WO2003025431A1 - Boites de vitesses automatique a plusieurs vitesses - Google Patents

Boites de vitesses automatique a plusieurs vitesses Download PDF

Info

Publication number
WO2003025431A1
WO2003025431A1 PCT/EP2002/009623 EP0209623W WO03025431A1 WO 2003025431 A1 WO2003025431 A1 WO 2003025431A1 EP 0209623 W EP0209623 W EP 0209623W WO 03025431 A1 WO03025431 A1 WO 03025431A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
speed vehicle
vehicle transmission
transmission according
automated multi
Prior art date
Application number
PCT/EP2002/009623
Other languages
German (de)
English (en)
Inventor
Wolfgang Rieger
Gerhard Gumpoltsberger
Jürgen WAFZIG
Detlef Baasch
Ralf Dreibholz
Markus Knobelspies
Original Assignee
Zf Friedrichshafen Ag
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 Zf Friedrichshafen Ag filed Critical Zf Friedrichshafen Ag
Publication of WO2003025431A1 publication Critical patent/WO2003025431A1/fr

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
    • 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
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • 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
    • 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
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths

Definitions

  • the invention relates to an automated multi-speed vehicle transmission, in which a plurality of power paths are provided between an input shaft and an output shaft for shifting the gears, which are summed in a planetary gear summing gear, the ratio being variable in at least one of the power paths.
  • Automated manual transmissions which are generally known from practice, are based predominantly on the principle of conventional manual transmissions in countershaft construction, in which a shift is implemented with the aid of synchronizations.
  • Such transmissions have relatively small shift elements, but the performance-determining elements, such as spur gear stages, require a large installation space and are also cost-intensive.
  • Gearbox types are known from practice which try to take advantage of the countershaft gearbox the small shifting elements and the advantages of the powershift automatic transmission with planetary gear sets with regard to the compact gears, by providing a planetary gear shift set in a countershaft transmission, in which case there is a group transmission with a purely geometrical gradation.
  • One problem here is that the gradation is very low in lower gears, while it is very large in higher gears, which makes driving more difficult for passenger cars.
  • Another known transmission design is represented by so-called power split transmissions or multi-range transmissions, which can realize many driving ranges with just a few shift elements.
  • a combination of features of the transmission types described above shows a transmission described in US Pat. No. 5,013,289, which has a countershaft transmission area and two planetary gears. Three power paths are provided between a transmission input shaft and an output which is not arranged coaxially for this purpose, in which the gear ratio can be changed by means of a load shift. By providing three power paths that can be connected to the planetary gear sets, six forward gears can be realized with a relatively small number of switching elements.
  • a multi-speed vehicle transmission of the type mentioned at the outset, in which at least one gear ratio is switched positively, offers the advantage that it has a significantly simpler and more cost-effective construction than planetary powershift transmissions, since at least some of the complex hydraulic systems for the shifting elements are dispensed with can. Due to the lack of or at least less use of hydraulics with the associated drag losses, better efficiency is achieved.
  • a multi-speed vehicle transmission as a six-speed transmission, e.g. Two power de can be provided, the planetary gear summing gear being designed as a three-shaft gear with a simple planetary gear.
  • a transmission is e.g. Realizable with four countershaft levels instead of seven countershaft levels and only six instead of seven synchronizations.
  • the multi-speed vehicle transmission according to the invention can be equipped in an advantageous embodiment with three performance paths, the planetary gear set summing gear being designed as a four-shaft gear unit with a double planetary gear set. Two wheel planes and five synchronizations are sufficient to implement six forward gears.
  • more than three power paths can also be provided, the planetary gear summing gear then being constructed from at least four shafts.
  • the translations in the individual performance paths can also be the same, it is usually still expedient if the performance paths have different translations.
  • the translation must be changeable in at least one of the performance paths.
