CN103148175B - Automobile dual-clutch automatic transmission - Google Patents
Automobile dual-clutch automatic transmission Download PDFInfo
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- CN103148175B CN103148175B CN201310062441.XA CN201310062441A CN103148175B CN 103148175 B CN103148175 B CN 103148175B CN 201310062441 A CN201310062441 A CN 201310062441A CN 103148175 B CN103148175 B CN 103148175B
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Abstract
The invention provides a kind of automobile dual-clutch automatic transmission, belong to mechanical engineering technical field.It solve existing speed changer and there is many association gears, cause there is complex structure, arrange in disorder problem.This automobile dual-clutch automatic transmission, has and comprises seven forward gearss and a reverse gear; Comprise clutch one, clutch two, solid input shaft, hollow input shaft, the axle that advances, advance two axles, reverse gear shaft and have the differential mechanism of main reduction gear ring; Advance on two axles and be positioned with four forward gear, above-mentioned four forward gear with on solid input shaft and hollow input shaft totally four driving gears be meshed correspondingly; Reverse gear shaft is positioned with a reverse gear.This automobile dual-clutch automatic transmission only has five layers of gear driving pair layer, at least reduces two-layer gear driving pair layer; Shorten the axial arranged size of geared portions thus to greatest extent, effectively ensure that the carried performance of this automatic transmission.
Description
Technical field
The invention belongs to mechanical engineering technical field, relate to a kind of automatic transmission, particularly a kind of automobile dual-clutch automatic transmission.
Background technique
Speed changer is the device changing automobile runs speed or tractive force.Along with the pollution to environment day by day increasing the weight of in the continuous minimizing of production-goods source oil and vehicle exhaust, various countries to the oil consumption of automobile and emission regulation demands more and more tighter.The transmission efficiency of transmission system strengthens automobile fuel consumption impact, develops the emphasis that energy-efficient automatic transmission has become the research and development of domestic and international car enterprise.Traditional automatic transmission AT and CVT (continuously variable transmission) CVT is because have employed the lower fluid torque converter of transmission efficiency, and comprehensive transmission efficiency is the highest can only reach about 85%, and the transmission efficiency of double-clutch automatic gearbox can reach more than 93%.The car load carrying double-clutch automatic gearbox presents quick growth trend in recent years, and the green grass or young crops being subject to increasing Consumer narrows.
With regard to power character, gear number is more, adds motor and plays high-power chance near peak output, improve acceleration and the grade ability of automobile; With regard to fuel economy, gear number is more, adds motor in low fuel consumption rate district work possibility, reduces oil consumption; With regard to gear shift travelling comfort, gear number is more, and the rank between each shelves are than less, and gear shift is easier; With regard to lift-launch property, gear number is more, and the axial arranged space of needs is larger, and lift-launch property is poorer.Therefore, design many gears, the short double-clutch automatic gearbox of axial dimension is the trend of future development.
Pertinent literature about double-clutch automatic gearbox is more, a kind of double-clutch automatic transmission without reverse gear shaft [application number: 200910311888.X disclosed in Chinese patent literature; Notification number: CN101907150B], comprise clutch one, clutch two, input an axle, input two axles, export an axle, export two axles and differential mechanism; Input each gear driving gear on an axle and input two axles to divide by idol, odd gear, form each shelves speed with output one axle and the corresponding driven gear exported on two axles respectively and export; Each shelves speed comprises seven forward gearss and a reverse gear; In seven forward gearss, two the even number shelves inputted on an axle share a driving gear, and two the odd number shelves inputted on two axles share another driving gear; Reverse gear comprises a reverse driving gear associated with low-grade driven gear and the reverse gear driven gear engaged with reverse driving gear, and reverse driving gear is located on output one axle, and reverse gear driven gear is located on output two axle.Although this speed changer can practical function, from structure, this speed changer has seven layers of gear driving pair from clutch to the other end, namely there is the problem that axial arranged requisite space is large.This speed changer also also exists many association gears, causes there is complex structure, arranges in disorder problem.
Summary of the invention
The object of the invention is to there are the problems referred to above for existing technology, propose a kind of automobile dual-clutch automatic transmission, this automatic transmission technical issues that need to address how to shorten the axial arranged size of geared portions to greatest extent.
