WO2014069720A1 - 더블 클러치 변속기 구조 - Google Patents
더블 클러치 변속기 구조 Download PDFInfo
- Publication number
- WO2014069720A1 WO2014069720A1 PCT/KR2013/001242 KR2013001242W WO2014069720A1 WO 2014069720 A1 WO2014069720 A1 WO 2014069720A1 KR 2013001242 W KR2013001242 W KR 2013001242W WO 2014069720 A1 WO2014069720 A1 WO 2014069720A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- gear train
- output shaft
- gear
- input shaft
- double clutch
- Prior art date
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Classifications
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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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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K20/00—Arrangement or mounting of change-speed gearing control devices in vehicles
-
- 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
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/64—Gearings having three or more central gears composed of a number of gear trains, the drive always passing through all the trains, each train having not more than one connection for driving another train
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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
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
- F16H2003/0931—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output shaft
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19219—Interchangeably locked
- Y10T74/19228—Multiple concentric clutch shafts
Definitions
- the present invention relates to a double clutch transmission structure, and more particularly, by implementing a multi-stage of the gear stage using a minimum number of gear trains, not only minimizing the overall length but also minimizing the increase in the weight of the transmission, the eight-speed forward and reverse
- the present invention relates to a structure of a double clutch transmission capable of one-speed.
- DCT double clutch transmission
- the DCT is the same as the input shafts (hollow shafts) for transmitting power in parallel, the length of the transmission is reduced, and in particular, the transmission is made by using two clutches, and thus the transmission efficiency is excellent. That is, it is a transmission that separates the input shaft that transmits the power of the engine into two shafts, and arranges a single gear gear on one shaft, an even gear on another shaft, and alternately operates two clutches to achieve shifting. .
- the present invention has been made in view of the above-described problems, while minimizing the gear train used for shifting, it is possible to provide a double clutch transmission structure capable of minimizing the overall length as well as enabling forward 8-speed shifting and reverse 1-speed shifting. There is this.
- the present invention uses a four or five gear train and four synchro devices, the structure is simple to reduce the overall weight of the transmission, while providing a double clutch transmission structure capable of eight forward forward and one-speed forward shifting. have.
- the double clutch transmission structure for achieving the above object is a double clutch transmission structure that can be shifted to eight forward and one reverse, each of the first input shaft is a power transmission from the engine by the clutch And a second input shaft;
- An output shaft comprising a first output shaft and a second output shaft for outputting power from the first input shaft and the second input shaft;
- a third sink device installed on the first output shaft so as to be positioned between the row and the fourth gear row and synchronizing the third gear train and the fourth gear train to selectively transmit power;
- a second sink device installed on the second output shaft so as to be positioned
- the double clutch transmission structure according to Embodiment 2 of the present invention is the same as that of Embodiment 1, but is constructed by arranging the fifth gear train in a double row in the fourth gear train.
- first input shaft and the second input shaft is characterized in that disposed on the coaxial line in the form of a double tube using a hollow shaft.
- first to fourth gear train is characterized in that the external gear.
- the conventional double clutch transmission increases the overall length when the gear train is added to increase the number of gear shifts.
- the forward gear speed and the reverse speed are made by using four or five gear trains without increasing the overall length. Shifting becomes possible.
- FIG. 1 is a configuration diagram schematically showing an example in which a double clutch transmission structure according to Embodiment 1 of the present invention is applied.
- Figure 2 is a schematic diagram showing a configuration to show an example in which the double clutch transmission structure according to the second embodiment of the present invention is applied.
- the first and second input shaft (10a, 10b) selectively receives power from the engine (E / G), the first output shaft for outputting the shifted power ( 20a) and the second output shaft 20b, the first to fourth gear trains 30a to 30d provided between the input shafts and the output shafts to increase or decrease the rotational speed, for synchronizing the operation of these input shafts and the output shafts and gear trains.
- First to fourth sink devices 40a to 40d, and an output gear 50 for outputting the output of the output shaft to the differential device (Diff).
- the double clutch transmission structure according to the first embodiment of the present invention using four gear trains and four first to fourth synchro devices 40a to 40d to shift eight forward and one reverse gears. This would be possible.
- the first input shaft 10a and the second input shaft 10b are connected to the engine E / G to receive power. At this time, the power is selectively transmitted or interrupted by the clutches C1 and C2, respectively.
- FIG. 1 shows an example in which power is transmitted to the first input shaft 10a by one clutch C1 and power is transmitted to the second input shaft 10b by the other clutch C2.
- first input shaft (10a) and the second input shaft (10b) is preferably arranged parallel to each other so that the power can be transmitted stably, in the present invention is formed on the coaxial line in the form of a conventional double tube of the hollow shaft form By doing so, the installation space is minimized.
