AT503476A1 - Gearbox for one vehicle - Google Patents

Gearbox for one vehicle Download PDF

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Publication number
AT503476A1
AT503476A1 AT0100607A AT10062007A AT503476A1 AT 503476 A1 AT503476 A1 AT 503476A1 AT 0100607 A AT0100607 A AT 0100607A AT 10062007 A AT10062007 A AT 10062007A AT 503476 A1 AT503476 A1 AT 503476A1
Authority
AT
Austria
Prior art keywords
gear
input shaft
shaft
transmission
clutch
Prior art date
Application number
AT0100607A
Other languages
German (de)
Other versions
AT503476B1 (en
Original Assignee
Avl List Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Avl List Gmbh filed Critical Avl List Gmbh
Priority to AT0100607A priority Critical patent/AT503476B1/en
Publication of AT503476A1 publication Critical patent/AT503476A1/en
Application granted granted Critical
Publication of AT503476B1 publication Critical patent/AT503476B1/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H3/00Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/006Toothed 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H2200/00Transmissions for multiple ratios
    • F16H2200/003Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0052Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H3/00Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08Toothed 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
    • F16H3/087Toothed 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
    • F16H3/089Toothed 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 all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H3/00Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08Toothed 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
    • F16H3/087Toothed 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
    • F16H3/093Toothed 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

