WO2011088849A1 - Dual clutch transmission - Google Patents

Dual clutch transmission Download PDF

Info

Publication number
WO2011088849A1
WO2011088849A1 PCT/EP2010/000400 EP2010000400W WO2011088849A1 WO 2011088849 A1 WO2011088849 A1 WO 2011088849A1 EP 2010000400 W EP2010000400 W EP 2010000400W WO 2011088849 A1 WO2011088849 A1 WO 2011088849A1
Authority
WO
WIPO (PCT)
Prior art keywords
deck
synchronizer
coupled
clutch
gear
Prior art date
Application number
PCT/EP2010/000400
Other languages
French (fr)
Inventor
Nicolas Alain Funalot
Original Assignee
Gm Global Technology Operations, Inc.
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 Gm Global Technology Operations, Inc. filed Critical Gm Global Technology Operations, Inc.
Priority to PCT/EP2010/000400 priority Critical patent/WO2011088849A1/en
Publication of WO2011088849A1 publication Critical patent/WO2011088849A1/en

Links

Classifications

    • 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
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
    • 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
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/04—Combinations of toothed gearings only
    • F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
    • F16H37/046—Combinations of toothed gearings only change gear transmissions in group arrangement with an additional planetary gear train, e.g. creep gear, overdrive
    • 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
    • F16H2003/445—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the input and the set of orbital gears
    • 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
    • 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
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • 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
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
    • F16H2200/2023—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 4 connections
    • 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
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2064—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using at least one positive clutch, e.g. dog clutch

Definitions

  • the invention concerns a dual clutch transmission comprising two clutches and two half transmissions with planetary gearsets .
  • a dual clutch transmission for a front-transverse arrangement comprising a dual clutch and two partial transmissions with planetary gearsets is known from DE 10 2006 028 798 Al .
  • Each of the two clutches of the dual clutch acts upon one coaxial transmission input shaft which effects a partial transmission.
  • the partial transmissions are embodied as planetary gearsets that are to be shifted in a positive manner, the output being performed axially parallel to the input, in the same rotational direction. Torque is transmitted to the output shaft by means of at least one intermediate shaft that runs parallel to the transmission input shaft.
  • the objective of the present invention is to provide an
  • the planetary gearsets are Ravigneaux-type gearsets each with two decks, with common carriers and a plurality of long pinions making the link between the two decks, the first deck comprising a sun gear and a planet gear, the sun gear of the first deck being permanently coupled to a first synchronizer, the second deck comprising a sun gear, a ring gear and a plurality of planet gears, the third deck comprising a sun gear and a ring gear, the forth deck comprising a sun gear and a plurality of planet gears, a second synchronizer being permanently coupled via a chain member to the second clutch, the output being permanently coupled to the ring gears.
  • This automatic transmission with a reduced number of mechanical parts and a lower weight due to the planetary gearsets provides a high efficiency (total drag losses in clutches are reduced due to the lower number of clutches) and a high torque density.
  • the elements of the planetary gearset are connected with input or transmission case with the help of synchronizers that are operated while the half transmission they belong to is out of. the powerflow.
  • this automatic transmission allows to combine the benefits of a planetary transmissions and of traditional dual clutch transmissions into the same transmission for front wheel drive (FWD) vehicles.
  • two further synchronizers being permanently coupled to the transmission case or ground are provided for each deck; the third synchronizer and the forth synchronizers being able to be alternately coupled to the sun gear of the second deck or to the carrier, the fifth synchronizer being able to be coupled to the carrier or to the sun gear of the third deck and the sixth synchronizer being able to be alternately coupled or not to the carrier in so-called on and off positions.
  • the synchronizers of the first two decks together with the first clutch activate the odd gears (1st, 3rd, 5th, 7th) as well as the reverse gear and the synchronizers of the second deck together with the second clutch activate the even gears (2nd, 4th, 6th, 8th) .
  • the first gear is engaged if the first clutch is activated and the third synchronizer is off, the forth synchronizer is coupled to the sun gear and the first synchronizer is coupled to the Input;
  • the second gear is engaged if the second clutch is activated and the second synchronizer is coupled to the sun gear of the forth deck, the fifth synchronizer is coupled to the carrier and the sixth synchronizer is off;
  • the third gear is engaged if the first clutch is activated and the third synchronizeris coupled to the sun gear of the second deck, the forth synchronizer is coupled to the carrier and the first synchronizer is off;
  • the forth gear being engaged if the second clutch is activated, the second synchronizer is coupled to the sun gear of the forth deck, the fifth synchronizer is coupled to the sun gear of the third deck and the sixth synchronizer is off;
  • the fifth gear being engaged if the first clutch is activated, the third synchronizer is coupled to the sun gear of the second deck, the forth synchronizer is off and the first synchronizer is coupled to the ground
  • FIGURE 1 shows a schematic representation of the automatic transmission according to the present invention
  • FIGURE 2 shows the clutching table for the automatic transmission according to the present invention.
  • the automatic transmission according to the invention is provided with two clutches (Clutch 1, Clutch 2) situated at the input (In), the first clutch (Clutch 1) for the odd gears (1st, 3rd, 5th, and 7th) and the reverse gear (Rev.), the second clutch (Clutch 2) for the even gears (2nd, 4th, 6th, 8th) .
  • the transmission comprises two half transmissions with planetary gearsets which are Ravigneaux-type gearsets each with two decks (deck 1, deck 2; deck 3, deck 4) with common carriers (CR12, CR43) and a plurality of long pinions (LP1, LP2; LP3, LP4) making the link between the two decks.
  • a chain is provided in order to transmit input from the second clutch (Clutch 2) to the third deck (deck 3) and the forth deck (deck 4) .
  • the first deck (deck 1) comprises a sun gear (SI) and a plurality of planet gears (PI)
  • the second deck (deck 2) comprises a sun gear (S2), a ring gear (R2) and a plurality of planet gears (P2)
  • the third deck (deck 3) comprises a sun gear (S3) and a ring gear (R3)
  • the forth deck (deck 4) comprises a sun gear (S4) and a plurality of planet gears (P4) .
  • the first synchronizer (Synclinput) and the second synchronizer (Synclground) can be coupled to the sun gear (S2) of the second deck (deck 2) or to the common carrier (CR12) of the first and the second deck.
  • the third synchronizer (Syncl- Sunl) can be coupled to input (In) or to the ground.
  • the forth synchronizer can be coupled to the sun gear (S4) of the forth deck (deck 4) or to the common carrier (CR43) of the third and the forth deck.
  • the fifth synchronizer can be coupled to the sun gear (S3) of the third deck or to the common carrier (CR43) of the third and the forth deck.
  • the sixth synchronizer can be alternately coupled or not to the carrier (CR43) in so- called on and off positions.
  • Sync2input, Sync2ground, Sync2direct eight forward speeds and one reverse speed can be attained according to the clutching table as shown in FIGURE 2.
  • PARK for securing the vehicle in park position (if the engine is off) .
  • the speed ratios can be as follows - speed ratios are proposed as an example, and can be adapted to any peculiar requirement by changing the numbers of teeth of the gears: Gear ratio Gear step

