WO2013004416A1 - Boîte de transfert - Google Patents

Boîte de transfert Download PDF

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Publication number
WO2013004416A1
WO2013004416A1 PCT/EP2012/058337 EP2012058337W WO2013004416A1 WO 2013004416 A1 WO2013004416 A1 WO 2013004416A1 EP 2012058337 W EP2012058337 W EP 2012058337W WO 2013004416 A1 WO2013004416 A1 WO 2013004416A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
wälzlaufbahn
central axis
transfer case
sum shaft
Prior art date
Application number
PCT/EP2012/058337
Other languages
German (de)
English (en)
Inventor
Tom-Michel During
Ramon Jurjanz
Philip Wurzberger
Original Assignee
Schaeffler Technologies AG & Co. KG
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 Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Priority to CN201290000661.9U priority Critical patent/CN203784226U/zh
Publication of WO2013004416A1 publication Critical patent/WO2013004416A1/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
    • F16H48/00—Differential gearings
    • F16H48/36—Differential gearings characterised by intentionally generating speed difference between outputs
    • 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
    • F16H48/00—Differential gearings
    • F16H48/05—Multiple interconnected differential sets
    • 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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur 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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H48/11—Differential gearings with gears having orbital motion with orbital spur gears having intermeshing planet 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
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/40—Constructional details characterised by features of the rotating cases
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/037—Gearboxes for accommodating differential gearings
    • 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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H2048/106—Differential gearings with gears having orbital motion with orbital spur gears characterised by two sun 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
    • F16H48/00—Differential gearings
    • F16H48/36—Differential gearings characterised by intentionally generating speed difference between outputs
    • F16H2048/368—Differential gearings characterised by intentionally generating speed difference between outputs using additional orbital gears in combination with clutches or brakes
    • 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
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/40—Constructional details characterised by features of the rotating cases
    • F16H2048/405—Constructional details characterised by features of the rotating cases characterised by features of the bearing of the rotating case

Definitions

  • the invention relates to a transfer case for distributing drive torque via a differential on at least two drive shafts, comprising a sum shaft and at least one geared connection formed of gears and coupled to the sum shaft, wherein the sum shaft (4) at at least one bearing point by means of at least one rolling bearing (5 , 43) is rotatably mounted on a housing about a central axis of the transfer case, and wherein the rolling bearing at least one rotatably to the housing first Wälzlaufbahn and at least one rotationally fixed to the sum shaft and rotatable with the sum shaft about the central axis second Wälzlaufbahn and between the Wälzlaufbahnen circumferentially about the central axis Having arranged rolling elements in contact with the Wälzlaufbahnen.
  • DE 10 2008 056 622 A1 shows a transfer case for distributing torques from a sum shaft via a differential to a first drive shaft and a second drive shaft.
  • the distribution of the torques in the differential can be influenced by an auxiliary gear arrangement and controllable brakes.
  • the transfer case has a planetary gear made of two so-called control gears which are coupled to one another and can be regulated by means of brakes.
  • the sum of the differential shaft is a rotatably mounted in a housing housing-like trained ring gear, to which a ring gear is attached as a power input member.
  • a ring gear In meshing with a pinion are on the ring gear on axial and radial components of the tooth forces.
  • the ring gear is therefore formed with one of two bearings Bearing assembly stored in the housing. Each of the bearings is occupied by a tapered roller bearing.
  • the tapered roller bearings are preloaded axially against each other.
  • a cover of the housing is provided with a central opening through which a further bearing with a ball bearing is accessible. With the ball bearing a planet carrier is mounted on the sum shaft of the differential. This central opening is closed with another lid.
  • the planet carrier is basket and thus the sum of the Stirnraddifferenzials on which the helical-toothed helical gear is attached as a power input member.
  • the long planet gears of a first set and the short planet wheels of a second set are stored.
  • Each of the sets is assigned in each case a sun gear with which the planet gears of this set are in meshing engagement.
  • Each sun gear is coupled to another drive shaft, which is operatively connected, for example, to a driven vehicle wheel.
  • the sum shaft of this differential can be mounted with two tapered roller bearings on the surrounding structure.
