WO2009129892A1 - Transmission à double embrayage - Google Patents

Transmission à double embrayage Download PDF

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Publication number
WO2009129892A1
WO2009129892A1 PCT/EP2009/001771 EP2009001771W WO2009129892A1 WO 2009129892 A1 WO2009129892 A1 WO 2009129892A1 EP 2009001771 W EP2009001771 W EP 2009001771W WO 2009129892 A1 WO2009129892 A1 WO 2009129892A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
dual
clutch transmission
transmission according
bearing device
Prior art date
Application number
PCT/EP2009/001771
Other languages
German (de)
English (en)
Inventor
Carsten Gitt
Martin Schetter
Original Assignee
Daimler 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 Daimler Ag filed Critical Daimler Ag
Publication of WO2009129892A1 publication Critical patent/WO2009129892A1/fr

Links

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
    • F16H57/00General details of gearing
    • F16H57/02Gearboxes; Mounting gearing therein
    • F16H57/021Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • 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 parallel flow paths, e.g. dual clutch transmissions
    • 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
    • F16H57/00General details of gearing
    • F16H57/0018Shaft assemblies for gearings
    • F16H57/0037Special features of coaxial shafts, e.g. relative support thereof
    • 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
    • F16H2003/0933Toothed 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 with coaxial countershafts
    • 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
    • F16H57/00General details of gearing
    • F16H57/02Gearboxes; Mounting gearing therein
    • F16H57/021Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F16H2057/0216Intermediate shaft supports, e.g. by using a partition wall
    • 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
    • F16H3/097Toothed 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 the input and output shafts being aligned on the same axis