- the output shaft 20 includes a first output shaft 20a and a second output shaft 20b, and is installed to be parallel to the above-described input shafts.
- the output shaft 20 is selectively powered from the first input shaft 10a or the second input shaft 10b by a gear train and a synchro apparatus to be described later.
- the first gear train 30a and the second gear train 30b are configured to selectively output the power of the first input shaft 10a to the first and second output shafts 20a and 20b, respectively.
- the first gear train 30a and the second gear train 30b are mounted on the first gear 31 and the first and second output shafts 20a and 20b, respectively, which rotate together with the first input shaft 10a.
- second and third gears 32 and 33 that are engaged with the first gear 31 and rotate.
- the second and third gears 32 and 33 are installed to face each other with the first and second gear trains 30a and 30b, and selectively by the first and second synchro devices 40a and 40b. Synchronized to transmit power to the first output shaft (20a) or the second output shaft (20b).
- the gear shift ratio of the first gear train 30a and the second gear train 30b is determined according to the gear ratio of each gear. That is, the rotation speed according to the gear shift speed is determined by this gear ratio.
- the gear ratios of the first gear 31 and the second and third gears 32 and 33 are used. Accordingly, the gear ratio of the first gear train 30a is configured to be engaged in five-speed shifting through the first output shaft 20a and to engage in eight-speed shifting, and to engage in seven-speed shifting through the second output shaft 20b.
- the gear ratio of the second gear train 30b is configured to be shifted in three steps through the first output shaft 20a and participates in the first and eighth speed shifts through the second output shaft 20b.
- the first gear 31 is mounted on the second input shaft 10b, respectively, and the second gear 32 and the third gear 33 are Respectively mounted on the first output shaft 20a and the second output shaft 20b, and meshed with the first gear 31.
- gear ratios in the case of the third gear train 30c, are shifted by four gears through the first output shaft 20a, and six gears are shifted through the second output shaft 20b and seven gears are involved. To configure.
- the fourth gear train 30d the reverse is made through the first output shaft 20a and the second output shaft 20b, and the second gear is shifted through the second output shaft 20b and the first gear is shifted. Configure to get involved.
- the first to fourth gear trains 30a to 30d use external gears so that power can be transmitted between the input shafts and the output shafts arranged side by side.
- the first to fourth synchro devices 40a to 40d are a kind of clutches, which are mounted on the output shaft 20 to interrupt the aforementioned first to fourth gear trains 30a to 30d to selectively transmit power from the input shaft to the output shaft. Make it happen.
- Such a synchro device will be made of a conventional technique, which will be briefly described only for its installation position and its operation.
- a first synchro device 40a and a third synchro device 40c are mounted on the first output shaft 20a.
- the first synchro device 40a is located between the first gear train 30a and the second gear train 30b
- the third synchro device 40c is located between the third gear train 30c and the fourth gear train. 30d).
- a second synchro device 40b and a fourth synchro device 40d are mounted on the second output shaft 20b.
- the second synchro device 40b is located between the first gear train 30a and the second gear train 30b
- the fourth synchro device 40d is the third gear train 30c and the fourth gear train 30d. It is installed to be located between.
- the synchro apparatus mounted as described above operates as shown in the following [Table 2] together with the above-described clutches C1 and C2, and the single gear shift is made by interrupting and releasing the selected gear train.
- the output gear 50 is a gear for outputting according to the number of stages shifted through the output shaft 20.
- the output gear 50 is meshed with the differential Diff.
- the configuration of the output gear 50 and the differential device (Diff) is made of a conventional technique and a detailed description thereof will be omitted herein.
- the double clutch transmission structure according to the first embodiment of the present invention made as described above comprises four gear trains and four synchro devices, and the eight clutches are moved forward by the operation of the clutches C1 and C2 after synchronizing to the desired gear stage. Reverse shift is possible.
- the parking gear is configured on the output side 20, it is omitted in FIG.
- the fourth gear train 30d ' is configured in a double row. That is, the fifth gear train 30e is further configured to operate together with the fourth gear train 30d '.
- the fourth gear train 30d ' is responsible for the second gear shift and the reverse as in the first embodiment.
- the fourth gear train 30d' is provided with the fifth gear train 30e to operate integrally with the fourth gear train 30d '.
- power is transmitted to the first output shaft 20a through the fourth gear train 30d 'and then decelerated from the fifth gear train 30e to the second output shaft 20b.
- the gear train is configured in five rows so that the reverse shift stage can be operated in a double row.