Abstract

The invention concerns a dual clutch transmission comprising two clutches and two half transmissions with planetary gearsets. In order to provide an improved dual clutch transmission, it is proposed according to the present invention that the planetary gearsets are Ravigneaux-type gearsets each with two decks, with common carriers and a plurality of long pinions making the link between the two decks, the first deck comprising a sun gear and a planet gear, the sun gear of the first deck being permanently coupled to a first synchronizer, the second deck comprising a sun gear, a ring gear and a plurality of planet gears, the third deck comprising a sun gear and a ring gear, the forth deck comprising a sun gear and a plurality of planet gears, a second synchronizer being permanently coupled via a chain member to the second clutch, the output being permanently coupled to the ring gears. This automatic transmission with a reduced number of mechanical parts and a lower weight due to the planetary gearsets provides a high efficiency (total drag losses in clutches are reduced due to the lower number of clutches) and a high torque density.

Description

DESCRIPTION
Dual clutch transmission
The invention concerns a dual clutch transmission comprising two clutches and two half transmissions with planetary gearsets .
A dual clutch transmission for a front-transverse arrangement comprising a dual clutch and two partial transmissions with planetary gearsets is known from DE 10 2006 028 798 Al . Each of the two clutches of the dual clutch acts upon one coaxial transmission input shaft which effects a partial transmission. The partial transmissions are embodied as planetary gearsets that are to be shifted in a positive manner, the output being performed axially parallel to the input, in the same rotational direction. Torque is transmitted to the output shaft by means of at least one intermediate shaft that runs parallel to the transmission input shaft.
The objective of the present invention is to provide an
improved dual clutch transmission.
This objective is achieved according to the invention in that the planetary gearsets are Ravigneaux-type gearsets each with two decks, with common carriers and a plurality of long pinions making the link between the two decks, the first deck comprising a sun gear and a planet gear, the sun gear of the first deck being permanently coupled to a first synchronizer, the second deck comprising a sun gear, a ring gear and a plurality of planet gears, the third deck comprising a sun gear and a ring gear, the forth deck comprising a sun gear and a plurality of planet gears, a second synchronizer being permanently coupled via a chain member to the second clutch, the output being permanently coupled to the ring gears.
This automatic transmission with a reduced number of mechanical parts and a lower weight due to the planetary gearsets provides a high efficiency (total drag losses in clutches are reduced due to the lower number of clutches) and a high torque density. The elements of the planetary gearset are connected with input or transmission case with the help of synchronizers that are operated while the half transmission they belong to is out of. the powerflow. In summary, this automatic transmission allows to combine the benefits of a planetary transmissions and of traditional dual clutch transmissions into the same transmission for front wheel drive (FWD) vehicles.
In a preferred embodiment of the invention, two further synchronizers being permanently coupled to the transmission case or ground are provided for each deck; the third synchronizer and the forth synchronizers being able to be alternately coupled to the sun gear of the second deck or to the carrier, the fifth synchronizer being able to be coupled to the carrier or to the sun gear of the third deck and the sixth synchronizer being able to be alternately coupled or not to the carrier in so-called on and off positions.