Definitions

  • the invention relates to a dual-clutch transmission according to the preamble of claim 1.
  • the invention is in particular the object of increasing the load capacity of the dual-clutch transmission. It is achieved according to the invention by the features of claim 1. Further developments emerge from the subclaims.
  • the object of the invention has a dual-clutch transmission with at least four gear levels, of which at least two are provided as input constants and at least two translation stages, with at least two coaxially arranged input shafts, and with at least one input-side main bearing plane, an output-side main bearing plane and a central main bearing plane, as well an output shaft, which is mounted in at least a first bearing device and a second bearing device, which are arranged in two of the main bearing planes in a transmission housing, wherein the inner input shaft is supported by a third bearing device relative to the output shaft.
  • a “main storage level” is to be understood in particular as meaning a storage level which has at least one element which for a connection of a bearing device to a stationary bearing element, such as a gear housing, is provided.
  • a “bearing plane” is to be understood as meaning a plane extending perpendicularly to a longitudinal direction and having at least one bearing element.
  • a bearing device arranged in a bearing plane is to be understood as a bearing device which adjoins at least the corresponding bearing plane.
  • “Provided” is to be understood in particular to be specially equipped and / or designed.
  • the first input shaft is designed as an inner shaft which passes through the second designed as a hollow shaft input shaft. This allows a compact design for the dual-clutch transmission can be achieved with a high load capacity.
  • the third bearing device is provided to support the inner input shaft, whereby a particularly simple stable storage can be achieved for the inner input shaft.
  • the central main bearing plane is designed as a bearing wall. As a result, a particularly simple and stable main bearing level can be realized.
  • a coaxially arranged to the input shafts output shaft is proposed, since a particularly simple storage concept for the dual-clutch transmission can be found in an advantageous embodiment of gears, and also a so-called direct gear can be realized in which an input shaft to the output shaft directly or indirectly is connected and thus rotate both shafts at the same speed.
  • the first bearing device is arranged in the central main bearing plane and is intended to support the output shaft. As a result, a stable bearing for the output shaft can be realized by means of the central main bearing plane.
  • the first and the third bearing device are arranged coaxially with each other, whereby the bearing devices can be advantageously arranged with respect to a space.
  • the first and the third bearing device are arranged axially overlapping with respect to a longitudinal direction of the dual-clutch transmission.
  • an axial space can be further optimized.
  • the bearing devices can also be arranged with respect to the longitudinal direction of the transmission with an axial offset from one another.
  • a "longitudinal direction" is to be understood in particular as meaning a main extension direction of the dual-clutch transmission, which is given in particular by the course of the input shafts and the output line.
  • a fourth bearing device supports one of the input shafts with respect to a transmission housing and that a fifth bearing device supports another input shaft with respect to the aforementioned input shaft.
  • the input shafts can be stored very stable. This applies in particular if at least the fourth bearing device or the fifth bearing device is arranged in the input-side main bearing plane. This also applies if the two input shafts are supported by a sixth bearing device, which is preferably located on the input side of the front main bearing plane with respect to the longitudinal direction of the transmission.
  • the dual-clutch transmission in addition to a first countershaft a second designed as a hollow shaft countershaft and arranged in the central main bearing level seventh bearing device, which is intended to store the second countershaft, and alternatively or additionally arranged in the central main bearing level eighth bearing device for storage the first countershaft compared to the second countershaft.
  • the middle main bearing plane can advantageously be used for storage and it can be moved to a main bearing plane which lent to the storage of the countershaft is provided, are omitted, with the second countershaft can be stored in a simple manner stable.
  • the seventh and eighth bearing devices are arranged coaxially and / or overlapping with respect to a longitudinal direction. Thereby, a particularly stable storage can be achieved and it can also space that is occupied by the storage devices can be reduced.
  • the fourth and / or fifth bearing device is designed as a fixed bearing.
  • a "fixed bearing” is to be understood as meaning, in particular, a bearing device which fixes a mounted element in all three directions of translation and permits only one rotation, In particular, it is proposed that at least one bearing device per shaft be designed as a fixed bearing.
  • At least the third bearing device is designed as a loose-end bearing.
  • a "floating bearing” is to be understood in particular as a bearing device which permits a movement of the rotatably mounted element in at least one direction, preferably along the axis of rotation.
  • At least one bearing device has a tapered roller bearing.
  • a particularly advantageous storage device can be realized.
  • the dual-clutch transmission has a transmission housing with two transmission housing parts and a connection unit which is provided to connect the transmission housing parts.
