CN102425647A - Power transmission mechanism for double-clutch automatic transmission - Google Patents
Power transmission mechanism for double-clutch automatic transmission Download PDFInfo
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- CN102425647A CN102425647A CN2011103899612A CN201110389961A CN102425647A CN 102425647 A CN102425647 A CN 102425647A CN 2011103899612 A CN2011103899612 A CN 2011103899612A CN 201110389961 A CN201110389961 A CN 201110389961A CN 102425647 A CN102425647 A CN 102425647A
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- 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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Abstract
The invention relates to a power transmission mechanism for a double-clutch automatic transmission for an automobile. The power transmission mechanism comprises a power input shaft, an odd shift clutch input shaft, a first auxiliary shaft, a second auxiliary shaft, a middle shaft, a reverse gear idler shaft, an odd shift clutch, an even shift clutch, and a differential; the left end of the power input shaft is provided with a sun gear, a planetary gear, an internal gear ring, and a fixed planet carrier; an internal gear ring external gear is fixed outside the internal gear ring; the second auxiliary shaft is provided with an even shift driving gear, a reverse gear driving gear and an even shift synchronizer; the middle shaft is provided with a driven gear and first and second reverse gear driven gears; and the reverse gear idler shaft is provided with first and second reverse gear idler gears. The transmission mechanism is simple and is high in integrated level, and manufacturing cost of the double-clutch automatic transmission is reduced to certain extent.
Description
Technical field
The present invention relates to the power-transmitting unit of automotive transmission, particularly the double-clutch automatic gearbox power-transmitting unit.
Background technique
Automatic gearbox mainly contains four types: hydraulic mechanical type automatic transmission (AT), electric control mechanical type automatic speed variator (AMT), mechanical stepless automatic speed changer (CVT) and double-clutch automatic gearbox (DCT).Wherein double-clutch automatic gearbox (DCT) had both been inherited AMT and manual transmission is simple in structure, installing space is compact, in light weight, many advantages such as transmission efficiency is high, low cost of manufacture; Having merged AT uninterruptible power, the good characteristics of smooth shifting rapidly again, is a kind of speed changer of excellent performance.
The power transmission of double-clutch automatic gearbox (DCT) has two lines; Article one, be odd number shelves transfer route; Another is even number shelves transfer routes, and two power transmission lines connect odd number shelves input shaft and even number shelves input shaft through strange, even clutch respectively, output power through the driving gear on the driven shaft corresponding with input shaft again; The DCT speed changer is through the coordination control and the synchromesh unit control of two clutches; Can be implemented in transmission ratio under the situation of not cutting off power, thereby shorten shift time, effectively improve property of automatic shft.Yet the relative manual transmission of the power transmission structure of existing double-clutch automatic gearbox (DCT) is complicated, thereby it is big to make double-clutch automatic gearbox get difficulty of processing, and cost of production is high.
Summary of the invention
The purpose of this invention is to provide a kind of double-clutch automatic gearbox power-transmitting unit simple in structure, to reduce the manufacture cost of double-clutch automatic gearbox.
Double-clutch automatic gearbox power-transmitting unit according to the invention; Comprise power input shaft, odd number shelves Clutch input shaft, odd number shelves clutch, even number shelves clutch and differential mechanism; Also comprise first countershaft parallel, second countershaft, jack shaft and reverse idler gear axle with power input shaft and odd number shelves Clutch input shaft; Jack shaft is positioned at the centre of first countershaft and second countershaft; Said even number shelves clutch is installed on the power input shaft and the left end of second countershaft, and odd number shelves clutch is installed on the odd number shelves Clutch input shaft and the left end of first countershaft, at the left end of power input shaft sun gear, planetary pinion, ring gear and fixing planet carrier is installed; The ring gear fixed outside has the ring gear external gear coaxial with it, and the ring gear external gear is meshed with odd number shelves clutch driving gear;
Odd number shelves driving gear and odd number shelves synchronizer are installed on first countershaft, even number shelves driving gear, reverse driving gear and even number shelves synchronizer are installed on second countershaft;
Driven gear and one or two reverse gear driven gears with the engagement of even number shelves driving gear and odd number shelves driving gear are installed on the jack shaft, and wherein the differential gear of driven gear and differential mechanism meshes;
The first reverse idler gear gear and the second reverse idler gear gear are installed on the said reverse idler gear axle from left to right successively, and it meshes with reverse driving gear and one or two reverse gear driven gears respectively.