Description

♦ + · · · · ····· ♦ + · · · · · · ····· - Γ- 55545
The invention relates to a transmission for a vehicle, which is designed as a double clutch transmission, wherein the gears are combined to input shafts and an output shaft gear groups, wherein the gears of the gear groups of the input shafts with the gears of at least one gear group of the output shaft in permanent engagement, and wherein a first input shaft via a first clutch and a second input shaft via a second clutch to a drive shaft of a prime mover is connectable.
From DE 198 07 374 Al a dual-clutch transmission is known, wherein the gears of the transmission are combined to form gear groups, which act on switching elements. The clutches are arranged at different end faces of the transmission and are driven by a single prime mover. A switching element for switching between different gears is designed so that it can be passed through the gear groups and thus can act on all gears of a gear group.
WO 92/04558 Al describes a dual-clutch gear change transmission for motor vehicles, with two simultaneously oppositely controlled clutches. One of the higher gear ratios is connected as a gear shift with the one clutch. The other gear ratios are connectable to the other clutch. When engaging the first clutch, which is controlled by means of its own switching device, the other gear ratios can be arbitrarily inserted.
WO 2005/085674 A1 discloses a dual-clutch transmission for a vehicle with rear-wheel drive. Via the dual clutch, a drive shaft may alternatively be connected to one of two input shafts, each input shaft having a plurality of first gears. On an output shaft a plurality of second gears are arranged, which mesh with the corresponding first gears of the input shafts. About the switching element, each second gear can be rotatably connected to the output shaft.
With the known manual transmissions short switching times can be achieved. The disadvantage is that a relatively high space and manufacturing costs are required.
The object of the invention is to avoid these disadvantages and to achieve short switching times in a space-saving manner in a transmission of the type mentioned. In this case, the production cost should be reduced.
According to the invention, we achieve this by arranging a first primary ratio between the input shaft and the first input shaft and a second primary ratio between the input shaft and the second input shaft, wherein preferably first and second primary ratios have different transmission ratios. The first primary ratio with the first clutch on the one hand and the second primary ratio with the second clutch on the other hand are arranged at different end faces of the transmission.
A space-saving arrangement can be achieved if at least one of the two clutches is arranged coaxially with the drive shaft.
Furthermore, it can be provided that the first clutch is coaxially arranged with the first input shaft and / or the second clutch coaxially with the second input shaft.
In a very narrow construction variant, it is provided that first and second input shaft are spaced apart and have different axes of rotation, wherein preferably one gear of the gear group of the first input shaft and a gear of the gear group of the second input shaft with the same gear of a arranged on the output shaft output gear group in permanent intervention stands. Alternatively, it is also possible that first and second input shaft are arranged coaxially with each other.
To save space and components, it is advantageous if a freely rotatably mounted middle gear, which is in permanent engagement with an associated gear of the output shaft, and which is arranged coaxially with the first and second input shaft, via at least one switching element optionally with the first or second input shaft is connectable. This design makes it possible to save a gear stage with the same number of gears. In a simple embodiment, in each case a switching element is arranged on both sides of the freely rotatable gear, wherein a rotational connection between the freely rotatable gear and the first or the second input shaft can be produced by moving the switching elements.
In a particularly narrow design variant is provided that the first and second input shafts are formed as coaxially arranged behind one another hollow shafts, wherein between the two hollow shafts, the freely rotatable gear is arranged, with which a freely rotatably mounted within the two hollow shafts inner shaft is rotatably connected and wherein the shaft is optionally connected via a switching element to the first one Input shaft or drehverbindbar with the second input shaft.
Furthermore, can be provided to save space width, that between two on the output shaft freely rotatably mounted adjacent gears of different gear groups, a switching element is arranged, by means of which either the first input shaft or the second input shaft is rotatably connected to the output shaft. It can be found with a very small number of switching elements Auslangen.
The invention will be explained in more detail below with reference to FIGS.
1 shows a double clutch transmission according to the invention in a first embodiment, FIG. 2 shows the dual clutch transmission in a second embodiment, FIG. 3 shows the dual clutch transmission in a third embodiment, FIG. 4 shows the dual clutch transmission in a fourth embodiment in an end view, FIG 6 shows the dual-clutch transmission in a fifth embodiment, FIG. 7 shows the dual-clutch transmission in a sixth embodiment, and FIG. 8 shows the dual-clutch transmission in a seventh embodiment variant.