  • the storage concept can be easily integrated into the transmission housing and in particular a mounting can be simplified.
  • connection unit which is intended to connect the central main bearing plane with the transmission housing.
  • the central main bearing plane can be easily fixed and connected to the transmission housing.
  • the connection unit of the central main bearing level should be provided to connect the central main bearing plane with at least one gear housing part. As a result, in particular a firm connection between the main bearing levels can be established.
  • connection unit of the central main bearing level and the connection unit of the gear housing are at least partially made in one piece. This can reduce costs for the connection units.
  • connection unit has at least one screw element. This allows a particularly simple and inexpensive connection unit can be realized.
  • the central main bearing plane has at least a first bearing wall element and a second bearing wall element, whereby a multi-part design and thus a simple fastening concept for the bearing devices can be realized simply.
  • a two-part design is advantageous.
  • the first bearing wall element on a bearing seat which is intended to receive the first bearing device for the output shaft.
  • a bearing seat is to be understood, in particular, as an embodiment of the main bearing plane, which is intended to receive a bearing device.
  • a force for a connection of the bearing device to the main bearing plane is essentially, i.e. more than 50%, passed over the corresponding bearing seat and the bearing seat thereby substantially contributes to the reception of the bearing device.
  • the second bearing wall element has a bearing seat, which is intended to receive the seventh bearing device for the countershaft.
  • a receptacle for the bearing of the countershaft can be realized, which can be particularly independent of the receptacle for the storage of the output shaft.
  • at least one of the bearing seats adjoin at least the first bearing wall element and the second bearing wall element. As a result, a simple assembly with high strength can be achieved.
  • Fig. 1 is a schematic representation of a dual clutch transmission in a first embodiment
  • Fig. 2 is a schematic representation of a Doppelkijnp h j ⁇ g ⁇ gGtriebes in a second embodiment.
  • FIG. 1 shows a dual-clutch transmission of an exemplary gear arrangement.
  • the dual-clutch transmission has two input shafts 10, 11 and an output shaft 26.
  • the input shafts 10, 11 are arranged coaxially, wherein the first inner input shaft 10 is formed as an inner shaft, which passes through the second outer input shaft 11, which is formed as a hollow shaft.
  • the output shaft 26 is arranged coaxially with the input shafts 10, 11.
  • the dual clutch transmission gears which are partially formed as loose wheels and partially as fixed wheels.
  • the gears are arranged in seven gear levels E1, E2, Z1, Z2, Z3, Z4, Z5.
  • Two gear levels are provided as input constants E1, E2 and are non-rotatably connected or connectable to at least one of the input shafts.
  • a further gear level Z1 can be used both as an input constant and as a gear pair to form a gear stage, in particular a forward gear, and can be connected to both the inner input shaft 10 and the output shaft 26 get connected.
  • the remaining gear levels Z2, Z3, Z4, Z5 are provided as translation stages for the forward gears and for reverse gears.
  • the dual-clutch transmission For storage of the two input shafts 10, 11, the output shaft 26 and the two countershafts 27, 28, the dual-clutch transmission according to Figure 1 has a storage concept with 10 storage devices 15-24, which is basically independent of the gear arrangement shown in Figure 1. According to the embodiment of Figure 2, the Doppelkupplungsg p gear two more Lsgervorrichturiye ⁇ L and ⁇ vl on. Furthermore, the storage concept is basically also applicable to dual-clutch transmission with two coaxial input shafts, which have a different number of gear levels than the dual-clutch transmission shown.
  • the dual-clutch transmission has three main bearing levels 12, 13, 14 and a bearing plane 38 in which the bearing devices 15-24 are arranged.
  • the coaxially arranged storage devices of a main storage level or storage level are arranged completely overlapping axially with respect to a longitudinal direction of the dual clutch transmission.
  • these can also be arranged only partially axially overlapping or axially offset adjacent to each other, as shown in FIG.
  • the storage devices thus have particularly advantageous their axial center on a main storage level or storage level.
  • a position of the axial center of the bearing device in the spatial vicinity of a main bearing plane or bearing plane is possible.
  • the fifth bearing device 15 axially overlapping, but offset in the direction of the gear plane E1, or according to the embodiment of Figure 2 no longer axially overlapping, but adjacent to the gear plane E1, be arranged with the fourth bearing device 17.
  • the fourth storage device 17 and the fifth storage device 15 are always arranged coaxially.
  • the third bearing device 16 axially offset in the direction of the gear level Z2, even to between the gear levels Z1 and Z2, but advantageously still between the gear level Z2 and located between the gear levels Z1 and Z2 shift sleeve to the first bearing device 18 may be arranged.
  • the input-side main bearing plane 12 is formed by means of the first gear housing part 30 and arranged in front of the first gear level E1.
  • the output-side main bearing plane 13 is formed by means of the second gear housing part 31. It is arranged after the last gear level Z5.