  • tapered roller bearings have high axial and radial load capacities. However, since always two tapered roller bearings of a bearing assembly must be axially biased against each other, they have high intrinsic friction, which essentially results in losses of drive power. Therefore, as described in DE102007003675A1, tapered roller bearings are replaced by bearing combinations of radial bearings and thrust bearings, which are formed for example of two needle or roller bearings and have low intrinsic friction.
  • the object of the invention is therefore to provide a transfer case with a bearing assembly, with which the disadvantages described above can be avoided.
  • the invention provides a transfer case for distributing drive torque from a sum shaft via a differential to two drive shafts of a vehicle.
  • sum wave the connecting shaft of a transmission or a geared connection is considered, at which the largest moments, ie the sum of all incoming in the transmission or the gearbox torque applied.
  • sum waves are input power elements of a transmission or differential, such as ring gears, planetary carriers or differential baskets.
  • Connecting shafts are drive and output shafts or permanent or permanently supported to the environment fixed links.
  • connecting shafts are the elements rotating around the central axis, such as sun gears, planet carriers or ring gears.
  • a geared connection is coupled to the sum shaft.
  • the geared connection is a combination of one or more branches of meshing gears, such as bevel gears or spur gears.
  • Gear connections are simple spur gears or bevel gears with bevel gears, alternatively multi-shaft arrangements with a plurality of meshing gears - alternatively with or without clutches and brakes.
  • the sum shaft is rotatably mounted on at least one bearing point by means of at least one roller bearing about a central axis of the transfer case on a housing.
  • Rolling bearings are formed from one or more rows circumferentially adjacent rolling elements of the same or different design of Wälzlaufbahnen.
  • the rolling elements lie between two generally opposing Wälzlaufbahnen in contact on a circumferential line or on two circumferential lines per Wälzlaufbahn.
  • the rolling bearing has at least one housing for the rotation-proof first Wälzlaufbahn and at least one rotationally fixed to the sum shaft and rotating with the sum of the shaft about the central axis second Wälzlaufbahn. Between the Wälzlaufbahnen are circumferentially arranged around the central axis rolling elements in contact with the Wälzlaufbahnen.
  • the Wälzlaufbahnen are either directly on the sum shaft or on the housing but preferably formed on bearing rings.
  • Bearing rings are all solid bearing rings or non-cutting, for example, sleeve or cup-shaped rings with Wälzlaufbahnen in the form of conical or cylindrical surfaces or ball grooves.
  • the rolling elements are arranged radially outwardly circumferentially at any point of the first Wälzlaufbahn with the first Wälzlaufbahn and radially inner circumferentially at any point of the second Wälzlaufbahn with the second Wälzlaufbahn in contact.
  • the sum of the sum shaft rotationally fixed second Wälzlaufbahn is an outer on the sum shaft directly or alternatively formed on an outer bearing ring Wälzlaufbahn.
  • the housing fixedly assigned first Wälzlaufbahn is formed on the housing either directly or on an inner bearing ring Wälzlaufbahn.
  • At any point of the Wälzlaufbahn means that the contact occurs not only at the largest outer or inner circumference of Wälzlaufmaschineen, but is also formed in areas between them. The contact is punctiform or linear and may also be formed flat under load.
  • the outer ring of the rolling bearing sits in a bearing bore, for example a hub of the sum shaft and an inner ring of the rolling bearing on a journal of the housing.
  • the advantage of the invention is that for the rolling bearings of shafts of the planetary gear including the storage for the sum shaft axially little space is claimed because they can be arranged concentrically with each other.
  • the effort for their production or sealing is low.
  • the radial and axial rolling bearings are arranged radially concentrically in a region which is filled in arrangements according to the prior art of the material of the housing.
  • the housing can be closed at the bearing, which is occupied by the bearing combination, in contrast to the previously known prior art with only a lid. The effort that must be operated to seal the arrangement is reduced.
  • the pitch diameter of both the radial bearing and the thrust bearing is larger. Accordingly, more rolling elements can be housed in a row in the radial bearing and thrust bearing, whereby the bearing capacity of these bearings can be increased. This is of great importance, in particular, when high axial loads must be absorbed on the ring gear due to large axial components of the tooth forces.
  • the diameter of the rolling elements can be increased compared to those of the prior art, which also results in improved load capacities.