Object of the present invention realizes by following technical proposal: a kind of automobile dual-clutch automatic transmission, has and comprises seven forward gearss and a reverse gear; It is characterized in that, comprise clutch one, clutch two, solid input shaft, hollow input shaft, the axle that advances, advance two axles, reverse gear shaft and have the differential mechanism of main reduction gear ring; Described hollow input shaft is set on solid input shaft, and described solid input shaft is connected with clutch one, and described hollow input shaft is connected with clutch two; Described advance one axle, advance two axles and reverse gear shaft are all fixed with the connection gear engaged with main reduction gear ring; Described solid input shaft and hollow input shaft are all fixed with two driving gears; Described advance one axle is positioned with three forward gear, and above-mentioned two forward gear are meshed correspondingly with the driving gear of two on solid input shaft, and another forward gear is meshed with the driving gear of on hollow input shaft; Described advance two axle is positioned with four forward gear, above-mentioned four forward gear with on solid input shaft and hollow input shaft totally four driving gears be meshed correspondingly; Described reverse gear shaft is positioned with a reverse gear, above-mentioned reverse gear is meshed with advance one axle or the advance low regime clutch advanced on two axles.
This automobile dual-clutch automatic transmission only has from structure and connects gear and transmission layer between main reduction gear ring and the transmission layer between four driving gears with corresponding advance shifting gear, therefore shorten the axial arranged size of geared portions to greatest extent, effectively ensure that the carried performance of this automatic transmission.
In above-mentioned automobile dual-clutch automatic transmission, a driving gear on described solid input shaft is 1/3 grade of driving gear, and another driving gear is 5/7 grade of driving gear.
In above-mentioned automobile dual-clutch automatic transmission, a driving gear on described hollow input shaft is 2 grades of driving gears, and another driving gear is 4/6 grade of driving gear.
In above-mentioned automobile dual-clutch automatic transmission, the axis of three forward gear edge advance one axles that described advance one axle is located passes through and is followed successively by advance 3 grades of gears, advance 7 grades of gears and the 4 grades of gears that advance.
In above-mentioned automobile dual-clutch automatic transmission, the axis of four forward gear edge advance two axles that described advance two axle is located passes through and is followed successively by advance 1 grade of gear, advance 5 grades of gears, advance 6 grades of gears and the 2 grades of gears that advance.
In above-mentioned automobile dual-clutch automatic transmission, described advance low regime clutch is advance 1 grade of gear or the 2 grades of gears that advance.
In above-mentioned automobile dual-clutch automatic transmission, described advance one axle is also fixedly connected with parking ratchet wheel.
In above-mentioned automobile dual-clutch automatic transmission, described parking ratchet wheel is at connection gear and advance between 4 grades of gears.
This automobile dual-clutch automatic transmission needs to arrange the synchronizer corresponding with forward gear, realizes respective notch transmission by manipulating synchronizer accordingly.The preferred version that synchronizer of the present invention is arranged is: in above-mentioned automobile dual-clutch automatic transmission, is provided with 3/7 grade of synchronizer between described advance 3 grades of gears and advance 7 grades of gears; Advance between 2 grades of gears and advance 6 grades of gears and be provided with 2/6 grade of synchronizer; Advance between 1 grade of gear and advance 5 grades of gears and be provided with 1/5 grade of synchronizer; The side of described advance 4 grades of gears is provided with monolateral joint 4 grades of synchronizers; The side of reverse gear is provided with monolateral engaged reverse synchronizer.
In above-mentioned automobile dual-clutch automatic transmission, described advance one axle, advance two axles and reverse gear shaft are all positioned at the outside of main reduction gear ring, and set gradually along main reduction gear ring circumference; Described hollow input shaft, advance an axle and advance two axles be acute triangle layout.
This automobile dual-clutch automatic transmission only has five layers of gear driving pair layer, compared with prior art, at least reduces two-layer gear driving pair layer; Shorten the axial arranged size of geared portions thus to greatest extent, effectively ensure that the carried performance of this automatic transmission.
This automobile dual-clutch automatic transmission has the advantage of connection and reasonable arrangement and compact structure.Simultaneously by parking ratchet wheel step on output shaft, more effectively improve structural compactness thus.
Accompanying drawing explanation
Fig. 1 is the structural representation of this automobile dual-clutch automatic transmission.
Fig. 2 is the layout schematic diagram of this automobile dual-clutch automatic transmission.