Functionally identical parts are provided in the figures with the same reference numerals.
Trained as a double-clutch transmission 1 has a first input shaft 2 with a first gear group 3 and a second input shaft 4 with a second gear group 5, and an output shaft 6 with corresponding gear groups 7, 8, wherein the gears of the first gear group 3 with gears of the third Gear group 7 and the gears of the second gear group 5 with gears of the fourth gear group 8 are engaged. Reference numeral 9 denotes a driven wheel. The first input shaft 2 can be driven via the first clutch 10, the second input shaft 4 via the second clutch 12 by the drive shaft 11 of the internal combustion engine 15. Thus, two different primary drives 13, 14 are available for driving the input shafts 2, 4, whereby the primary drives 13, 14 can have different transmission ratios. The gears are indicated by G1, G2, G3, G4, G5, G6.
In the embodiment variant shown in Fig. 1, the first clutch on the first input shaft 2 and the second clutch 12 is disposed on the second input shaft 4. Alternatively, it is also possible to arrange one or both clutches 10, 12 directly on the drive shaft 11, as shown in FIGS. 2 and 3. FIGS. 4 and 5 show an embodiment of a •••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••••• ···· · ································································································································ In the case of which the first and second input shafts 2, 4 are not disposed on the same axis of rotation 2a as shown in FIGS. but offset from each other are arranged. In this case, the gears of the first gear group 3 and the gears of the second gear group 5 act on the same on the output shaft 6 arranged gears of the output gear group 16 a. Between in each case two gears of the first gear group 3 and the second gear group 5, respectively switching elements 17, 18 are arranged on the first input shaft 2, or the second input shaft 4. This construction makes it possible to save components and to make the dual-clutch transmission very narrow. The clutches 10, 12 may be arranged on the side of the input shafts 2, 4 or else on the side of the drive shaft 11.
Fig. 6 shows a variant with arranged on a rotation axis 2a first and second input shafts 2, 4. For switching between two gears switching elements 17, 18 are arranged between each two gears on the output shaft 6 of the third gear group 7 and the fourth gear group. The particular feature of this embodiment is that a further switching element 19 between the arranged on the output shaft 6 adjacent inner gears 20, 21 of the third gear group 7 and the fourth gear group 8 is provided. The inner shift element 19 can thus be used for shifting, for example, between the third and the sixth gear G3, G6.
7 and 8 show embodiments in which between the first and the second gear group 3, 5 coaxially with the first and second input shaft 2, 4, a freely rotating middle gear 22 is arranged, which with a corresponding gear 23 on the output shaft. 6 in permanent engagement. On both sides of the gear 22 switching elements 24, 25 are arranged in Fig. 7, via which the central gear 22 with the first input shaft 2 or with the second input shaft 4 can be rotatably connected. Assuming that the primary drives 10, 12 have different transmission ratios, the gears G5 and G6 can be switched by means of the shift elements 24, 25. The advantage of this design is that - compared to conventional 6-speed transmissions - a gear stage can be saved. Furthermore, a narrower design of the dual clutch transmission is possible.
Fig. 8 differs from the embodiment shown in Fig. 7 in that the first and the second Eingangswelie 2, 3 are formed as hollow shafts, within the hollow shafts, an inner shaft 27 is freely rotatably mounted, wherein the inner shaft 27 with the central gear 22 is rotationally connected, and wherein the rotary connection düng 26 via an axially displaceable shaft-hub connection. The inner shaft 27 can be displaced axially between a first and a second position via a switching element 28 designed as a sliding sleeve, the switching element 28 rotating with the first input shaft 2 and being axially displaceable thereon. The axial movement of the switching element 28 is transmitted directly to the inner shaft 27, which - depending on the direction of movement - via a shaft-hub connection 29, 30 with the first or second input shaft 2, 4 is rotatably connected and thus the first input shaft 2 or the second input shaft 4 connects to the middle gear 22. As a result, different translations according to the gear stages G5, G6 can be realized in combination with differently translated primary gears 13, 14. In the embodiment shown in Fig. 8, the switching elements 17, 18 for switching gear stages Gl, G3, and G2, G4 on the side of the first and second input shaft 2, 4 are arranged. The reference numerals 31, 32 denote sliding or roller bearings for supporting the inner shaft 27, and for supporting the first and second input shafts 2, 4.
Compared to the embodiment shown in Fig. 7, the embodiment of FIG. 8 has the advantage that a switching element can be saved and thus an even more compact design of the dual clutch transmission can be realized.

