CN103438163A - Multi-speed planetary gear type double-clutch gearbox - Google Patents
Multi-speed planetary gear type double-clutch gearbox Download PDFInfo
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- CN103438163A CN103438163A CN2013103212708A CN201310321270A CN103438163A CN 103438163 A CN103438163 A CN 103438163A CN 2013103212708 A CN2013103212708 A CN 2013103212708A CN 201310321270 A CN201310321270 A CN 201310321270A CN 103438163 A CN103438163 A CN 103438163A
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Abstract
The invention discloses a multi-speed planetary gear type double-clutch gearbox which comprises a first clutch, a first input shaft corresponding to the first clutch, a second clutch, a second input shaft corresponding to the second clutch, a plurality of synchronizers and an output shaft, wherein the first input shaft and the second input shaft are arranged in a sleeving way; the multi-speed planetary gear type double-clutch gearbox also comprises a first double-row planetary gear train, a second double-row planetary gear train, a first gear, a second gear, a third gear and a fourth gear, wherein the first gear is meshed with the second gear; the third gear is meshed with the fourth gear; one of the first double-row planetary gear train and the second double-row planetary gear train is formed by two planet rows; in the front planet row, a front sun gear is connected with a rear planet carrier into a whole, and is fixed with a shell by the first constant mesh synchronizer or the clutches; the rear planet row adopts a double-planet wheel structure; a front gear ring is connected with a rear gear ring into a whole; the power is transmitted into a rear sun gear or the rear gear ring by the second synchronizer, the third synchronizer or the clutches through a first rear outer shaft, and is output by a front planet carrier. The multi-speed planetary gear type double-clutch gearbox can realize more speed ratio gears by fewer gear pairs, reduces the size of the gearbox, and enables the structural layout design of an automobile to be more flexible.
Description
Technical field
The present invention relates to the automotive transmission technical field, specifically relate to a kind of multi-speed planetary gear type double-clutch speed changer.
Background technique
The automotive transmission driving mechanism, 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 power-transmitting 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.At present the double-clutch speed changer forward gears of application adopts 7 grades at most, and most widely used is six grades, and speed ratio changes greatly, like this during gear shift the engine speed variation greatly, make automobile power character, economical be not very desirable, smoothness is poor.
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 the multi-speed planetary gear type double-clutch speed changer of brand new, and what reduce speed changer axially reaches radial dimension, and the gear that simultaneously advances can be more, 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: a kind of multi-speed planetary gear type double-clutch speed changer, 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 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 one of them of described first, second double planetary gear train adopts the La Weinashi gear shift, small sun gear meshes and is connected with the second jack shaft with short planet wheel, short planet wheel and long planet wheel engagement, the large sun gear of rear planet row also meshes with long planet wheel, large sun gear is connected with the second outer shaft, front and back planet row common planet carrier and a gear ring, planet carrier is connected with the second jack shaft, and gear ring is connected with the second gear.
Described the first gear is connected with the planet carrier of the front planet row of described the first double planetary gear train, described the second gear is connected with the gear ring of the front planet row of described the second double planetary gear train, described the 3rd gear is connected with described the first input shaft, described the 4th gear is connected with the 7th synchronizer of the second double planetary gear train, and described output shaft is connected with described the second gear.
The described first normal engagement synchronizer is located between the first front outer shaft 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 outer shaft and the second input shaft.
The 4th synchronizer is arranged between the rear planet carrier and the second outer shaft of the second double planetary gear train, the 5th synchronizer is arranged between second outer shaft and the second normal engagement synchronizer of the second double planetary gear train, the described second normal engagement synchronizer is arranged between second jack shaft and the 7th synchronizer of the second double planetary gear train, and described the 7th synchronizer is arranged between second jack shaft and the 4th gear of the second double planetary gear train.
The described first double planetary gear train adopts the La Weinashi gear shift, small sun gear meshes and is connected with the second jack shaft with short planet wheel, short planet wheel and long planet wheel engagement, the large sun gear of rear planet row also meshes with long planet wheel, large sun gear is connected with the second outer shaft, front and back planet row common planet carrier and a gear ring, and planet carrier is connected with the second jack shaft, gear ring is connected with the second gear, and the second normal engagement synchronizer is arranged between the second jack shaft and the second input shaft.
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 La Weinashi 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 increases, and speed ratio changes less, and engine speed changes littlely during gear shift like this, makes the power character, economical all more satisfactory of automobile, and while gear shift smoothness is improved.
The accompanying drawing explanation
The power-transmitting unit schematic diagram that Fig. 1 is double-clutch speed changer the first embodiment of the present invention;
The power-transmitting unit schematic diagram that Fig. 2 is second embodiment of the invention;
The structural representation that the output form that Fig. 3 is double-clutch speed changer of the present invention changes.
