264 is set according to the gear velocity ratio, and a value of each planet row.The such first double planetary gear train 181 is realized 1.3.5 and reverse gear, and the second double planetary gear train 182 is realized the 2.4.6 shelves.
The 5th embodiment
Referring to Fig. 5, on the 4th embodiment's basis, output shaft 6 is placed on to the left side of the first double planetary gear train, all the other position of components are constant, and two clutch components 1 and output shaft 6 are at homonymy not but at same axis.The velocity ratio that needs appropriate change the first gear 261 and the second gear 262, the 3rd gear 263 and the 4th gear 264 is set according to the gear velocity ratio, and a value of each planet row.The such first double planetary gear train 181 is realized 1.3.5 and reverse gear, and the second double planetary gear train 182 is realized the 2.4.6 shelves.
In addition, in all transmission modes, two clutch components and output shaft can suitably change in the output form of the same side, referring to Fig. 6, reduce the first gear 161 and the second gear 162 diameters, two gears and main reducing gear driven gear 190 directly mesh, and by the external outputting power of differential mechanism 191.
Claims (9)
1. six fast transmission device of dual-clutch transmissions, comprise the first clutch and the first corresponding input shaft, the second clutch and the second corresponding input shaft, a plurality of synchronizers, output shaft, the sheathed setting of described first and second input shaft, also comprise first, second double planetary gear train, intermeshing the first gear and the second gear and the 3rd gear and the 4th gear; It is characterized in that: the double planetary gear train of one of them of described first, second double planetary gear train is comprised of front and back two rows of planetary rows, in front planet row, front sun gear is connected with rear planet carrier, by the first normal synchronizer or clutch and housing of meshing, fixes; Rear planet row adopts the dual planetary gear structure, and front ring gear is connected with rear gear ring, power can by the second synchronizer or the 3rd synchronizer or clutch outer shaft after first be delivered to rear sun gear or after gear ring, and exported by front planet carrier;
The double planetary gear train of another of described first, second double planetary gear train adopts the Simpson gear shift, and front sun gear is connected with rear sun gear and is connected with the second external axle sleeve, and front ring gear is connected with the second jack shaft.
2. according to claim 1 six fast transmission device of dual-clutch transmissions, it is characterized in that: the described second double planetary gear train adopts the Simpson gear shift, the front sun gear of described Simpson gear shift is connected with the second jack shaft and the 4th gear, and the front planet carrier of described Simpson gear shift is connected with rear gear ring and the second gear.
3. according to claim 2 six fast transmission device of dual-clutch transmissions, it is characterized in that: the described first normal engagement synchronizer is located between the first front external axle sleeve of double planetary gear train first and housing, the second synchronizer is arranged between the rear gear ring and the 3rd synchronizer of the first double planetary gear train, and described the 3rd synchronizer is arranged between the first rear external axle sleeve and the second input shaft.
4. according to claim 3 six fast transmission device of dual-clutch transmissions, it is characterized in that: the 4th synchronizer is arranged between the rear planet carrier and the second external axle sleeve of the second double planetary gear train, the 5th synchronizer is arranged between the second normal engagement synchronizer and the second external axle sleeve of the second double planetary gear train, and the second normal engagement synchronizer is arranged between the second jack shaft of the 4th gear and the second double planetary gear train.
5. according to claim 1 six fast transmission device of dual-clutch transmissions, it is characterized in that: the described first double planetary gear train adopts the Simpson gear shift, and the second normal engagement synchronizer and the 5th synchronizer are placed on the right side of the first double planetary gear train.
6. according to claim 1 six fast transmission device of dual-clutch transmissions, it is characterized in that: described pair of clutch component is placed on the right side of the first double planetary gear train, and the described pair of clutch component and output shaft are at homonymy not and not at same axis.
7. according to claim 1 six fast transmission device of dual-clutch transmissions is characterized in that: the described first normal engagement synchronizer is placed on the right side of the second double planetary gear train, and two clutch components and output shaft are at homonymy not and not at same axis.
8. according to claim 1 six fast transmission device of dual-clutch transmissions, it is characterized in that: described output shaft is placed on the left side of the first double planetary gear train, and two clutch components and output shaft are at homonymy not but on same axis.
9. according to the arbitrary described six fast transmission device of dual-clutch transmissions of claim 1 to 8, it is characterized in that: the first gear or the second gear and the engagement of main reducing gear driven gear, main reducing gear driven gear connected with differential.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310321291.XA CN103423386B (en) | 2013-07-27 | 2013-07-27 | Six fast transmission device of dual-clutch transmissions |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310321291.XA CN103423386B (en) | 2013-07-27 | 2013-07-27 | Six fast transmission device of dual-clutch transmissions |
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| Publication Number | Publication Date |
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| CN103423386A true CN103423386A (en) | 2013-12-04 |
| CN103423386B CN103423386B (en) | 2016-01-13 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201310321291.XA Expired - Fee Related CN103423386B (en) | 2013-07-27 | 2013-07-27 | Six fast transmission device of dual-clutch transmissions |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105546098A (en) * | 2016-01-19 | 2016-05-04 | 无锡商业职业技术学院 | Planetary gear type double-clutch six-gear automatic transmission |
| CN107420451A (en) * | 2017-10-06 | 2017-12-01 | 东莞市松研智达工业设计有限公司 | A kind of dual drive clutch |
| CN110259894A (en) * | 2018-03-12 | 2019-09-20 | 上海汽车集团股份有限公司 | A kind of 12 gear automatic gear-box |
| CN110735892A (en) * | 2019-11-18 | 2020-01-31 | 四川坤成润科技有限公司 | parallel fixed shaft type power shifting gearbox |
| WO2020143488A1 (en) * | 2019-01-11 | 2020-07-16 | 罗灿 | Balanced speed reducer of variable line speed planetary row having double sun gears |
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| US5078663A (en) * | 1989-09-16 | 1992-01-07 | Dr. Ing. H.C.F. Porsche Ag | Motor vehicle automatic transmission |
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| CN1746529A (en) * | 2004-09-07 | 2006-03-15 | 现代自动车株式会社 | Six-speed powertrain of an automatic transmission |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105546098A (en) * | 2016-01-19 | 2016-05-04 | 无锡商业职业技术学院 | Planetary gear type double-clutch six-gear automatic transmission |
| CN105546098B (en) * | 2016-01-19 | 2017-10-17 | 无锡商业职业技术学院 | A kind of double speed automatic transmissions of clutch six of planetary gear type |
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| CN110259894A (en) * | 2018-03-12 | 2019-09-20 | 上海汽车集团股份有限公司 | A kind of 12 gear automatic gear-box |
| WO2020143488A1 (en) * | 2019-01-11 | 2020-07-16 | 罗灿 | Balanced speed reducer of variable line speed planetary row having double sun gears |
| CN111801514A (en) * | 2019-01-11 | 2020-10-20 | 罗灿 | Double-sun-wheel line-speed-variable planetary row balance speed reducer |
| US11441641B2 (en) | 2019-01-11 | 2022-09-13 | Can Luo | Balanced speed reducer of variable line speed planetary row having double sun gears |
| CN110735892A (en) * | 2019-11-18 | 2020-01-31 | 四川坤成润科技有限公司 | parallel fixed shaft type power shifting gearbox |
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| CN103423386B (en) | 2016-01-13 |
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