  • the translations are not continuously variable. riabel, but designed as spur gear ratios or as a direct connection, preferably all of which are positively connected by synchronizations or claw couplings, each of which connects two shafts or a shaft and a housing.
  • the arrangement of the switching elements is preferably selected so that the synchronizations or claw clutches are combined into pairs and can be switched as synchronous or claw packets with a power actuation, i.e. that, for example, in an advantageous embodiment, two dog clutches can be actuated by a shift fork, only one or none of the dog clutches being actuated in each case.
  • Fig.l is a schematic diagram of a first variant of an automated multi-speed
  • the summing gear has a simple planetary gear set
  • 2a shows a transmission diagram of an exemplary embodiment of the first variant of the multi-speed vehicle transmission according to the invention
  • FIG. 2b shows a switching logic belonging to the transmission diagram according to FIG. 2a;
  • FIG. 3a shows a transmission diagram of a further exemplary embodiment of the first variant of the multi-speed vehicle transmission according to the invention
  • FIG. 3b shows a switching logic belonging to the transmission diagram according to FIG. 3a;
  • FIG. 4a shows a transmission diagram of a further exemplary embodiment of the first variant of the multi-speed vehicle transmission according to the invention.
  • FIG. 4b shows a switching logic belonging to the transmission diagram according to FIG. 4a
  • FIG. 5 shows a basic diagram of a second variant of a multi-speed vehicle transmission according to the invention, the summation transmission of which has a double planetary gear set;
  • 6a shows a transmission diagram of an exemplary embodiment of the multi-speed vehicle transmission according to the second variant according to FIG. 4;
  • FIG. 6b shows a switching logic belonging to the transmission diagram according to FIG. 6a
  • 7a shows a transmission diagram of a second exemplary embodiment of a multi-speed vehicle transmission according to the second variant according to FIG. 4
  • FIG. 7b shows a shifting logic belonging to the transmission scheme according to FIG. 7a.
  • FIG. 1 shows a basic diagram of a first variant of an automated multi-speed vehicle transmission 1, which in the present case has six forward gears and one reverse gear.
  • the vehicle transmission 1 has, between an input shaft or drive shaft 2 and an output shaft 3 connected to an output, a countershaft transmission 4 and a planetary gear summing gear 5, which in the present case is a differential and is designed as a three-shaft gear with a simple planetary gear set.
  • the power of the input shaft 2 can be divided into two power paths P1, P2, a first power path P1 being connected to a first shaft 6 and a second power path P2 being connected to a second shaft 7 of the three-shaft transmission 5.
  • the third shaft of the three-shaft gear 5 represents the output shaft 3 connected to the output.
  • translation stages il, i2 and i3 are provided, which are preferably designed in the countershaft design.
  • first power path P1 two fixed translations i1, i2 arranged in parallel are provided, which can be connected via assigned clutches K1 or K2.
  • second power path P2 Translation ⁇ 3 is also a fixed one in the second power path P2 Translation ⁇ 3 provided that can be switched into the power flow via an associated clutch K3.
  • a reverse gear can be achieved either by an additional spur gear stage with integrated speed reversal or by a speed reversal in the planetary gear set.
  • FIGS. 2a and 2b show a transmission and shifting diagram of such an automated multi-speed vehicle transmission.
  • six shifting elements or clutches A, B, C, D, E and F that are to be switched as well as a planetary gear summing gear 5 designed as a three-shaft gear are provided.
  • a reverse gear 8 is also provided between the clutch C and the countershaft 9.
  • the gearshifts are made via synchronizers 39 or dog clutches.
  • the planetary gear set summing gear 5 is a simple planetary gear set, which has planet gears 12 that roll between a sun gear 10 and a ring gear 11, the planet gear carriers of which are firmly connected to the output shaft 3 leading to the output.
  • the gear step is progressive, ie that the Jump of the ratio i between the gears with increasing number of gears becomes less and less.
  • FIGS. 3a and 3b show a transmission diagram essentially corresponding to the embodiment according to FIGS. 2a and 2b, with associated shift logic, with a greater spread of the transmission here due to the design of the planetary gear summing transmission 5 with between a sun gear 13 and a with the output shaft 3 fixedly connected ring gear 14 radially adjacent planet gears 15, 16 which are mounted on a common planet carrier 17 is achieved.