Embodiment
The double planetary gear train of the present invention first and the second double planetary gear train adopt La Weinashi gear shift or novel double-row star toothrow wheel gear.Can obtain multiple transmission scheme by combination.
Below, in conjunction with Figure of description and specific embodiment, technological scheme of the present invention is further described, should be appreciated that specific embodiment described herein, only in order to explain the present invention, is not construed as limiting the invention.
The first embodiment (seven grades)
Referring to Fig. 1, double clutch of the present invention comprises that two clutch components 1 (comprise first clutch 2 and second clutch 3, distinguish the first input shaft 4, the double planetary gear train 182 of the double planetary gear train 181, second of the second input shaft 5, the first, output shaft 8 and a plurality of synchronizer of corresponding two clutches.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 La Weinashi 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 planet row before third planet row X3() and fourth planet row X4(after planet row).The second input shaft 5 is set in outside the first input shaft 4.
The front sun gear 105 of the first double planetary gear train, rear planet carrier 106 are connected with the first front outer shaft 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 110 is connected with the first rear outer shaft 114.The first rear outer shaft 114 and the first front outer shaft 115 are set in outside the second input shaft 5.
The front planet row X3 of the second double planetary gear train adopts dual planetary gear structural type, small sun gear 133 meshes and is connected with the second jack shaft 132 with short planet wheel 123, short planet wheel 123 and long planet wheel 124 engagements, the large sun gear 125 of rear planet row X4 also meshes with long planet wheel 124, large sun gear 125 is connected with the second outer shaft 131, front and back planet row common planet carrier 121 and a gear ring 122, planet carrier 121 is connected with major axis 130 in the middle of second, and gear ring 122 is connected with the second gear 162 and carries out power output by output shaft 8.The second outer shaft 131 is located at outside the second jack shaft 132.
First input shaft 4 the other ends are connected with the 3rd gear 163, 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 8, and output shaft 8 and double clutch assembly 1 are in the same side.
The first normal engagement synchronizer 101 is located between the first front outer shaft 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 outer shaft 114 and the second input shaft 5.
The 4th synchronizer (one, third gear synchronizer 126) is arranged between planet carrier 121 and the second outer shaft 131, the 5th synchronizer (reversing-gear synchronizer 127) is arranged between the second outer shaft 131 and the second normal engagement synchronizer 128, the second normal engagement synchronizer 128 is arranged between the second jack shaft 132 and the 7th synchronizer 129, between the 7th synchronizer (five, seven grades of synchronizers) 129, is arranged between the second middle major axis 130 and the 4th gear 164.
The double-clutch speed changer of the present embodiment can be realized seven 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, seven 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 outer shaft 115 of the first double planetary gear train first to maintain static with housing, and the second normal engagement synchronizer 128 links together second double planetary gear train the second jack shaft 132 and the 7th synchronizer 129.One, third gear synchronizer 126 mediates, fourth gear synchronizer 112 and two, six grades of synchronizers 113 and five, seven grades of synchronizers 129 and reversing-gear synchronizer 127 on right side in jointing state not.
One grade: one, third gear synchronizer 126 moves to left, and the planet carrier 121 in the second double planetary gear train 182 is maintained static moving, and the such second double planetary gear train 182 forms restriction relations.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 8 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 outer shaft 114 is connected with the second input shaft 5, and the such first double planetary gear train 181 forms restriction relation.First clutch 2 separates, and second clutch 3 engages simultaneously, and power passes to the second input shaft 5 through second clutch 2, through the first double planetary gear train 182, the first gear 161, the second gears 162, then by output shaft 8 outputs.
Third gear: one, third gear synchronizer 126 moves to right, and the second outer shaft 131 is connected, thereby also connect motionless by the large sun gear of the second double planetary gear train 125.Second clutch 3 separates, and first clutch 2 engages, and realizes the third gear transmission of power.Power passes to the first input shaft 4, the three gear 163, the four gears 164 through first clutch 2, then arrives output shaft 8 through the second double planetary gear train 182.
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, seven grades of synchronizers 129 move to left, and the 4th gear 164 is connected with major axis 130 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.
Seven grades: five, seven grades of synchronizers 129 move to left, and the 4th gear 164 is connected with major axis 130 in the middle of second, and the second normal engagement synchronizer 128 moves to right, and while one, third gear synchronizer 126 move to right, and the second outer shaft 131 is fixing.Second clutch 3 separates, and first clutch 2 engages, and realizes seven grades of transmission of power.Power passes to the first input shaft 4, the three gear 163, the four gears 164 through first clutch 2, then arrives output shaft 8 through the second double planetary gear train 182.