- reference numeral 60 denotes a parking gear.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Structure Of Transmissions (AREA)
Abstract
Description
클러치 | 싱크로 장치 | |||||||||
C1 | C2 | 제1싱크로 | 제2싱크로 | 제3싱크로 | 제4싱크로 | |||||
제1열 | 제2열 | 제1열 | 제2열 | 제3열 | 제4열 | 제3열 | 제4열 | |||
R | ○ | ● | ||||||||
N | (●) | ● | ||||||||
1 | ○ | ● | ● | |||||||
2 | ○ | ● | ||||||||
3 | ○ | ● | ||||||||
4 | ○ | ● | ||||||||
5 | ○ | ● | ||||||||
6 | ○ | ● | ||||||||
7 | ○ | ● | ● | |||||||
8 | ○ | ● | ● | |||||||
(●)는 싱크로장치를 구속 또는 해제를 선택적으로 할 수 있는 것임 |
클러치 | 싱크로 장치 | |||||||||
C1 | C2 | 제1싱크로 | 제2싱크로 | 제3싱크로 | 제4싱크로 | |||||
제1열 | 제2열 | 제1열 | 제2열 | 제3열 | 제4열 | 제3열 | 제4열 | |||
R | ○ | ● | ||||||||
N | (●) | ● | ||||||||
1 | ○ | ● | ● | |||||||
2 | ○ | ● | ||||||||
3 | ○ | ● | ||||||||
4 | ○ | ● | ||||||||
5 | ○ | ● | ||||||||
6 | ○ | ● | ||||||||
7 | ○ | ● | ● | |||||||
8 | ○ | ● | ● | |||||||
(●)는 싱크로장치를 구속 또는 해제를 선택적으로 할 수 있는 것임 |
Claims (5)
- 전진 8단과 후진 1단으로 변속이 가능한 더블 클러치 변속기 구조에 있어서,각각 클러치(C1,C2)에 의해 엔진(E/G)으로부터 선택적으로 동력전달이 이루어지는 제1입력축(10a) 및 제2입력축(10b);상기 제1입력축(10a) 및 제2입력축(10b)으로부터 동력을 전달받아 출력하기 위한 제1출력축(20a) 및 제2출력축(20b)으로 구성된 출력축(20);상기 제1입력축(10a)에 장착되어 출력축(20)에 선택적으로 동력을 전달을 시켜 주는 제1기어열(30a)과 제2기어열(30b);상기 제2입력축(10b)에 장착되어 출력축(20)에 선택적으로 동력을 전달시켜 주는 제3기어열(30c)과 제4기어열(30d);상기 제1기어열(30a)과 제2기어열(30b) 사이에 위치하도록 상기 제1출력축(20a)에 설치되어 상기 제1기어열(30a)과 제2기어열(30b)을 선택적으로 동력전달이 이루어지도록 동기화시켜 주는 제1싱크로장치(40a), 및 상기 제3기어열(30c)과 제4기어열(30d)에 위치하도록 제1출력축(20a)에 설치되어 제3기어열(30c)과 제4기어열(30d)을 선택적으로 동력전달이 이루어지도록 동기화시켜 주는 제3싱크로장치(40c);상기 제1기어열(30a)과 제2기어열(30b) 사이에 위치하도록 상기 제2출력축(20b)에 설치되어 상기 제1기어열(30a)과 제2기어열(30b)을 선택적으로 동력전달이 이루어지도록 동기화시켜 주는 제2싱크로장치(40b), 및 상기 제3기어열(30c)과 제4기어열(30d)에 위치하도록 상기 제2출력축(20b)에 설치되어 제3기어열(30c)과 제4기어열(30d)을 선택적으로 동력전달이 이루어지도록 동기화시켜 주는 제4싱크로장치(40d); 및상기 출력축(20)에 설치되어 그 출력을 차동장치(Diff)로 출력시켜 주기 위한 출력기어(50);를 포함하는 것을 특징으로 하는 더블 클러치 변속기 구조.