  • FIGS. 4a and 4b show a further variant of the gear shift with the associated shift logic, which essentially corresponds to the embodiment according to FIGS. 2a and 2b as well as FIGS. 3a and 3b, which is why the analog gear components are not further discussed here is received.
  • the reverse gear is not realized by a spur gear stage with an intermediate gear as in the embodiment according to FIGS. 2a and 3a, but by a reversal of the direction of rotation in the planetary gear set of the planetary gear set 5.
  • Such a reversal of the direction of rotation is achieved by holding and supporting a ring gear 53 Planet set reached by means of the switching element A on a housing 40 of the transmission.
  • FIG. 5 shows a schematic diagram of a second variant of an automated six-speed vehicle transmission 1.
  • the power of the input shaft 2 can be separated into three power paths P10, P20 and P30, which via corresponding input shafts 18, 19, 20 Planet gear summing gear 50 mouth, which is designed here as a double differential in the form of a four-shaft gear with a double planetary gear.
  • three performance paths P10, P20 and P30 with the respective assigned ratios ilO, i20, i30 and clutches K10, K20, K30 as well as two shift elements or brakes Bl and B2 supported on the transmission housing, six forward gears and one reverse gear can be carried out.
  • Two of the three power paths P10, P20 and P30 are combined in the planetary gear summing gear 5.
  • an additional clutch can also be provided between two of the power paths.
  • FIGS. 6a and 6b An exemplary embodiment of such a variant of a multi-speed vehicle transmission is shown in FIGS. 6a and 6b, which for shifting six forward gears five shifting elements A, B, C, D, E to be switched and a planetary gear summing gear 50 which represents a four-shaft transmission with two planetary gear sets.
  • the planetary gear summing gear 50 here consists of a common ring gear 21, which is fixedly connected to the output shaft 3 leading to the output, two sun gears 22, 23 of different sizes, and planet gears 24, 25 of different lengths which roll between them and the ring gear 21 and which have a common length Have planet carrier 26.
  • the planetary gear summing gear 50 thus essentially corresponds to a known Ravigneaux gear.
  • connection to the countershaft 27 is established via two wheel planes 28, 29.
  • 7a and 7b show a further exemplary embodiment of the second variant of an automated multi-speed vehicle transmission according to the invention, in which the planetary gear summing gear 50 is a typical four-shaft set with a common sun gear 30, two ring gears
  • the output shaft 3 is connected to one of the planet carriers 34.
  • the planetary gear summing gear 50 is arranged in the power train between the all form-fitting shifting elements A, E, C on the one hand and B, F on the other hand, the planetary gear arrangement being simpler to build, because the lateral forces of the spur gear stages are supported close to the housing.
  • the countershaft 35 can be connected to the input shaft 2 and the shifting elements via three wheel planes 36, 37, 38.
  • the gear ratio is designed progressively both in the embodiment according to FIGS. 6a and 6b and in the embodiment according to FIGS. 7a and 7b.
  • the multi-speed vehicle transmission according to the invention is of course not limited to the designs shown as a six-speed vehicle transmission, but is also suitable for transmissions with a different, in particular higher number of gears.
  • the arrangement of the individual elements in the exemplary embodiments shown is also not mandatory, since, for example, the planetary gear summation gear, as already shown in the embodiment according to FIG. 6, can be arranged at different points between the input shaft and the output shaft of the vehicle transmission.
  • each gear ratio is switched positively, it can also be provided that non-positive or frictional shifting elements are used in addition to the positively locking shifting elements.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L'invention concerne une boîte de vitesses automatique à plusieurs vitesses. Pour sélectionner les vitesses, plusieurs voies de sortie sont prévues entre un arbre d'entrée et un arbre de sortie, ces voies de sortie étant cumulées dans une boîte de cumul à train planétaire. Dans au moins une voie de sortie, la démultiplication peut être modifiée étagée. Au moins une démultiplication est commandée par liaison de forme.
PCT/EP2002/009623 2001-09-14 2002-08-29 Boites de vitesses automatique a plusieurs vitesses WO2003025431A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10145519.4 2001-09-14
DE2001145519 DE10145519A1 (de) 2001-09-14 2001-09-14 Automatisiertes Mehrgang-Fahrzeuggetriebe