Claims (11)

  1. ············· 1. A transmission (1) for a vehicle, which is designed as a double-clutch transmission, wherein the gears arranged on input shafts (2, 4) and an output shaft (6) Gear groups (3, 5) are combined, wherein the gears of the gear groups (3, 5) of the input shafts (2, 4) with the gears of at least one gear group (7, 8, 16) of the output shaft (6) in permanent engagement, and wherein a first input shaft (2) via a first clutch (10) and a second input shaft (4) via a second clutch (12) with a drive shaft (11) of a prime mover is connectable, characterized in that between the drive shaft (11) and the first input shaft (2) has a first primary ratio (13) and between the drive shaft (11) and the second one output shaft (4) a second primary ratio (14) is arranged, preferably first and second primary ratios (13, 14) have different transmission ratios.
  2. 2. Transmission (1) according to claim 1, characterized in that at least one of the two clutches (10, 12) is arranged coaxially with the drive shaft (11).
  3. 3. Transmission (1) according to claim 1 or 2, characterized in that the first primary ratio (13) with the first clutch (10) on the one hand and the second primary ratio (14) with the second clutch (12) on the other hand at different end faces of the transmission (1) are arranged.
  4. 4. Transmission (1) according to one of claims 1 to 3, characterized in that the first clutch (10) arranged coaxially with the first input shaft (2) and / or the second clutch (12) coaxially with the second input shaft (4) is.
  5. 5. Transmission (1) according to one of claims 1 to 4, characterized in that the first and second input shaft (2, 4) are arranged coaxially with each other.
  6. 6. Transmission (1) according to one of claims 1 to 4, characterized in that the first and second input shaft (2, 4) are spaced from each other and have different axes of rotation (2a, 4a).
  7. 7. gearbox (1) according to claim 6, characterized in that in each case a gear of the gear group (3) of the first input shaft (2) and a ···· ··· «···· ···· ··· · · · · · ····· ·· 5) of the second input shaft (4) is in permanent engagement with the same gear of a driven gear group (16) arranged on the output shaft (7).
  8. 8. Transmission (1) according to one of claims 1 to 6, characterized in that a freely rotatably mounted middle gear (22) which is in permanent engagement with an associated gear of the output shaft (6), and which is coaxially with the first and second input shaft (2, 4) is arranged, via at least one switching element (24, 25) optionally with the first or second input shaft (2, 4) is connectable.
  9. 9. gear (1) according to claim 8, characterized in that on both sides of the freely rotatable middle gear (22) each have a switching element (24, 25) is arranged, wherein by moving one of the two switching elements (24, 25) one Rotary connection between the freely rotatable central gear (22) and the first or second input shaft (2, 4) can be produced.
  10. 10. Transmission (1) according to claim 8, characterized in that the first and second input shaft (2, 4) are formed as coaxially arranged behind one another hollow shafts, wherein between the two hollow shafts, the freely rotatable central gear (22) is arranged, with which a freely rotatable within the two hollow shafts rotatably mounted inner shaft (27) and wherein the inner shaft (27) selectively via a switching element (28) with the first input shaft (2) or with the second input shaft (4) is drehverbindbar.
  11. 11. Transmission (1) according to one of claims 1 to 7, characterized in that between two on the output shaft (6) freely rotatably mounted adjacent gears (20, 21) of different gear groups (7, 8), a switching element (19) is arranged by means of which either the first input shaft or the second input shaft (2) with the output shaft (6) is drehverbindbar. 2007 06 28 Fu / Sc Patent Attorney Dipl.-Ing. Michael Babeluk A-1150 Vienna, Mariahilfer GOrtal 39/17 Tel .: (+431) 892 89 33-0 Fax: (+43 1) 8? 2 89 323 e-mail: oatem »hatwMrfea *
AT0100607A 2007-06-28 2007-06-28 Gearbox for one vehicle AT503476B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT0100607A AT503476B1 (en) 2007-06-28 2007-06-28 Gearbox for one vehicle

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
AT0100607A AT503476B1 (en) 2007-06-28 2007-06-28 Gearbox for one vehicle
PCT/EP2008/057827 WO2009000755A2 (en) 2007-06-28 2008-06-20 Transmission for a vehicle
DE112008001725.5T DE112008001725B4 (en) 2007-06-28 2008-06-20 Transmission for a vehicle
CN2008800223163A CN101730805B (en) 2007-06-28 2008-06-20 Transmission for a vehicle

Publications (2)

Publication Number Publication Date
AT503476A1 true AT503476A1 (en) 2007-10-15
AT503476B1 AT503476B1 (en) 2010-11-15

Family

ID=38565648

Family Applications (1)

Application Number Title Priority Date Filing Date
AT0100607A AT503476B1 (en) 2007-06-28 2007-06-28 Gearbox for one vehicle

Country Status (4)

Country Link
CN (1) CN101730805B (en)
AT (1) AT503476B1 (en)
DE (1) DE112008001725B4 (en)
WO (1) WO2009000755A2 (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2182247A1 (en) * 2008-10-30 2010-05-05 Yamaha Hatsudoki Kabushiki Kaisha Engine unit, and motor cycle equipped therewith
EP2182254A1 (en) * 2008-10-30 2010-05-05 Yamaha Hatsudoki Kabushiki Kaisha Shift mechanism, and vehicle equipped therewith
EP2182246A1 (en) * 2008-10-30 2010-05-05 Yamaha Hatsudoki Kabushiki Kaisha Twin clutch transmission, and vehicle equipped therewith
EP2182245A1 (en) 2008-10-30 2010-05-05 Yamaha Hatsudoki Kabushiki Kaisha Twin clutch transmission, and vehicle and motorcycle equipped therewith