- 전진 8단과 후진 1단으로 변속이 가능한 더블 클러치 변속기 구조에 있어서,각각 클러치(C1,C2)에 의해 엔진(E/G)으로부터 선택적으로 동력전달이 이루어지는 제1입력축(10a) 및 제2입력축(10b);상기 제1입력축(10a) 및 제2입력축(10b)으로부터 동력을 전달받아 출력하기 위한 제1출력축(20a) 및 제2출력축(20b)으로 구성된 출력축(20);상기 제1입력축(10a)에 장착되어 출력축(20)에 선택적으로 동력을 전달을 시켜 주는 제1기어열(30a)과 제2기어열(30b);상기 제2입력축(10b)에 장착되어 출력축(20)에 선택적으로 동력을 전달시켜 주는 제3기어열(30c)과 제4기어열(30d);상기 제1기어열(30a)과 제2기어열(30b) 사이에 위치하도록 상기 제1출력축(20a)에 설치되어 상기 제1기어열(30a)과 제2기어열(30b)을 선택적으로 동력전달이 이루어지도록 동기화시켜 주는 제1싱크로장치(40a), 및 상기 제3기어열(30c)과 제4기어열(30d)에 위치하도록 제1출력축(20a)에 설치되어 제3기어열(30c)과 제4기어열(30d)을 선택적으로 동력전달이 이루어지도록 동기화시켜 주는 제3싱크로장치(40c);상기 제1기어열(30a)과 제2기어열(30b) 사이에 위치하도록 상기 제2출력축(20b)에 설치되어 상기 제1기어열(30a)과 제2기어열(30b)을 선택적으로 동력전달이 이루어지도록 동기화시켜 주는 제2싱크로장치(40b), 및 상기 제3기어열(30c)과 제4기어열(30d)에 위치하도록 상기 제2출력축(20b)에 설치되어 제3기어열(30c)과 제4기어열(30d)을 선택적으로 동력전달이 이루어지도록 동기화시켜 주는 제4싱크로장치(40d); 및상기 출력축(20)에 설치되어 그 출력을 차동장치(Diff)로 출력시켜 주기 위한 출력기어(50);를 포함하되,상기 제4기어열(30d)에는 제5기어열(30e)이 복열로 배치되어 구성된 것을 특징으로 하는 더블 클러치 변속기 구조.
- 제 1 항 또는 제 2 항에 있어서,상기 제1입력축(10a)과 제2입력축(10b)은 중공축을 이용하여 이중관 형태로 동축선 상에 배치된 것을 특징으로 하는 더블 클러치 변속기 구조.
- 제 3 항에 있어서,상기 제1 내지 제4기어열(30a~30d)은 외접기어인 것을 특징으로 하는 더블 클러치 변속기 구조.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112013005196.6T DE112013005196B4 (de) | 2012-10-31 | 2013-02-18 | Doppelkupplungsgetriebe |
US14/439,539 US9772006B2 (en) | 2012-10-31 | 2013-02-18 | Double clutch transmission |
CN201380056805.1A CN104797853B (zh) | 2012-10-31 | 2013-02-18 | 双离合器变速器 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR10-2012-0122110 | 2012-10-31 | ||
KR1020120122110A KR101334508B1 (ko) | 2012-10-31 | 2012-10-31 | 더블 클러치 변속기 구조 |
Publications (1)
Publication Number | Publication Date |
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WO2014069720A1 true WO2014069720A1 (ko) | 2014-05-08 |
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US (1) | US9772006B2 (ko) |
KR (1) | KR101334508B1 (ko) |
CN (1) | CN104797853B (ko) |
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CN105864404A (zh) * | 2015-02-05 | 2016-08-17 | 现代自动车株式会社 | 用于车辆的变速器 |
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KR101637725B1 (ko) | 2014-11-12 | 2016-07-07 | 현대자동차주식회사 | 하이브리드 차량용 변속기 |
KR101684087B1 (ko) * | 2015-04-07 | 2016-12-08 | 현대자동차주식회사 | 차량용 변속기 |
KR101679967B1 (ko) | 2015-04-29 | 2016-11-25 | 현대자동차주식회사 | 다단 변속기 |
KR101755833B1 (ko) * | 2015-09-02 | 2017-07-10 | 현대자동차주식회사 | 차량용 변속기 |
DE102016202914A1 (de) * | 2016-02-25 | 2017-08-31 | Ford Global Technologies, Llc | Doppelkupplungsgetriebe für Kraftfahrzeuge |
DE102016202915A1 (de) * | 2016-02-25 | 2017-08-31 | Ford Global Technologies, Llc | Doppelkupplungsgetriebe für Kraftfahrzeuge |
CN106838154B (zh) * | 2016-12-14 | 2019-01-01 | 山推工程机械股份有限公司 | 一种换挡变速箱 |
CN110578773A (zh) * | 2018-06-08 | 2019-12-17 | 长城汽车股份有限公司 | 八挡变速器 |
DE102019004762B3 (de) * | 2019-07-08 | 2020-07-23 | Daimler Ag | Hybrid-Doppelkupplungsgetriebe |
CN110588324A (zh) * | 2019-10-09 | 2019-12-20 | 宁波上中下自动变速器有限公司 | 一种变速装置、动力总成及车辆 |
DE102020005390B4 (de) * | 2020-09-03 | 2022-06-15 | Mercedes-Benz Group AG | Doppelkupplungsgetriebe und Hybridantriebsystem |
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Also Published As
Publication number | Publication date |
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DE112013005196B4 (de) | 2017-09-28 |
US20150285340A1 (en) | 2015-10-08 |
DE112013005196T5 (de) | 2015-08-13 |
CN104797853B (zh) | 2017-09-01 |
US9772006B2 (en) | 2017-09-26 |
KR101334508B1 (ko) | 2013-11-29 |
CN104797853A (zh) | 2015-07-22 |
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