Reverse gear: reversing-gear synchronizer 127 moves to left, and the second outer shaft 131 and the second normal engagement synchronizer 128 is connected to one, third gear synchronizer 126 fixed carrier 121 that moves to left.Second clutch 3 separates, and first clutch 2 engages, and realizes the reverse gear transmission of power.Power passes to the first input shaft 4, the three gear 163, the four gears 164 through first clutch 2, then arrives output shaft 8 through the second double planetary gear train 182.
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 outer shaft 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 126 gets back to neutral position, make the second double planetary gear train planet carrier 121 unfettered, 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 seven grades and drop to fourth 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, and one, third gear synchronizer 126 first gets back to neutral position, then move to right and connect motionless by the large sun gear of the second double planetary gear train 125.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 passed through each planet row
value (
equal planet row the ratio of the gear ring number of teeth and the sun gear number of teeth), the velocity ratio of the first gear 161 and the second gear 162
and the 3rd gear 163 and the 4th gear 164 velocity ratios
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 third planet is arranged X3 and fourth planet is arranged X4's
value is respectively
2.1,
2.1,
4.4,
3.2,
1.08,
1.25, 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, more appropriate rationally 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
Zero means that clutch engages or the synchronizer action
The second embodiment (six grades)
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, cancel five, seven grades of synchronizers 129 and the second middle major axis 130, the second normal engagement synchronizer 128 positions are arranged between the second jack shaft 132 and the second input shaft 5, two clutch components 1 are arranged on the first double planetary gear train 181 right sides, and output shaft 8 is arranged on the first double planetary gear train 181 with two clutch components 1 at same axis and at homonymy not.The second outer shaft 131 is set in outside the second jack shaft 132.The first rear outer shaft 114 is set in outside the first front outer shaft 115.The first input shaft 4 is set in outside the second input shaft 5.
The velocity ratio that needs appropriate change the first gear 161 and the second gear 162, the 3rd gear 163 and the 4th gear 164 is set according to the gear velocity ratio, and each planet row
value.The such first double planetary gear train 181 realizes one, three, five and reverse gear, and the second double planetary gear train 182 is realized two, four, six grades.
From top embodiment, output shaft 8 can change with the position relationship of two clutch components 1, when being arranged on the second double planetary gear train 182, output shaft 8 can be placed on not homonymy and the same side with two clutch components 1, when homonymy not, output shaft 8 both can also can be at different axis at same axis from two clutch components 1, and when the same side, output shaft 8 can only be from two clutch components 1 at different axis.Can only be at homonymy not when output shaft 8 is arranged on the first double planetary gear train 181, but same output shaft 8 can also can be at different axis at same axis from two clutch components 1.Odd number shelves or even number shelves can be arranged on the first double planetary gear train 181 also can be at the second double planetary gear train 182.Obtain 10 kinds of transmission schemes by permutation and combination thus, referring to table 2.
table 2 La Weinashi gear shift and novel double-row star toothrow wheel gear combination transmission scheme
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. 3, 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 (7)
1. a multi-speed planetary gear type double-clutch speed changer, 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, described first and second input shaft setting, 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 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.
2. multi-speed planetary gear type double-clutch speed changer according to claim 1, it is characterized in that: the double planetary gear train of one of them of described first, second double planetary gear train adopts the La Weinashi gear shift, small sun gear meshes and is connected with the second jack shaft with short planet wheel, short planet wheel and long planet wheel engagement, the large sun gear of rear planet row also meshes with long planet wheel, large sun gear is connected with the second outer shaft, front and back planet row common planet carrier and a gear ring, planet carrier is connected with major axis in the middle of second, and gear ring is connected with the second gear.
3. multi-speed planetary gear type double-clutch speed changer according to claim 2, it is characterized in that: described the first gear is connected with the planet carrier of the front planet row of described the first double planetary gear train, described the second gear is connected with the gear ring of the front planet row of described the second double planetary gear train, described the 3rd gear is connected with described the first input shaft, described the 4th gear is connected with the 7th synchronizer of the second double planetary gear train, and described output shaft is connected with described the second gear.
4. multi-speed planetary gear type double-clutch speed changer according to claim 3, it is characterized in that: the described first normal engagement synchronizer is located between the first front outer shaft 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 outer shaft and the second input shaft.
5. multi-speed planetary gear type double-clutch speed changer according to claim 4, it is characterized in that: the 4th synchronizer is arranged between the rear planet carrier and the second outer shaft of the second double planetary gear train, the 5th synchronizer is arranged between second outer shaft and the second normal engagement synchronizer of the second double planetary gear train, the described second normal engagement synchronizer is arranged between second jack shaft and the 7th synchronizer of the second double planetary gear train, and described the 7th synchronizer is arranged between the second middle major axis and the 4th gear of the second double planetary gear train.