Odd number shelves driving gear comprises five grades of driving gears, third speed drive gear and one grade of driving gear; It is installed on first countershaft from left to right successively; Said odd number shelves synchronizer comprises a Five-gear synchronizer and a third gear synchronizer; Five-gear synchronizer is positioned at five grades of driving gears left side, and a third gear synchronizer is between third speed drive gear and one grade of driving gear.
Said even number shelves driving gear comprises fourth gear driving gear and second gear driving gear; It is installed on second countershaft from left to right successively; Be positioned at the reverse driving gear right side; Said even number shelves synchronizer comprises reverse gear synchronizer and two fourth gear synchronizers, and the reverse gear synchronizer is positioned at the reverse driving gear left side, and two fourth gear synchronizers are between fourth gear driving gear and second gear driving gear.
Driven gear on the said jack shaft comprises five grades of driven gears and three fourth gear driven gears; It is installed on the jack shaft from left to right successively; Be positioned at one or two reverse gear driven gears left side; Wherein one or two reverse gear driven gears mesh with one grade of driving gear, second gear driving gear and reverse idler gear shaftgear respectively, and three fourth gear driven gears mesh with third speed drive gear and fourth gear driving gear respectively, and five grades of driven gears mesh with five grades of driving gears engagements and differential gear respectively.
As another kind of technological scheme; Driven gear on the said jack shaft comprises five grades of driven gears and three fourth gear driven gears; It is installed on the jack shaft from left to right successively, is positioned at one or two reverse gear driven gears left side, and wherein one or two reverse gear driven gears mesh with one grade of driving gear, second gear driving gear and reverse idler gear shaftgear respectively; Three fourth gear driven gears mesh with third speed drive gear and fourth gear driving gear respectively; Five grades of driven gears and five grades of driving gear engagements also are equipped with the differential mechanism driven gear on the jack shaft, itself and differential gear mesh.
Double-clutch automatic gearbox power-transmitting unit according to the invention is owing to adopted the idle pulley of planetary pinion as first shaftgear; Reduced the spatial arrangement size of driving mechanism effectively; Make driving mechanism simpler; Level of integration is higher, thereby has to a certain degree reduced the manufacture cost of double-clutch automatic gearbox.
Below in conjunction with accompanying drawing the present invention is done further explain.
Description of drawings
Fig. 1 for the present invention at power intake along the power input shaft axial view;
Fig. 2 concerns schematic representation for dissecing a kind of power transmission that obtains along the A-A line among Fig. 1;
Fig. 3 concerns schematic representation for dissecing the another kind of power transmission that obtains along the A-A line among Fig. 1.
Embodiment
As Fig. 1, shown in Figure 2 be double clutch five gear transmission power-transmitting units; Comprise parallel layout and can be around the power input shaft 1 of self rotational, odd number shelves Clutch input shaft 30, first countershaft 10, second countershaft 5, jack shaft 9 and reverse idler gear axle 11; And odd number shelves clutch 28, even number shelves clutch 29 and differential mechanism 36; Jack shaft 9 is positioned at the centre of first countershaft 10 and second countershaft 5; Said even number shelves clutch 29 is installed on the power input shaft 1 and the left end of second countershaft 5; Odd number shelves clutch 28 is installed on the odd number shelves Clutch input shaft 30 and the left end of first countershaft 10; Left end at power input shaft 1 is equipped with sun gear 2, planetary pinion 3, ring gear 4 and fixing planet carrier 31, and ring gear 4 fixed outside have the ring gear external gear 37 coaxial with it, and ring gear external gear 37 is meshed with odd number shelves clutch driving gear 27.
Odd number shelves driving gear and odd number shelves synchronizer are installed on first countershaft 10; Odd number shelves driving gear comprises five grades of driving gears 17, third speed drive gear 16 and one grade of driving gear 8; It is installed on first countershaft 10 from left to right successively; Odd number shelves synchronizer comprises a Five-gear synchronizer 21 and a third gear synchronizer 13, and Five-gear synchronizer 21 is positioned at five grades of driving gear 17 left sides, and a third gear synchronizer 13 is between third speed drive gear 16 and one grade of driving gear 8.