In figure, 1, solid input shaft; 2, hollow input shaft; 3, advance an axle; 4, advance two axles; 5, reverse gear shaft; 6, differential mechanism; 7,5/7 grade of driving gear; 8,2 grades of driving gears; 9,1/3 grade of driving gear; 10,4/6 grade of driving gear; 11, gear one is connected; 12, gear two is connected; 13, gear three is connected; 14, main reduction gear ring; G1, advance 1 grade of gear; G2, advance 2 grades of gears; G3, advance 3 grades of gears; G4, advance 4 grades of gears; G5, advance 5 grades of gears; G6, advance 6 grades of gears; G7, advance 7 grades of gears; GR, reverse gear; P, parking ratchet wheel; S1,3/7 grade of synchronizer; S2,2/6 grade of synchronizer; S3, monolateral joint 4 grades of synchronizers; S4,1/5 grade of synchronizer; S5, monolateral engaged reverse synchronizer; K1, clutch one; K2, clutch two.
Embodiment
Be below specific embodiments of the invention and by reference to the accompanying drawings, technological scheme of the present invention is further described, but the present invention be not limited to these embodiments.
As shown in Figure 1, this automobile dual-clutch automatic transmission has and comprises seven forward gearss and a reverse gear.This automobile dual-clutch automatic transmission comprises clutch one K1, clutch two K2, solid input shaft 1, hollow input shaft 2, the axle 3 that advances, advance two axles 4, reverse gear shaft 5 and have the differential mechanism 6 of main reduction gear ring 14; This automobile dual-clutch automatic transmission also comprises seven forward gear, reverse gear GR, four driving gears are connected gear with three.
Specifically, hollow input shaft 2 is set on an end of solid input shaft 1, and solid input shaft 1 is connected with clutch one K1, and hollow input shaft 2 is connected with clutch two K2; Clutch one K1 and clutch two K2 can alternately transmit operation power, realizes gear switch.
An advance axle 3, advance two axles 4 and reverse gear shaft 5 all be arranged in parallel with hollow input shaft 2; In order to implementation structure compactedness, the axle 3 that advances is fixed with near one end of clutch and connects gear 1, and two axles 4 that advance are fixed with near one end of clutch and connect gear 2 12, and reverse gear shaft 5 is fixed with near one end of clutch and connects gear 3 13; Above-mentioned three connection gears all engage with main reduction gear ring 14; Therefore differential mechanism 6 is arranged relative to being connected gear homonymy with clutch.
Two driving gears are fixed on solid input shaft 1, and another two driving gears are all fixed on hollow input shaft 2.In order to more reasonable distribution outputting power and driving gear divide by even, odd gear, then the size of four driving gears is completely not identical, is followed successively by 1/3 grade of driving gear, 9,2 grades of driving gears, 8,5/7 grade of driving gear 7 and 4/6 grade of driving gear 10 from minimum to maximum.A driving gear on solid input shaft 1 is 1/3 grade of driving gear 9, and another driving gear is 5/7 grade of driving gear 7.A driving gear on hollow input shaft 2 is 2 grades of driving gears 8, and another driving gear is 4/6 grade of driving gear 10.
Three forward gear are positioned on advance one axle 3, and two forward gear wherein in above-mentioned three forward gear, another forward gear is meshed with a driving gear on hollow input shaft 2.More particularly, three forward gear of location on an axle 3 of advancing pass through along the axis of the axles 3 that advance and are followed successively by advance 3 grades of gear G3, advance 7 grades of gear G7 and the 4 grades of gear G4 that advance.Thus, on solid input shaft 1 two driving gears and hollow input shaft 2 to put two driving gear positions corresponding with three forward gear positions of advancing on an axle 3.
Four forward gear are positioned on advance two axle 4, four forward gear with on solid input shaft 1 and hollow input shaft 2 totally four driving gears be meshed correspondingly.Four forward gear of location on two axles 4 of then advancing pass through along the axis of two axles 4 that advance and are followed successively by advance 1 grade of gear G1, the 5 grades of gear G5 that advance, advance 6 grades of gear G6 and the 2 grades of gear G2 that advance.
Reverse gear GR is positioned on reverse gear shaft 5, and above-mentioned reverse gear GR is meshed with advance one axle 3 or the advance low regime clutch advanced on two axles 4.More particularly, advance low regime clutch is advance 1 grade of gear G1 or the 2 grades of gear G2 that advance.As described in Figure 1, reverse gear GR and advance 2 grades of gear G2 are meshed.Advance 2 grades of gear G2 near clutch, effectively shortens the length of reverse gear shaft 5 and take up room needed for reducing.
Advance on an axle 3 and be also fixedly connected with parking ratchet wheel P.From structure, position corresponding with 2 grades of driving gears 8 on the axle 3 that advances is empty; Then parking ratchet wheel P is arranged in above-mentioned position, namely parking ratchet wheel P is between connection gear 1 and advance 4 grades of gear G4.