  • the central main bearing plane 14 is arranged between the input-side main bearing plane 12 and the output-side main bearing plane 13, the central main bearing plane 14 is arranged.
  • the central main bearing plane 14 is formed by means of a bearing wall 25. It is arranged in the axial direction between the fourth gear plane Z2 and the fifth gear plane Z3.
  • gear levels E1, E2, Z1, Z2 by one greater than a number of gear levels Z3, Z4, Z5, which are arranged behind the central main bearing plane 14.
  • the bearing plane 38 is arranged in the second gear level E2.
  • the central main bearing plane 14, which is formed by means of the bearing wall 25, is connected via a connecting unit 33 to the two gear housing parts 30, 31.
  • the connecting unit 32 which connects the gear housing parts 30, 31 with each other
  • the connecting unit 33 which connects the central main bearing plane 14 with the gear housing parts 30, 31, made in one piece.
  • the connecting units 32, 33 have common screw elements 39, 40 which pass through the two gear housing parts 30, 31 and the central main bearing plane 14 or the bearing wall 25 and connect them to one another.
  • the fifth bearing device 15 is arranged in the input-side main bearing plane 12.
  • the third storage Device 16 is arranged in the central main storage level 14.
  • the fifth bearing device 15 supports the inner input shaft 10 against the outer input shaft 11.
  • the third bearing device 16 supports the inner input shaft 10 against the output shaft 26.
  • the fifth bearing device 15 is designed as a fixed bearing, the third bearing device 16 as a floating bearing.
  • the dual-clutch transmission can advantageously have a sixth bearing device L on the input side of the main input bearing plane 12, which supports the inner input shaft 10 with respect to the outer input shaft 11, and / or a ninth bearing device M on the input side of a double clutch the inner input shaft 10 opposite to an input shaft of the double clutch, which is arranged radially outside of the inner input shaft 10, have.
  • the fourth bearing device 17 supports the outer input shaft 11 directly in the input-side main bearing plane 12, whereby the outer input shaft 11 is mounted directly against the front gear housing part 30.
  • the fourth bearing device 17 of the outer input shaft 11 and the fifth bearing device 15 of the inner input shaft 10 the inner input shaft 10 is mounted indirectly in the first main bearing plane 12 and thus indirectly against the front gear housing part 30.
  • the fourth bearing device 17 of the outer input shaft 11 is designed as a fixed bearing.
  • the first bearing device 18 of the output shaft 26 is arranged in the central main bearing plane 14.
  • the second bearing device 19 is arranged in the output-side main bearing plane 13.
  • the first bearing device 18 supports the output shaft 26 directly in the central main bearing plane 14 and thus against the bearing wall 25.
  • the second bearing device 19 supports the output shaft 26 directly in the output side main bearing plane 13 and thus directly against the rear gear housing part 31.
  • the third storage device 16 and the first storage device 18 are coaxial and intersecting with respect to a longitudinal direction.
  • the first bearing device 18 of the output shaft is designed as a movable bearing, the second bearing device 19 as a fixed bearing.
  • the dual-clutch transmission has the eighth bearing device 21, the tenth bearing device 20 and the eleventh bearing device 22, which are each arranged in one of the three main bearing planes 12, 13, 14.
  • the tenth bearing device 20 supports the inner countershaft 27 directly in the input-side main bearing plane 12.
  • the eighth bearing device 21 supports the inner countershaft 27 against the central main bearing plane 14 and the eleventh bearing device 22 directly supports the inner countershaft 27 against the output-side main bearing plane 13
  • the tenth bearing device 20 and the eleventh bearing device 22 are designed as floating bearings.
  • the eighth bearing device 21 is designed as a fixed bearing.
  • the twelfth bearing device 23 is arranged in the bearing plane 38 between the input-side main bearing plane 12 and the central main bearing plane 14 and supports the outer countershaft 28 against the inner countershaft 27.
  • the seventh bearing device 24 is disposed in the central main bearing plane 14 and supports the outer countershaft 28 directly in the central main bearing plane 14, whereby the inner countershaft 27 via the eighth bearing device 21 of the inner countershaft 27 and the seventh bearing device 24 of the outer countershaft 28 is mounted indirectly in the central main bearing plane 14 and thus indirectly against the bearing wall 25.
  • the eighth bearing device 21 and the seventh bearing device 24 are coaxial and intersecting with respect to the longitudinal direction.
  • the twelfth bearing device 23 of the outer countershaft 28 is designed as a floating bearing.
  • the seventh bearing device 24 of the outer countershaft 28 is designed as a fixed bearing.
  • All storage devices 15-24 are designed as rolling bearings. In principle, however, other embodiments are conceivable. Also, another arrangement of the floating bearing and the fixed bearing is conceivable.
  • the middle Main bearing plane 14 has a first bearing wall element 34 with a bearing seat 36 for the first bearing device 18 of the output shaft 26. Furthermore, the central main bearing plane 14 has a second bearing wall element 35 with a bearing seat 37 for the seventh bearing device 24 of the outer countershaft 28. The first bearing wall element 34 also adjoins the bearing seat 37 of the second bearing wall element 35. However, a connection of the seventh bearing device 24 of the outer countershaft 28 takes place essentially via the bearing seat 37 of the second bearing wall element 35.
  • the bearing wall 25 may alternatively be made in one piece.