Even number shelves driving gear, reverse driving gear 24 and even number shelves synchronizer are installed on second countershaft 5; Even number shelves driving gear comprises fourth gear driving gear 14 and second gear driving gear 6; It is installed on second countershaft 5 from left to right successively, is positioned at reverse driving gear 24 right sides, and even number shelves synchronizer comprises reverse gear synchronizer 20 and two fourth gear synchronizers 12; Reverse gear synchronizer 20 is positioned at reverse driving gear 24 left sides, and two fourth gear synchronizers 12 are between fourth gear driving gear 14 and second gear driving gear 6.
Driven gear and one or two reverse gear driven gears 7 are installed on the said jack shaft 9; Driven gear comprises five grades of driven gears 18 and three fourth gear driven gears 15; It is installed on the jack shaft 9 from left to right successively; Be positioned at one or two reverse gear driven gears, 7 left sides; Wherein one or two reverse gear driven gears 7 respectively with one grade of driving gear 8, second gear driving gear 6 and 34 engagements of reverse idler gear shaftgear, three fourth gear driven gears 15 respectively with third speed drive gear 16 and 14 engagements of fourth gear driving gear, five grades of driven gears 18 respectively with differential gear 26 engagements of five grades of driving gears 17 and differential mechanism 36.
The velocity ratio that the every pair of driving gear and driven gear produce has nothing in common with each other, such as, the velocity ratio of each gear can be chosen as:
One grade: 16.4; Second gear: 10.8; Third gear: 6.7; Fourth gear: 5; Five grades: 3.7; Reverse gear: 15.9.
The first reverse idler gear gear 25 and the second reverse idler gear gear 34 are installed on the said reverse idler gear axle 11 from left to right successively, and it meshes with reverse driving gear 24 and one or two reverse gear driven gears 7 respectively.
The power transmission line of these double clutch five gear transmission power-transmitting units is following:
During one grade of transmission of power:
One third gear synchronizer 13 engages with one grade of driving gear 8, odd number shelves clutch 28 engages, even number shelves clutch 29 separates; Be delivered to the power of input shaft 1 from motor; Be delivered to (1 grade) on the ring gear external gear 37 through sun gear 2, planet wheel 3, ring gear 4; Ring gear external gear 37 with transmission of power to odd number shelves clutch driving gear 27; At this moment, one grade of driving gear 8, a third gear synchronizer 13, first countershaft 10 are combined together synchronously, and power is delivered to (2 grades) on the odd number shelves Clutch input shaft 30 through odd number shelves clutch driving gear 27; All the other gear driving gears are in idling conditions, and power is delivered to (3 grades) on one or the two reverse gear driven gears 7 through one grade of driving gear 8 then; Power from one or two reverse gear driven gears 7 behind jack shaft 9, again through five grades of driven gears 18 with transmission of power to differential gear 26 the most at last transmission of power to differential mechanism 36 (4 grades).At this moment, transmitting progression is level Four.
During the second gear transmission of power:
Two fourth gear synchronizers 12 engage with second gear driving gear 6, even number shelves clutch 29 engages, odd number shelves clutch 28 separates; The transmission of power that is delivered to power input shaft 1 from motor is to even number shelves clutch 29; At this moment; Second gear driving gear 6, two fourth gear synchronizers 12, second countershaft 5 are combined together synchronously, with the transmission of power of motor to second countershaft 5; All the other gear driving gears are in idling conditions, and power is delivered to (1 grade) on one or the two reverse gear driven gears 7 through second gear driving gear 6 then; Power from one or two reverse gear driven gears 7 to jack shaft 9 again through five grades of driven gears 18 with transmission of power to differential gear 26 the most at last transmission of power to differential mechanism 36 (2 grades).At this moment, transmitting progression is secondary.