The synchronizers of the first two decks together with the first clutch activate the odd gears (1st, 3rd, 5th, 7th) as well as the reverse gear and the synchronizers of the second deck together with the second clutch activate the even gears (2nd, 4th, 6th, 8th) . According to the present invention, that the first gear is engaged if the first clutch is activated and the third synchronizer is off, the forth synchronizer is coupled to the sun gear and the first synchronizer is coupled to the Input; the second gear is engaged if the second clutch is activated and the second synchronizer is coupled to the sun gear of the forth deck, the fifth synchronizer is coupled to the carrier and the sixth synchronizer is off; the third gear is engaged if the first clutch is activated and the third synchronizeris coupled to the sun gear of the second deck, the forth synchronizer is coupled to the carrier and the first synchronizer is off; the forth gear being engaged if the second clutch is activated, the second synchronizer is coupled to the sun gear of the forth deck, the fifth synchronizer is coupled to the sun gear of the third deck and the sixth synchronizer is off; the fifth gear being engaged if the first clutch is activated, the third synchronizer is coupled to the sun gear of the second deck, the forth synchronizer is off and the first synchronizer is coupled to the ground; the sixth gear being engaged if the second clutch is activated, the third synchronizer is coupled to the sun gear of the forth deck, the fifth synchronizer is off and the sixth synchronizer is on; the seventh gear being engaged if the first clutch is activated, the third synchronizer is coupled to the carrier, the forth synchronizer is off and the first synchronizer is coupled to the ground; the eighth gear being engaged if the second clutch is activated, the second synchronizer is coupled to the carrier, the fifth synchronizer is coupled to the sun gear of the third deck, the sixth synchronizer is off and the reverse gear being engaged if the first clutch is activated, the third synchronizer is off, the forth synchronizer is coupled to the carrier and the first synchronizer is coupled to the input. Furthermore, there is a blocking mechanism for securing the vehicle in park position.
In the following, the invention is explained in detail with reference to the drawings in which
FIGURE 1 shows a schematic representation of the automatic transmission according to the present invention,
FIGURE 2 shows the clutching table for the automatic transmission according to the present invention.
As represented in FIGURE 1, the automatic transmission according to the invention is provided with two clutches (Clutch 1, Clutch 2) situated at the input (In), the first clutch (Clutch 1) for the odd gears (1st, 3rd, 5th, and 7th) and the reverse gear (Rev.), the second clutch (Clutch 2) for the even gears (2nd, 4th, 6th, 8th) .
The transmission comprises two half transmissions with planetary gearsets which are Ravigneaux-type gearsets each with two decks (deck 1, deck 2; deck 3, deck 4) with common carriers (CR12, CR43) and a plurality of long pinions (LP1, LP2; LP3, LP4) making the link between the two decks. A chain is provided in order to transmit input from the second clutch (Clutch 2) to the third deck (deck 3) and the forth deck (deck 4) .
The first deck (deck 1) comprises a sun gear (SI) and a plurality of planet gears (PI), the second deck (deck 2) comprises a sun gear (S2), a ring gear (R2) and a plurality of planet gears (P2), the third deck (deck 3) comprises a sun gear (S3) and a ring gear (R3) and the forth deck (deck 4) comprises a sun gear (S4) and a plurality of planet gears (P4) .
There are six synchronizers (Synclinput, Synclground, Syncl- Sunl; Sync2input, Sync2ground, Sync2direct) provided, three for each half transmission.
The first synchronizer (Synclinput) and the second synchronizer (Synclground) can be coupled to the sun gear (S2) of the second deck (deck 2) or to the common carrier (CR12) of the first and the second deck. The third synchronizer (Syncl- Sunl) can be coupled to input (In) or to the ground.
The forth synchronizer (Sync2input) can be coupled to the sun gear (S4) of the forth deck (deck 4) or to the common carrier (CR43) of the third and the forth deck. The fifth synchronizer ( Sync2ground) can be coupled to the sun gear (S3) of the third deck or to the common carrier (CR43) of the third and the forth deck. Finally, the sixth synchronizer (Sync2direct ) can be alternately coupled or not to the carrier (CR43) in so- called on and off positions.
With the two clutches (Clutch 1, Clutch 2) and the six synchronizers (Synclinput, Synclground, Syncl-Sunl;
Sync2input, Sync2ground, Sync2direct) , eight forward speeds and one reverse speed can be attained according to the clutching table as shown in FIGURE 2.
Furthermore, there is a blocking mechanism (PARK) for securing the vehicle in park position (if the engine is off) .
The speed ratios can be as follows - speed ratios are proposed as an example, and can be adapted to any peculiar requirement by changing the numbers of teeth of the gears: Gear ratio Gear step
Rev. -14.57
-0.81
1st 18.00 1.46
2nd 12.29 1.46
3rd 8.97 1.37
4th 6.63 1.35
5th 4.96 1.34
6th 3.77 1.31
7th 3.07 1.23
8th 2.51 1.22
Transmission spread 7.18