In order to ensure compactedness structurally, the axle 3 that advances, advance two axles 4 and reverse gear shaft 5 are all positioned at the outside of main reduction gear ring 14, and set gradually along main reduction gear ring 14 circumference; Hollow input shaft 2, advance an axle 3 and two axles 4 that advance are arranged in acute triangle.
Advance between 3 grades of gear G3 and advance 7 grades of gear G7 and be provided with 3/7 grade of synchronizer S1; Advance between 2 grades of gear G2 and advance 6 grades of gear G6 and be provided with 2/6 grade of synchronizer S2; Advance between 1 grade of gear G1 and advance 5 grades of gear G5 and be provided with 1/5 grade of synchronizer S4; The side of advance 4 grades of gear G4 is provided with monolateral joint 4 grades of synchronizer S3; The side of reverse gear GR is provided with monolateral engaged reverse synchronizer S5.
As shown in Figure 1, power transmission line of the present invention illustrates:
When automobile is in parked state, park pawl is meshed with parking ratchet wheel P; Clutch one K1, clutch two K2 often leave, and are namely in separated state, not transferring power at two clutches at ordinary times, and only have when needing to hang corresponding gear, corresponding clutch just engages, transferring power.
When automobile needs one grade of starting, 1/5 grade of synchronizer S4 and advance 1 grade of gear G1 engages by self-clanging gear-shift, and gear switch is one grade, and clutch one K1 combines, and clutch two K2 remains open state, and automobile starts with one grade of operation.Then one grade of power transmission line: power passes to solid input shaft 1 through clutch one K1, advance 1 grade of gear G1 is passed to by 1/3 grade of driving gear 9 on solid input shaft 1, advance two axle 4 is passed to through 1/5 grade of synchronizer S4, passing to the main reduction gear ring 14 of differential mechanism 6 through connecting gear 2 12, eventually through differential mechanism 6, transmission of power being gone out.
Automobile one grade run time because now clutch two K2 is in separated state, not transferring power, when automobile accelerates, when reaching the shift point close to second gear, gear can be changed to second gear by self-clanging gear-shift in advance, engage by 2/6 grade of synchronizer S2 and advance 2 grades of gear G2, then clutch one K1 unclamps, and clutch two K2 engages, and two clutches alternately switch, until clutch one K1 is separated completely, clutch two K2 combines completely, and whole gearshift procedure terminates, and automobile changes to second gear.
Second gear power transmission line: power passes to hollow input shaft 2,2 grades of driving gears 8 successively through clutch two K2, the 2 grades of gear G2 of advancing, 2/6 grade of synchronizer S2, two axles 4 that advance, connect the main reduction gear ring 14 of gear 2 12, differential mechanism 6, eventually through differential mechanism 6, transmission of power is gone out.
After vehicle enters second gear operation, vehicular automatic transmission ECU (Electrical Control Unit) can know vehicle current operating conditions according to relevant sensor signals, and then judge that vehicle is about to enter the gear of operation, if vehicle acceleration, then next gear is third gear, if vehicle deceleration, then next gear is one grade.And one grade controls by clutch one K1 with third gear, because this clutch is in separated state, not transferring power, therefore the substitution in advance very easily of instruction self-clanging gear-shift can be about to the gear of the work of entering, when vehicle operating reaches shift point, only need clutch two K2 worked to be separated, clutch one K1 engages simultaneously, work good the switching sequence of two clutches, whole gear shift action all completes.The handoff procedure of other advance gear is also like this; Below just no longer burden statement.
Introduce the detailed power transmission line of all the other gears below respectively.
Third gear power transmission line: power passes to solid input shaft 1,1/3 grade of driving gear 9 successively through clutch one K1, the 3 grades of gear G3 of advancing, 3/7 grade of synchronizer S1, the axle 3 that advances, connect the main reduction gear ring 14 of gear 1, differential mechanism 6, eventually through differential mechanism 6, transmission of power is gone out.
Fourth gear power transmission line: power passes to the main reduction gear ring 14 of hollow input shaft 2,4/6 grade of driving gear 10, advance 4 grades of gear G4, monolateral joint 4 grades of synchronizer S3, the axle 3 that advances, connection gear 1, differential mechanism 6 successively through clutch two K2, eventually through differential mechanism 6, transmission of power is gone out.