Publications (1)

Publication Number Publication Date
WO2003025431A1 true WO2003025431A1 (fr) 2003-03-27

Family

ID=7699150

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2002/009623 WO2003025431A1 (fr) 2001-09-14 2002-08-29 Boites de vitesses automatique a plusieurs vitesses

Country Status (2)

Country Link
DE (1) DE10145519A1 (fr)
WO (1) WO2003025431A1 (fr)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006032312A1 (fr) 2004-09-23 2006-03-30 Daimlerchrysler Ag Transmission automatique pour un véhicule à moteur et procédé pour la faire fonctionner
GB2471859A (en) * 2009-07-15 2011-01-19 Alvan Burgess Transmission comprising an infinitely variable drive and a differential
US8287416B2 (en) 2010-03-31 2012-10-16 GM Global Technology Operations LLC Eight-speed planetary layshaft transmission
US8360925B2 (en) 2010-03-01 2013-01-29 GM Global Technology Operations LLC Multi-speed transmission with compound and simple planetary gear sets and with layshafts
US8360923B2 (en) 2010-03-19 2013-01-29 GM Global Technology Operations LLC Multi-speed transmission with planetary gear sets and layshafts
US8360919B2 (en) 2010-03-31 2013-01-29 GM Global Technology Operations LLC Multi-speed transmission
US8360924B2 (en) 2010-02-25 2013-01-29 GM Global Technology Operations LLC Multi-speed planetary transmission with two planetary gear sets and up to ten forward speed ratios
US8360918B2 (en) 2010-03-31 2013-01-29 GM Global Technology Operations LLC Multi-speed transmission with planetary and layshaft gears
US8360922B2 (en) 2010-02-25 2013-01-29 GM Global Technology Operations LLC Multi-speed planetary transmission with up to ten forward speed ratios
US8398524B2 (en) 2010-03-19 2013-03-19 GM Global Technology Operations LLC Multi-speed transmission with eight torque-transmitting mechanisms
US8439787B2 (en) 2010-03-19 2013-05-14 GM Global Technology Operations LLC Transmission with mixed planetary layshaft structure
US8540600B2 (en) 2010-03-03 2013-09-24 GM Global Technology Operations LLC Multi-speed planetary transmission with three brakes and four clutches
US11209075B2 (en) * 2019-07-22 2021-12-28 Deere & Company Transmission

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10250480B4 (de) * 2002-10-30 2018-02-01 Zf Friedrichshafen Ag Automatisiertes Mehrgang-Schaltgetriebe
DE10315313A1 (de) * 2003-04-04 2005-01-20 Zf Friedrichshafen Ag Getriebe, insbesondere automatisiertes leistungsverzweigtes Mehrganggetriebe
DE10322234A1 (de) * 2003-05-17 2004-12-23 Zf Friedrichshafen Ag Leistungsverzweigtes, schaltbares Zweigang-Getriebe, insbesondere für eine Schiffsantriebsanlage
DE102011105065A1 (de) * 2011-06-21 2012-12-27 GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) Zweiwellenschaltgetriebe für ein Kraftfahrzeug
DE102019007129B4 (de) * 2019-10-14 2021-09-23 Daimler Ag Gruppengetriebevorrichtung, insbesondere Splitgetriebe

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE555298C (de) * 1927-02-27 1932-07-21 Herbert Mewitz Stufenloses Getriebe
US4662240A (en) * 1984-11-26 1987-05-05 Leyland Vehicles Limited Continuously variable transmission
US4682511A (en) * 1985-10-18 1987-07-28 Wittke Ernest C Gear assisted continuously variable transmission
DE19631216A1 (de) * 1995-08-23 1997-03-20 Luk Getriebe Systeme Gmbh Getriebeeinheit
DE19944792A1 (de) * 1998-09-19 2000-04-27 Michael Meyerle Stufenloses Getriebe, insbesondere mit Leistungsverzweigung

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2708524C3 (de) * 1977-02-26 1981-10-22 Getrag Getriebe- Und Zahnradfabrik Gmbh, 7140 Ludwigsburg Schaltgetriebe für Personenkraftwagen und Nutzfahrzeuge
FR2522100B1 (fr) * 1982-02-22 1987-04-24 Valeo Transmission entre une prise de mouvement et un arbre recepteur, notamment pour vehicule automobile
US5013289A (en) * 1990-02-20 1991-05-07 General Motors Corporation Power transmission
KR100262593B1 (ko) * 1996-12-17 2000-08-01 정몽규 차량용 무단 변속장치
DE19949507B4 (de) * 1999-10-14 2014-10-23 Zf Friedrichshafen Ag Mehrstufengetriebe

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE555298C (de) * 1927-02-27 1932-07-21 Herbert Mewitz Stufenloses Getriebe
US4662240A (en) * 1984-11-26 1987-05-05 Leyland Vehicles Limited Continuously variable transmission
US4682511A (en) * 1985-10-18 1987-07-28 Wittke Ernest C Gear assisted continuously variable transmission
DE19631216A1 (de) * 1995-08-23 1997-03-20 Luk Getriebe Systeme Gmbh Getriebeeinheit
DE19944792A1 (de) * 1998-09-19 2000-04-27 Michael Meyerle Stufenloses Getriebe, insbesondere mit Leistungsverzweigung