Claims

1. A dual clutch transmission comprising two clutches and two half transmissions with planetary gearsets, characterized in that the planetary gearsets are Ravigneaux-type gearsets each with two decks (deck 1, deck 2; deck 3, deck 4), with common carriers (CR12, CR43) and a plurality of long pinions (LP1, LP2; LP3, LP4) making the link between the two decks, the first deck (deck 1) comprising a sun gear (SI) and a planet gear (PI), the sun gear (SI) of the first deck (deck 1) being permanently coupled to a first synchronizer (Syncl- Sunl) , the second deck (deck 2) comprising a sun gear
(52) , a ring gear (R2) and a plurality of planet gears (P2), the third deck (deck 3) comprising a sun gear (S3) and a ring gear (R3) , the forth deck (deck 4) comprising a sun gear (S4) and a plurality of planet gears (P4); a second synchronizer (Sync2input) being permanently coupled via a chain member to the second clutch (clutch 2) , the output (Out) being permanently coupled to the ring gears (R2, R3) .
2. The dual clutch transmission of claim 1, characterized in that two further synchronizers (Synclinput, Synclground; Sync2ground, Sync2direct) being permanently coupled to the transmission case or ground are provided for each deck (deck 1, deck 2; deck 3, deck 4); the third synchronizer (Synclinput) and the forth synchronizers (Synclground) being able to be alternately coupled to the sun gear (S2) of the second deck or to the carrier (CR12), the fifth synchronizer (Sync2ground) being able to be coupled to the carrier (CR43) or to the sun gear
(53) of the third deck (deck 3) and the sixth synchronizer ( Sync2direct ) being able to be alternately coupled or not to the carrier (CR43) in so-called on and off positions.
3. The dual clutch transmission of claim 2, characterized in that the first gear is engaged if the first clutch (Clutch 1) is activated and the third synchronizer (Synclinput) is off, the forth synchronizer (Synclground) is coupled to the sun gear (S2) and the first synchronizer (Syncl-Sunl) is coupled to the Input; the second gear is engaged if the second clutch (Clutch 2) is activated and the second synchronizer (Sync2input) is coupled to the sun gear (S4) of the forth deck (deck 4), the fifth synchronizer (Sync2ground) is coupled to the carrier (CR43) and the sixth synchronizer ( Sync2direct ) is off; the third gear is engaged if the first clutch (Clutch 1) is activated and the third synchronizer (Synclinput) is coupled to the sun gear (S2) of the second deck, the forth synchronizer (Synclground) is coupled to the carrier (CR12) and the first synchronizer (Syncl-Sunl) is off; the forth gear being engaged if the second clutch (Clutch 2) is activated, the second synchronizer (Sync2input) is coupled to the sun gear (S4) of the forth deck, the fifth synchronizer ( Sync2ground) is coupled to the sun gear (S3) of the third deck (deck 3) and the sixth synchronizer ( Sync2direct ) is off; the fifth gear being engaged if the first clutch (Clutch 1) is activated, the third synchronizer (Synclinput) is coupled to the sun gear (S2) of the second deck (deck 2), the forth synchronizer (Synclground) is off and the first synchronizer (Syncl-Sunl) is coupled to the ground; the sixth gear being engaged if the second clutch (Clutch 2) is activated, the third synchronizer (Sync2input) is coupled to the sun gear (S4) of the forth deck (deck 4), the fifth synchronizer (Sync2ground) is off and the sixth synchronizer (Sync2direct ) is on; the seventh gear being engaged if the first clutch (Clutch 1) is activated, the third synchronizer (Synclinput) is coupled to the carrier
(CR12), the forth synchronizer (Synclground) is off and the first synchronizer (Syncl-Sunl) is coupled to the ground; the eighth gear being engaged if the second clutch (Clutch 2) is activated, the second synchronizer
(Sync2input) is coupled to the carrier, the fifth synchronizer ( Sync2ground) is coupled to the sun gear
(S3) of the third deck (deck 3) , the sixth synchronizer
(Sync2direct ) is off and the reverse gear being engaged if the first clutch (Clutch 1) is activated, the third synchronizer (Synclinput) is off, the forth synchronizer
(Synclground) is coupled to the carrier (CR12) and the first synchronizer (Syncl-Sunl) is coupled to the input.
The dual clutch transmission of claim 1, characterized in that there is a blocking mechanism for securing the vehicle in park position .
PCT/EP2010/000400 2010-01-23 2010-01-23 Dual clutch transmission WO2011088849A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/EP2010/000400 WO2011088849A1 (en) 2010-01-23 2010-01-23 Dual clutch transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2010/000400 WO2011088849A1 (en) 2010-01-23 2010-01-23 Dual clutch transmission