6. multi-speed planetary gear type double-clutch speed changer according to claim 1, it is characterized in that: the described first double planetary gear train adopts the La Weinashi gear shift, small sun gear meshes and is connected with the second jack shaft with short planet wheel, short planet wheel and long planet wheel engagement, the large sun gear of rear planet row also meshes with long planet wheel, large sun gear is connected with the second outer shaft, front and back planet row common planet carrier and a gear ring, planet carrier is connected with the second jack shaft, gear ring is connected with the second gear, the second normal engagement synchronizer is arranged between the second jack shaft and the second input shaft.
7. according to the arbitrary described multi-speed planetary gear type double-clutch speed changer of claim 1 to 6, it is characterized in that: the second gear and the engagement of main reducing gear driven gear, main reducing gear driven gear connected with differential.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201310321270.8A CN103438163B (en) | 2013-07-27 | 2013-07-27 | A kind of multi-speed planetary gear type double-clutch gearbox |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201310321270.8A CN103438163B (en) | 2013-07-27 | 2013-07-27 | A kind of multi-speed planetary gear type double-clutch gearbox |
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| CN103438163B CN103438163B (en) | 2016-08-10 |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103711845A (en) * | 2013-12-30 | 2014-04-09 | 长城汽车股份有限公司 | Multi-gear dual-clutch transmission and car |
| CN108351011A (en) * | 2015-11-24 | 2018-07-31 | 舍弗勒技术股份两合公司 | driving device for motor vehicle |
| CN110657206A (en) * | 2018-06-29 | 2020-01-07 | 比亚迪股份有限公司 | Transmission, power driving system and vehicle |
| CN110657208A (en) * | 2018-06-29 | 2020-01-07 | 比亚迪股份有限公司 | Transmission, power driving system and vehicle |
| 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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| JP2001182785A (en) * | 1999-12-24 | 2001-07-06 | Aisin Seiki Co Ltd | Transmission |
| US20040110596A1 (en) * | 2002-12-06 | 2004-06-10 | Usoro Patrick Benedict | Family of multi-speed dual-clutch transmissions having three interconnected planetary gear members |
| CN102797812A (en) * | 2012-08-23 | 2012-11-28 | 赵良红 | Double-clutch transmission device |
| CN102913598A (en) * | 2012-10-30 | 2013-02-06 | 顺德职业技术学院 | Planetary gear type manual transmission |
| CN203363023U (en) * | 2013-07-27 | 2013-12-25 | 顺德职业技术学院 | Multi-speed planetary gear type double-clutch transmission |
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2013
- 2013-07-27 CN CN201310321270.8A patent/CN103438163B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001182785A (en) * | 1999-12-24 | 2001-07-06 | Aisin Seiki Co Ltd | Transmission |
| US20040110596A1 (en) * | 2002-12-06 | 2004-06-10 | Usoro Patrick Benedict | Family of multi-speed dual-clutch transmissions having three interconnected planetary gear members |
| CN102797812A (en) * | 2012-08-23 | 2012-11-28 | 赵良红 | Double-clutch transmission device |
| CN102913598A (en) * | 2012-10-30 | 2013-02-06 | 顺德职业技术学院 | Planetary gear type manual transmission |
| CN203363023U (en) * | 2013-07-27 | 2013-12-25 | 顺德职业技术学院 | Multi-speed planetary gear type double-clutch transmission |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103711845A (en) * | 2013-12-30 | 2014-04-09 | 长城汽车股份有限公司 | Multi-gear dual-clutch transmission and car |
| CN108351011A (en) * | 2015-11-24 | 2018-07-31 | 舍弗勒技术股份两合公司 | driving device for motor vehicle |
| CN110657206A (en) * | 2018-06-29 | 2020-01-07 | 比亚迪股份有限公司 | Transmission, power driving system and vehicle |
| CN110657208A (en) * | 2018-06-29 | 2020-01-07 | 比亚迪股份有限公司 | Transmission, power driving system and vehicle |
| WO2020143488A1 (en) * | 2019-01-11 | 2020-07-16 | 罗灿 | Balanced speed reducer of variable line speed planetary row having double sun gears |
| US11441641B2 (en) | 2019-01-11 | 2022-09-13 | Can Luo | Balanced speed reducer of variable line speed planetary row having double sun gears |
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| Publication number | Publication date |
|---|---|
| CN103438163B (en) | 2016-08-10 |
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Effective date of registration: 20231023 Address after: The third, second, and third floors of the first floor, No. 15 Dafu Road, Ronggui Dafuji Neighborhood Committee, Shunde District, Foshan City, Guangdong Province, 528303 Patentee after: Nuo Feng Lin Address before: 528300 93 Desheng East Road, Shunde District, Foshan, Guangdong. Patentee before: SHUNDE POLYTECHNIC |
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