During the third gear transmission of power:
One third gear synchronizer 13 engages with third speed drive gear 16, odd number shelves clutch 28 engages, even number shelves clutch 29 separates; Be delivered to the power of input shaft 1 from motor; Be delivered to (1 grade) on the ring gear external gear 37 through sun gear 2, planet wheel 3, ring gear 4; Ring gear external gear 37 with transmission of power to odd number shelves clutch driving gear 27; At this moment, third speed drive gear 16, a third gear synchronizer 13, odd number shelves Clutch input shaft 30 are combined together synchronously, accomplish power and are delivered to (2 grades) on first countershaft 10 through odd number shelves clutch driving gear 27; All the other gear driving gears are in idling conditions, and power is delivered to (3 grades) on the three fourth gear driven gears 15 through third speed drive gear 16 then; Power from three fourth gear driven gears 15 to jack shaft 9 again through five grades of driven gears 18 with transmission of power to differential gear 26 the most at last transmission of power to differential mechanism 36 (4 grades).At this moment, transmitting progression is level Four.
During the fourth gear transmission of power:
Two fourth gear synchronizers 12 engage with fourth gear driving gear 14, even number shelves clutch 29 engages, odd number shelves clutch 28 separates; The transmission of power that is delivered to power input shaft 1 from motor is to even number shelves clutch 29; At this moment; Fourth gear driving gear 14, two fourth gear synchronizers 12, second countershaft 5 are combined together synchronously, accomplish power and are delivered on second countershaft 5 through even number shelves clutch 29; All the other gear driving gears are in idling conditions, and power is delivered to (1 grade) on the three fourth gear driven gears 15 through fourth gear driving gear 14 then; Power from three fourth gear driven gears 15 to jack shaft 9 again through five grades of driven gears 18 with transmission of power to differential gear 26 the most at last transmission of power to differential mechanism 36 (2 grades).At this moment, transmitting progression is secondary.
During five grades of transmission of power:
Five-gear synchronizer 21 engages with five grades of driving gears 17, odd number shelves clutch 28 engages, even number shelves clutch 29 separates; Be delivered to the power of input shaft 1 from motor; Be delivered to (1 grade) on the ring gear external gear 37 through sun gear 2, planet wheel 3, ring gear 4; Ring gear external gear 37 with transmission of power to odd number shelves clutch driving gear 27; At this moment, five grades of driving gears 17, Five-gear synchronizer 21, odd number shelves Clutch input shafts 30 are combined together synchronously, accomplish power and are delivered to (2 grades) on first countershaft 10 through odd number shelves clutch driving gear 27; All the other gear driving gears are in idling conditions, and power is delivered to (3 grades) on five grades of driven gears 18 through five grades of driving gears 17 then; Power through five grades of driven gears 18 with transmission of power to differential gear 26 the most at last transmission of power to differential mechanism 36 (4 grades).At this moment, transmitting progression is level Four.
During the reverse gear transmission of power:
Reverse gear synchronizer 20 engages with reverse driving gear 24, even number shelves clutch 29 engages, odd number shelves clutch 28 separates; The transmission of power that is delivered to power input shaft 1 from motor is to even number shelves clutch 29; At this moment; Reverse driving gear 24, reverse gear synchronizer 20, second countershaft 5 are combined together synchronously, accomplish power and are delivered on second countershaft 5 through even number shelves clutch 29; All the other gear driving gears are in idling conditions, and power is delivered on the reverse idler gear 25 through reverse driving gear 24 then, and reverse idler gear 25 passes through reverse idler gear axle 11 with transmission of power (1 grade) to reverse idler gear shaftgear 34; Reverse idler gear shaftgear 34 is with on transmission of power to the one two reverse gear driven gears 7 (2 grades); Power from one or two reverse gear driven gears 7 to jack shaft 9 again through five grades of driven gears 18 with transmission of power to differential gear 26 the most at last transmission of power to differential mechanism 36 (3 grades).At this moment, transmitting progression is three grades.
During gear shift:
When above-mentioned any one gear engaged, but the next gear of preliminary election (the corresponding synchronous device is cooperated with shifting gear accordingly) is the switching of clutch during gear shift, and gear shift is accomplished under the unbroken situation of transmission of power.
Double clutch five gear transmission power-transmitting units as shown in Figure 3 are installed a differential mechanism driven gear 118 on jack shaft 9, itself and differential gear 26 mesh, and other structure is identical with above-mentioned mode of execution.Changed the position of differential mechanism 36 relative other gear trains like this, the transmission that helps under the special construction condition is arranged.