Five grades of power transmission lines: power passes to solid input shaft 1,5/7 grade of driving gear 7 successively through clutch one K1, the 5 grades of gear G5 of advancing, 1/5 grade of synchronizer S4, two axles 4 that advance, connect the main reduction gear ring 14 of gear 2 12, differential mechanism 6, eventually through differential mechanism 6, transmission of power is gone out.
Six grades of power transmission lines: power passes to hollow input shaft 2,4/6 grade of driving gear 10 successively through clutch two K2, the 6 grades of gear G6 of advancing, 2/6 grade of synchronizer S2, two axles 4 that advance, connect the main reduction gear ring 14 of gear 2 12, differential mechanism 6, eventually through differential mechanism 6, transmission of power is gone out.
Seven grades of power transmission lines: power passes to solid input shaft 1,5/7 grade of driving gear 7 successively through clutch one K1, the 7 grades of gear G7 of advancing, 3/7 grade of synchronizer S1, the axle 3 that advances, connect the main reduction gear ring 14 of gear 1, differential mechanism 6, eventually through differential mechanism 6, transmission of power is gone out.
Reverse gear power transmission line: power passes to the main reduction gear ring 14 of hollow input shaft 2,2 grades of driving gears 8, advance 2 grades of gear G2, reverse gear GR, monolateral engaged reverse synchronizer S5, reverse gear shaft 5, connection gear 3 13, differential mechanism 6 successively through clutch two K2, eventually through differential mechanism 6, transmission of power is gone out.During this state, the 2 grades of gear G2 that advance are reverse intermediate idler of reverse gear.
Specific embodiment described herein is only to the explanation for example of the present invention's spirit.Those skilled in the art can make various amendment or supplement or adopt similar mode to substitute to described specific embodiment, but can't depart from spirit of the present invention or surmount the scope that appended claims defines.
Claims (7)
1. an automobile dual-clutch automatic transmission, has and comprises seven forward gearss and a reverse gear, it is characterized in that, comprise clutch one (K1), clutch two (K2), solid input shaft (1), hollow input shaft (2), the axle (3) that advances, two axles (4) that advance, reverse gear shaft (5) and there is the differential mechanism (6) of main reduction gear ring (14), described hollow input shaft (2) is set on solid input shaft (1), described solid input shaft (1) is connected with clutch one (K1), and described hollow input shaft (2) is connected with clutch two (K2), described advance one axle (3), advance two axles (4) and reverse gear shaft (5) are all fixed with the connection gear engaged with main reduction gear ring (14), described solid input shaft (1) and hollow input shaft (2) are all fixed with two driving gears, a driving gear on described solid input shaft (1) is 1/3 grade of driving gear (9), another driving gear is 5/7 grade of driving gear (7), a driving gear on described hollow input shaft (2) is 2 grades of driving gears (8), another driving gear is 4/6 grade of driving gear (10), the size of four driving gears is completely not identical, 1/3 grade of driving gear (9) is followed successively by from minimum to maximum, 2 grades of driving gears (8), 5/7 grade of driving gear (7) and 4/6 grade of driving gear (10), described advance one axle (3) is positioned with three forward gear, above-mentioned two forward gear are meshed correspondingly with two driving gears on solid input shaft (1), another forward gear is meshed with a driving gear on hollow input shaft (2), described advance two axle (4) is positioned with four forward gear, above-mentioned four forward gear with on solid input shaft (1) and hollow input shaft (2) totally four driving gears be meshed correspondingly, described reverse gear shaft (5) is positioned with a reverse gear (GR), above-mentioned reverse gear (GR) is meshed with advance one axle (3) or the advance low regime clutch advanced on two axles (4), described advance one axle (3), advance two axles (4) and reverse gear shaft (5) are all positioned at the outside of main reduction gear ring (14), and set gradually along main reduction gear ring (14) circumference, described hollow input shaft (2), advance an axle (3) and advance two axles (4) arrange in acute triangle.
2. automobile dual-clutch automatic transmission according to claim 1, it is characterized in that, the axis of three forward gear edge advance one axle (3) of the upper location of described advance one axle (3) passes through and is followed successively by advance 3 grades of gears (G3), advance 7 grades of gears (G7) and 4 grades of gears (G4) of advancing.
3. automobile dual-clutch automatic transmission according to claim 1, it is characterized in that, the axis of four forward gear edge advance two axles (4) that described advance two axle (4) is above located passes through and is followed successively by advance 1 grade of gear (G1), advance 5 grades of gears (G5), advance 6 grades of gears (G6) and advance 2 grades of gears (G2).