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2562443A4 (en) * 2010-04-23 2018-04-25 Yamaha Hatsudoki Kabushiki Kaisha Engine unit and two-wheeled motor vehicle with same
CN103727181B (en) * 2014-01-09 2017-03-15 陈兵 A kind of dual input shaft transmission with fluid torque-converter

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Publication number Priority date Publication date Assignee Title
DE515101C (en) * 1927-04-02 1930-12-23 Fried Krupp Akt Ges Gear change gears with permanently engaged gears and adjustable clutches designed as change gears, especially for motor vehicles
DE3027984A1 (en) * 1980-07-24 1982-02-25 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8000 München COMPACT ENGINE
JPH0249424B2 (en) * 1982-01-08 1990-10-30 Nissan Motor
GB8602560D0 (en) * 1986-02-03 1986-03-12 Automotive Prod Plc Rotary transmission
JP2556608B2 (en) * 1990-06-20 1996-11-20 川崎重工業株式会社 Transmission for vehicle
EP0469451B1 (en) * 1990-07-25 1997-02-05 CLARK-HURTH COMPONENTS S.p.A. Three-shaft gearbox particularly for industrial vehicles in general
WO1992004558A1 (en) * 1990-09-05 1992-03-19 Valentin Balass Double clutch gear-change for motor vehicles
DE19807374A1 (en) * 1998-02-21 1999-04-29 Bosch Gmbh Robert Automotive double clutch transmission unit
DE19911027C2 (en) * 1999-03-12 2000-12-28 Bosch Gmbh Robert Multi-speed manual transmission for a motor vehicle with a double clutch
AU2003229490A1 (en) * 2002-03-13 2003-09-29 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Gearbox, in particular a double-clutch gearbox
ITBO20040112A1 (en) * 2004-02-27 2004-05-27 Ferrari Spa Double clutch transmission for rear-wheel drive vehicles
FR2868141B1 (en) * 2004-03-24 2007-05-25 Antonov Automotive Europ GEARBOX FOR THE AUTOMOTIVE, IN PARTICULAR A DOUBLE CLUTCH
JP4346483B2 (en) * 2004-03-25 2009-10-21 本田技研工業株式会社 Twin clutch transmission

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2182247A1 (en) * 2008-10-30 2010-05-05 Yamaha Hatsudoki Kabushiki Kaisha Engine unit, and motor cycle equipped therewith
EP2182254A1 (en) * 2008-10-30 2010-05-05 Yamaha Hatsudoki Kabushiki Kaisha Shift mechanism, and vehicle equipped therewith
EP2182246A1 (en) * 2008-10-30 2010-05-05 Yamaha Hatsudoki Kabushiki Kaisha Twin clutch transmission, and vehicle equipped therewith
EP2182245A1 (en) 2008-10-30 2010-05-05 Yamaha Hatsudoki Kabushiki Kaisha Twin clutch transmission, and vehicle and motorcycle equipped therewith
US8567276B2 (en) 2008-10-30 2013-10-29 Yamaha Hatsudoki Kabushiki Kaisha Engine unit, and motorcycle equipped therewith
US8578805B2 (en) 2008-10-30 2013-11-12 Yamaha Hatsudoki Kabushiki Kaisha Twin clutch transmission, and vehicle and motorcycle equipped therewith
US8794091B2 (en) 2008-10-30 2014-08-05 Yamaha Hatsudoki Kabushiki Kaisha Twin clutch transmission, and vehicle equipped therewith

Also Published As

Publication number Publication date
AT503476B1 (en) 2010-11-15
DE112008001725A5 (en) 2010-07-29
WO2009000755A3 (en) 2009-02-19
WO2009000755A2 (en) 2008-12-31
DE112008001725B4 (en) 2019-05-23
CN101730805A (en) 2010-06-09
CN101730805B (en) 2012-11-21

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