Claims (5)
1. double-clutch automatic gearbox power-transmitting unit; Comprise power input shaft (1), odd number shelves Clutch input shaft (30), odd number shelves clutch (28), even number shelves clutch (29) and differential mechanism (36); It is characterized in that: also comprise first countershaft (10), second countershaft (5), jack shaft (9) and the reverse idler gear axle (11) parallel with power input shaft and odd number shelves Clutch input shaft; Jack shaft is positioned at the centre of first countershaft and second countershaft; Said even number shelves clutch (29) is installed on the power input shaft (1) and the left end of second countershaft (5); Odd number shelves clutch (28) is installed on the odd number shelves Clutch input shaft (30) and the left end of first countershaft (10); Left end at power input shaft (1) is equipped with sun gear (2), planetary pinion (3), ring gear (4) and fixing planet carrier (31); Ring gear (3) fixed outside has the ring gear external gear (37) coaxial with it, and the ring gear external gear is meshed with odd number shelves clutch driving gear (27);
Odd number shelves driving gear and odd number shelves synchronizer are installed on first countershaft (10), even number shelves driving gear, reverse driving gear (24) and even number shelves synchronizer are installed on second countershaft (5);
Driven gear and one or two reverse gear driven gears (7) with the engagement of even number shelves driving gear and odd number shelves driving gear are installed on the jack shaft (9), and wherein the differential gear (26) of driven gear and differential mechanism (36) meshes;
The first reverse idler gear gear (25) and the second reverse idler gear gear (34) are installed on the said reverse idler gear axle (11) from left to right successively, and it meshes with reverse driving gear (24) and one or two reverse gear driven gears (7) respectively.
2. according to the said double-clutch automatic gearbox power-transmitting unit of claim 1; It is characterized in that: said odd number shelves driving gear comprises five grades of driving gears (17), third speed drive gear (16) and one grade of driving gear (8); It is installed on first countershaft (10) from left to right successively; Said odd number shelves synchronizer comprises a Five-gear synchronizer (21) and a third gear synchronizer (13); Five-gear synchronizer (21) is positioned at five grades of driving gear left sides, and a third gear synchronizer (13) is positioned between third speed drive gear (16) and the one grade of driving gear (8).
3. according to the said double-clutch automatic gearbox power-transmitting unit of claim 1; It is characterized in that: said even number shelves driving gear comprises fourth gear driving gear (14) and second gear driving gear (6); It is installed on second countershaft (5) from left to right successively; Be positioned at reverse driving gear (24) right side; Said even number shelves synchronizer comprises reverse gear synchronizer (20) and two fourth gear synchronizers (12), and reverse gear synchronizer (20) is positioned at reverse driving gear (24) left side, and two fourth gear synchronizers (12) are positioned between fourth gear driving gear (14) and the second gear driving gear (6).
4. according to the said double-clutch automatic gearbox power-transmitting unit of claim 1; It is characterized in that: the driven gear on the said jack shaft (9) comprises five grades of driven gears (18) and three fourth gear driven gears (15); It is installed on the jack shaft (9) from left to right successively; Be positioned at one or two reverse gear driven gears (7) left side; Wherein one or two reverse gear driven gears mesh with one grade of driving gear (8), second gear driving gear (6) and reverse idler gear shaftgear (34) respectively; Three fourth gear driven gears (15) mesh with third speed drive gear (16) and fourth gear driving gear (14) respectively, and five grades of driven gears (18) mesh with five grades of driving gears (17) engagement and differential gear (26) respectively.