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006032312A1 (fr) 2004-09-23 2006-03-30 Daimlerchrysler Ag Transmission automatique pour un véhicule à moteur et procédé pour la faire fonctionner
GB2471859A (en) * 2009-07-15 2011-01-19 Alvan Burgess Transmission comprising an infinitely variable drive and a differential
US8360924B2 (en) 2010-02-25 2013-01-29 GM Global Technology Operations LLC Multi-speed planetary transmission with two planetary gear sets and up to ten forward speed ratios
US8360922B2 (en) 2010-02-25 2013-01-29 GM Global Technology Operations LLC Multi-speed planetary transmission with up to ten forward speed ratios
US8360925B2 (en) 2010-03-01 2013-01-29 GM Global Technology Operations LLC Multi-speed transmission with compound and simple planetary gear sets and with layshafts
US8540600B2 (en) 2010-03-03 2013-09-24 GM Global Technology Operations LLC Multi-speed planetary transmission with three brakes and four clutches
US8360923B2 (en) 2010-03-19 2013-01-29 GM Global Technology Operations LLC Multi-speed transmission with planetary gear sets and layshafts
US8398524B2 (en) 2010-03-19 2013-03-19 GM Global Technology Operations LLC Multi-speed transmission with eight torque-transmitting mechanisms
US8439787B2 (en) 2010-03-19 2013-05-14 GM Global Technology Operations LLC Transmission with mixed planetary layshaft structure
US8360919B2 (en) 2010-03-31 2013-01-29 GM Global Technology Operations LLC Multi-speed transmission
US8360918B2 (en) 2010-03-31 2013-01-29 GM Global Technology Operations LLC Multi-speed transmission with planetary and layshaft gears
US8287416B2 (en) 2010-03-31 2012-10-16 GM Global Technology Operations LLC Eight-speed planetary layshaft transmission
US11209075B2 (en) * 2019-07-22 2021-12-28 Deere & Company Transmission

Also Published As

Publication number Publication date
DE10145519A1 (de) 2003-04-03

Similar Documents

Publication Publication Date Title
EP1611370B1 (fr) Boite de vitesses automatique a plusieurs etages
EP1373756B1 (fr) Demultiplicateur a plusieurs etages
EP1611373B1 (fr) Transmission, en particulier transmission a plusieurs vitesses automatisees a derivation de puissance
DE3610577C2 (de) Automatisches Getriebe
EP2899427B1 (fr) Boîte de vitesses d'un véhicule automobile
EP2558745B1 (fr) Train d'engrenages à double embrayage et procédé pour actionner un train d'engrenages à double embrayage
EP1841984B1 (fr) Boite de vitesses a double embrayage
WO2003025431A1 (fr) Boites de vitesses automatique a plusieurs vitesses
WO2005093289A1 (fr) Boite de vitesses a double embrayage
WO2002079671A2 (fr) Boite de vitesses a plusieurs etages
WO2014121957A1 (fr) Groupe-relais d'un véhicule à moteur
WO2002079665A2 (fr) Transmission a plusieurs etages
DE10213820A1 (de) Automatikgetriebe für ein Fahrzeug
DE102006038193A1 (de) Gruppengetriebe für ein Kraftfahrzeug
WO2009018969A1 (fr) Boîte de vitesses à double embrayage
WO2011157479A1 (fr) Transmission à embrayage double
DE602005004659T2 (de) Mehrstufiges automatikgetriebe für personenkraftfahrzeuge oder nutzfahrzeuge
WO2014067632A1 (fr) Boîte de vitesses à double embrayage
DE10250480B4 (de) Automatisiertes Mehrgang-Schaltgetriebe
DE102006001646B4 (de) Lastschaltgetriebe
DE102005057802A1 (de) Doppelkupplungsgetriebe
EP0221120A1 (fr) Boite de vitesses a roues planetaires
DE102010055643A1 (de) Automatisches, insbesondere automatisiertes Schaltgetriebe für ein Kraftfahrzeug
DE10250371A1 (de) Automatikgetriebe
DE112011105576B4 (de) Mehrkupplungsgetriebe für ein Kraftfahrzeug

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): JP

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FR GB GR IE IT LU MC NL PT SE SK TR

121 Ep: the epo has been informed by wipo that ep was designated in this application
DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
122 Ep: pct application non-entry in european phase
NENP Non-entry into the national phase

Ref country code: JP

WWW Wipo information: withdrawn in national office

Country of ref document: JP