Publications (1)

Publication Number Publication Date
WO2011088849A1 true WO2011088849A1 (en) 2011-07-28

Family

ID=42555618

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/000400 WO2011088849A1 (en) 2010-01-23 2010-01-23 Dual clutch transmission

Country Status (1)

Country Link
WO (1) WO2011088849A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105317943A (en) * 2014-07-31 2016-02-10 通用汽车环球科技运作有限责任公司 Automated manual transmission with dynamic torque transfer device
WO2017201361A1 (en) * 2016-05-19 2017-11-23 Dana Limited Planetary powertrain configurations with a ball variator continuously variable transmission used as a powersplit

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030232689A1 (en) * 2002-06-13 2003-12-18 Raymond James Haka Dual input clutch transmission having synchronizers for establishing speed ratios
EP1647736A2 (en) * 2004-10-12 2006-04-19 LuK Lamellen und Kupplungsbau Beteiligungs KG Power shift transmission, a motor vehicle gearbox and a vehicle drive train
DE102006028798A1 (en) 2006-06-23 2008-01-31 Zf Friedrichshafen Ag Double clutch
EP2085646A1 (en) * 2008-02-01 2009-08-05 GM Global Technology Operations, Inc. Automatic transmission

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030232689A1 (en) * 2002-06-13 2003-12-18 Raymond James Haka Dual input clutch transmission having synchronizers for establishing speed ratios
EP1647736A2 (en) * 2004-10-12 2006-04-19 LuK Lamellen und Kupplungsbau Beteiligungs KG Power shift transmission, a motor vehicle gearbox and a vehicle drive train
DE102006028798A1 (en) 2006-06-23 2008-01-31 Zf Friedrichshafen Ag Double clutch
EP2085646A1 (en) * 2008-02-01 2009-08-05 GM Global Technology Operations, Inc. Automatic transmission

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105317943A (en) * 2014-07-31 2016-02-10 通用汽车环球科技运作有限责任公司 Automated manual transmission with dynamic torque transfer device
US9377084B2 (en) * 2014-07-31 2016-06-28 GM Global Technology Operations LLC Automated manual transmission with dynamic torque transfer device
WO2017201361A1 (en) * 2016-05-19 2017-11-23 Dana Limited Planetary powertrain configurations with a ball variator continuously variable transmission used as a powersplit

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