4. automobile dual-clutch automatic transmission according to claim 1, is characterized in that, described advance low regime clutch is advance 1 grade of gear (G1) or 2 grades of gears (G2) of advancing.
5. automobile dual-clutch automatic transmission according to claim 1, is characterized in that, described advance one axle (3) is also fixedly connected with parking ratchet wheel (P).
6. automobile dual-clutch automatic transmission according to claim 5, is characterized in that, described parking ratchet wheel (P) is positioned at and connects gear and advance between 4 grades of gears (G4).
7. automobile dual-clutch automatic transmission according to claim 1, is characterized in that, is provided with 3/7 grade of synchronizer (S1) between described advance 3 grades of gears (G3) and advance 7 grades of gears (G7); Advance between 2 grades of gears (G2) and advance 6 grades of gears (G6) and be provided with 2/6 grade of synchronizer (S2); Advance between 1 grade of gear (G1) and advance 5 grades of gears (G5) and be provided with 1/5 grade of synchronizer (S4); The side of described advance 4 grades of gears (G4) is provided with monolateral joint 4 grades of synchronizers (S3); The side of reverse gear (GR) is provided with monolateral engaged reverse synchronizer (S5).
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| CN201310062441.XA CN103148175B (en) | 2013-02-28 | 2013-02-28 | Automobile dual-clutch automatic transmission |
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| CN201310062441.XA CN103148175B (en) | 2013-02-28 | 2013-02-28 | Automobile dual-clutch automatic transmission |
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| CN103148175B true CN103148175B (en) | 2016-04-13 |
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Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103542044B (en) * | 2013-09-25 | 2016-12-07 | 浙江吉利控股集团有限公司 | A kind of double-clutch automatic gearbox for vehicle |
| CN103557322B (en) | 2013-10-16 | 2016-06-29 | 浙江吉利控股集团有限公司 | A kind of double-clutch automatic gearbox |
| KR101611056B1 (en) * | 2014-07-02 | 2016-04-21 | 현대자동차주식회사 | Automatic Manual Transmission |
| EP3006243B1 (en) * | 2014-10-06 | 2019-01-30 | Volvo Car Corporation | dual clutch transmission, hybrid vehicle and method for controlling a hybrid vehicle |
| KR101846871B1 (en) * | 2014-10-17 | 2018-04-09 | 현대자동차 주식회사 | Power transmission apparatus for vehicle |
| CN105736652A (en) * | 2016-04-21 | 2016-07-06 | 中国第一汽车股份有限公司 | Double-clutch type automatic transmission |
| DE102016210713A1 (en) * | 2016-06-16 | 2017-12-21 | Zf Friedrichshafen Ag | Transmission for a motor vehicle |
| CN107539103B (en) * | 2016-06-29 | 2020-07-10 | 比亚迪股份有限公司 | Power driving system and vehicle |
| CN111853170A (en) * | 2019-04-25 | 2020-10-30 | 广州汽车集团股份有限公司 | Eight-speed double-clutch type automatic transmission and vehicle |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101571181A (en) * | 2009-06-15 | 2009-11-04 | 上海汽车集团股份有限公司 | Double clutch gearbox |
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| DE10343991A1 (en) * | 2003-09-23 | 2005-05-04 | Zahnradfabrik Friedrichshafen | Manual transmission for motor vehicles, has input shaft comprising parts joined together via non rotary connection |
| EP2060827B1 (en) * | 2007-11-14 | 2011-09-07 | Getrag Ford Transmissions GmbH | Application of a dual clutch transmission in two different transmission types |
| WO2009121544A2 (en) * | 2008-03-31 | 2009-10-08 | Gm Global Technology Operations, Inc. | Double-clutch transmission for vehicles |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN101571181A (en) * | 2009-06-15 | 2009-11-04 | 上海汽车集团股份有限公司 | Double clutch gearbox |
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Effective date of registration: 20190318 Address after: 317000 east gate of Taizhou City, Zhejiang Province Co-patentee after: Zhejiang Geely Holding Group Co., Ltd. Patentee after: Zhejiang Geely Automobile Research Institute Co., Ltd. Address before: 311228 No. 206 Farmer's Second House in Linjiang Industrial Park, Xiaoshan District, Hangzhou City, Zhejiang Province Co-patentee before: Zhejiang Geely Automobile Research Institute Co., Ltd. Patentee before: Hangzhou Branch, Zhejiang Geely Automobile Research Institute Co., Ltd. Co-patentee before: Zhejiang Geely Holding Group Co., Ltd. |
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