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

Abstract

Pour augmenter la résistance de la transmission à double embrayage, celle-ci comporte au moins quatre plans de roues dentées (E1, E2, Z1, Z2, Z3, Z4, Z5) dont au moins deux plans sont prévus en tant que constantes d'entrée (E1, E2, Z1) et au moins deux autres plans sont prévus en tant qu'étages de multiplication (Z1, Z2, Z3, Z4, Z5). La transmission à double embrayage comporte également au moins deux arbres d'entrée (10, 11) disposés de façon coaxiale, au moins un plan de palier principal côté entrée (12), un plan de palier principal côté sortie (13), un plan de palier principal central (14) et un arbre de sortie (26) logé dans un carter de transmission (29) au moyen d'un premier dispositif de palier (18) et d'un deuxième dispositif de palier (19) disposés dans deux plans de palier principaux (13, 14). L'arbre d'entrée intérieur (10) est logé au moyen d'un troisième dispositif de palier (16) par rapport à l'arbre de sortie (26).
PCT/EP2009/001771 2008-04-22 2009-03-12 Transmission à double embrayage WO2009129892A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102008020232 2008-04-22
DE102008020232.0 2008-04-22
DE102008023146A DE102008023146A1 (de) 2008-04-22 2008-05-09 Doppelkupplungsgetriebe
DE102008023146.0 2008-05-09

Publications (1)

Publication Number Publication Date
WO2009129892A1 true WO2009129892A1 (fr) 2009-10-29

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ID=41111907

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2009/001771 WO2009129892A1 (fr) 2008-04-22 2009-03-12 Transmission à double embrayage

Country Status (2)

Country Link
DE (1) DE102008023146A1 (fr)
WO (1) WO2009129892A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3575638A1 (fr) * 2018-06-01 2019-12-04 Mazda Motor Corporation Transmission de véhicule et son procédé de fabrication

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109139819A (zh) * 2018-09-27 2019-01-04 安徽江淮汽车集团股份有限公司 一种双离合器变速器传动机构

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2386540A (en) * 1943-09-17 1945-10-09 John J Campodonico Multispeed gear transmission
US2732727A (en) * 1956-01-31 Automatic fluid pressure transmission
JPS59140941A (ja) * 1983-01-28 1984-08-13 Hino Motors Ltd 自動トランスミツシヨン
DE3913091A1 (de) * 1989-04-21 1990-10-25 Porsche Ag Gangschaltgetriebe fuer ein kraftfahrzeug
EP0976952A1 (fr) * 1998-07-28 2000-02-02 Renault Boíte de vitesses comportant des paliers d'arbres portés par deux demi-cloisons intérieures
EP1566569A1 (fr) * 2004-02-20 2005-08-24 Mazda Motor Corporation Transmission à double embrayage permettant de transmettre de l' énergie motrice
DE102004043386A1 (de) * 2004-09-08 2006-04-13 Zf Friedrichshafen Ag Getriebevorrichtung in Vorgelegebauweise
DE102005005338B3 (de) * 2005-01-27 2006-08-10 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Stufenwechselgetriebe
WO2008018477A1 (fr) * 2006-08-08 2008-02-14 Isuzu Motors Limited Transmission à double embrayage du type à reduction de vitesse d'arbre de sortie

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2732727A (en) * 1956-01-31 Automatic fluid pressure transmission
US2386540A (en) * 1943-09-17 1945-10-09 John J Campodonico Multispeed gear transmission
JPS59140941A (ja) * 1983-01-28 1984-08-13 Hino Motors Ltd 自動トランスミツシヨン
DE3913091A1 (de) * 1989-04-21 1990-10-25 Porsche Ag Gangschaltgetriebe fuer ein kraftfahrzeug
EP0976952A1 (fr) * 1998-07-28 2000-02-02 Renault Boíte de vitesses comportant des paliers d'arbres portés par deux demi-cloisons intérieures
EP1566569A1 (fr) * 2004-02-20 2005-08-24 Mazda Motor Corporation Transmission à double embrayage permettant de transmettre de l' énergie motrice
DE102004043386A1 (de) * 2004-09-08 2006-04-13 Zf Friedrichshafen Ag Getriebevorrichtung in Vorgelegebauweise
DE102005005338B3 (de) * 2005-01-27 2006-08-10 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Stufenwechselgetriebe
WO2008018477A1 (fr) * 2006-08-08 2008-02-14 Isuzu Motors Limited Transmission à double embrayage du type à reduction de vitesse d'arbre de sortie

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3575638A1 (fr) * 2018-06-01 2019-12-04 Mazda Motor Corporation Transmission de véhicule et son procédé de fabrication

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Publication number Publication date
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