5. according to the said double-clutch automatic gearbox power-transmitting unit of claim 1; It is characterized in that: the driven gear on the said jack shaft (9) comprises five grades of driven gears (18) and three fourth gear driven gears (15); It is installed on the jack shaft (9) from left to right successively; Be positioned at one or two reverse gear driven gears (7) left side; Wherein one or two reverse gear driven gears mesh with one grade of driving gear (8), second gear driving gear (6) and reverse idler gear shaftgear (34) respectively, and three fourth gear driven gears (15) mesh with third speed drive gear (16) and fourth gear driving gear (14) respectively, five grades of driven gears (18) and five grades of driving gears (17) engagement; Differential mechanism driven gear (118) also is installed on the jack shaft (9), and itself and differential gear (26) mesh.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011103899612A CN102425647B (en) | 2011-11-30 | 2011-11-30 | Power transmission mechanism for double-clutch automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011103899612A CN102425647B (en) | 2011-11-30 | 2011-11-30 | Power transmission mechanism for double-clutch automatic transmission |
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| CN102425647A true CN102425647A (en) | 2012-04-25 |
| CN102425647B CN102425647B (en) | 2013-12-04 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2011103899612A Active CN102425647B (en) | 2011-11-30 | 2011-11-30 | Power transmission mechanism for double-clutch automatic transmission |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103821897A (en) * | 2014-03-14 | 2014-05-28 | 上海交通大学 | Single row planetary gear train two-gear automatic mechanical transmission for electrocar |
| CN108162741A (en) * | 2017-12-22 | 2018-06-15 | 重庆蓝黛动力传动机械股份有限公司 | A kind of hybrid vehicle speed changing structure |
| CN108162743A (en) * | 2017-12-22 | 2018-06-15 | 重庆蓝黛动力传动机械股份有限公司 | A kind of hybrid vehicle speed change gear |
| CN109630566A (en) * | 2019-01-30 | 2019-04-16 | 陈奇 | A kind of wet clutch unit assembly |
| CN109723769A (en) * | 2019-03-08 | 2019-05-07 | 重庆青山工业有限责任公司 | The two reduction gear of pure electric vehicle retarder |
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| CN101655141A (en) * | 2009-09-21 | 2010-02-24 | 重庆青山工业有限责任公司 | Double-clutch transmission |
| CN102128236A (en) * | 2010-01-12 | 2011-07-20 | 博格华纳公司 | DCT transmission utilizing a two axis chain |
| CN202349120U (en) * | 2011-11-30 | 2012-07-25 | 重庆青山工业有限责任公司 | Power transmission mechanism of automobile transmission |
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| WO2006032789A1 (en) * | 2004-09-23 | 2006-03-30 | Antonov Automotive Technologies Bv | Double-clutch gearbox, in particular for motor vehicle |
| CN101089420A (en) * | 2006-06-16 | 2007-12-19 | 比亚迪股份有限公司 | Double-clutch automatic transmission mechanism |
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Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103821897A (en) * | 2014-03-14 | 2014-05-28 | 上海交通大学 | Single row planetary gear train two-gear automatic mechanical transmission for electrocar |
| CN103821897B (en) * | 2014-03-14 | 2016-08-03 | 上海交通大学 | Electric motor car two grades of automatic speed changer for machine of single planet circular system |
| CN108162741A (en) * | 2017-12-22 | 2018-06-15 | 重庆蓝黛动力传动机械股份有限公司 | A kind of hybrid vehicle speed changing structure |
| CN108162743A (en) * | 2017-12-22 | 2018-06-15 | 重庆蓝黛动力传动机械股份有限公司 | A kind of hybrid vehicle speed change gear |
| CN108162743B (en) * | 2017-12-22 | 2023-08-04 | 蓝黛科技集团股份有限公司 | Speed variator for hybrid power vehicle |
| CN108162741B (en) * | 2017-12-22 | 2023-08-04 | 蓝黛科技集团股份有限公司 | Speed change structure of hybrid power vehicle |
| CN109630566A (en) * | 2019-01-30 | 2019-04-16 | 陈奇 | A kind of wet clutch unit assembly |
| CN109630566B (en) * | 2019-01-30 | 2024-04-05 | 浙江海天机械有限公司 | Wet clutch unit assembly |
| CN109723769A (en) * | 2019-03-08 | 2019-05-07 | 重庆青山工业有限责任公司 | The two reduction gear of pure electric vehicle retarder |
| CN109723769B (en) * | 2019-03-08 | 2023-07-21 | 重庆青山工业有限责任公司 | Two-stage speed reducing mechanism of pure electric vehicle speed reducer |
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|---|---|
| CN102425647B (en) | 2013-12-04 |
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Effective date of registration: 20181214 Address after: 230001 No. 966 Dabieshan Road, Hefei High-tech Zone, Anhui Province Co-patentee after: Qingshan Industry Co., Ltd., Chongqing Patentee after: Hefei Changan Automobile Co., Ltd. Address before: 402761 Qingba Town, Bishan County, Chongqing Patentee before: Qingshan Industry Co., Ltd., Chongqing |
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