  • the transfer case is rotatably mounted in a housing 2 formed from at least two housing parts 2a and 2b and has a housing-like ring gear carrier 3, the sum of shaft 4 of the transfer case 1 is.
  • a gear 9 is fixed as a power input, that is designed either as a helical spur gear 9a or as a cone (plate) wheel 9b.
  • the sum shaft Due to axial components of tooth forces from the meshing of the gear 9 with a drive gear, not shown, the sum shaft is mounted radially and axially rotatable about the central axis 10 of the transfer case.
  • the sum shaft 4 is therefore rotatably supported in the housing 2 at three bearing points 4.1, 4.2 and 4.3.
  • Figure 2 shows the detail Z of Figure 1 in detail.
  • the first bearing 4.1 of the sum shaft 4 is formed by a rolling bearing 5 of the type radial roller bearings.
  • the radial rolling bearing is a floating bearing, which can absorb any axial forces, and is a radial roller bearing.
  • the radial roller bearing has a solid and hollow cylindrical inner bearing ring 5a and a sleeve-like outer bearing ring 5b and rolling elements 5c in the form of cylindrical or spherical rollers.
  • the rolling elements 5 c are arranged radially between a first rolling raceway 21 and a second rolling raceway 22.
  • the first Wälzlaufbahn 21 is fixed by means of a housing 2 fixed to the inner bearing ring 5a on the housing 2.
  • the second Wälzlaufbahn 22 is rotatable about the central axis 10 by means of the seated in a bearing seat 3a of the Hohlradebens 3 outer bearing ring 5b.
  • the sum shaft 4 is therefore rotatably supported at the bearing point 4.1 on the outer bearing ring 5b relative to the housing 2 about the central axis 10.
  • the second bearing point 4.2 of the sum shaft 4 is formed by an axial roller bearing 6.
  • the thrust roller bearing 6 is an axial bearing and can not support in radial directions. It is designed as an axial needle bearing.
  • the third bearing point 4.3 of the sum shaft 4 is a one-sided axially acting fixed bearing of the type angular contact ball bearing 7, which can absorb axial forces in one direction and forces in both radial directions.
  • the ring gear 3 carries a ring gear 1 first
  • the ring gear 1 1 is part of a geared connection with spur gears in the form of a differential 12, which is a planetary gear and which is formed from the sum shaft 4, from the ring gear 1 1 from a set of planet gears 13, a planet carrier 14 and a sun gear 15 ,
  • the planet gears 13 are rotatably mounted at a radial distance from the central axis 10 to the planet carrier 14 and are in meshing engagement with the sun gear 15 and the ring gear 1 first
  • the planetary carrier 14 is rotatably mounted about the rotation axis 10 at a first bearing 14.1 relative to the housing 2 on the housing, rotatably supported at a second bearing 14.2 on a hollow shaft 16 relative to the hollow shaft 16 and at a third bearing 14.3 axially relative to the sum shaft rotatably supported on the sum shaft 4.
  • the planet carrier 14 is connected to a connecting flange 14a of a drive shaft not shown.
  • the sun gear 15 is connected to the extension 15a with a connecting flange, not shown, of a drive shaft not shown.
  • Drive torques applied to the sum shaft 2 are distributed via the differential 12 to the drive shafts.
  • the proportions of the moments can be influenced via a control gear 25 and thus operatively connected brakes.
  • the first bearing 14.1 of Planetenträges 14 is a ball bearing 8, which sits in a bearing seat 17 of the housing 2.
  • the bearing seat 17 is sealed to the outside of the housing 2 with a radial shaft sealing ring 18 and concealed at the outlet opening 17a from the outside of the connection flange 14a.
  • the hollow cylindrical bearing seat 17 is partially formed in a pin 20.
  • the pin 20 is hollow cylindrical and receives inside the ball bearing 8 and the outside of the rolling bearing 5, so that the rolling bearing 5 and the ball bearing 8 concentric with the central axis 10 on the one-piece with the housing part 2a trained pin 20 of the housing part 2a sit.
  • the ball bearing 8 is seated with an outer bearing ring 8a in the pin 20.
  • the roller bearing 5 is seated in the interior of the housing 2 with the inner bearing ring 5a on the pin 20, so that the bearing point 4.1 does not have to be sealed.
  • the second bearing 14.2 of the planet carrier 14 has an angular contact ball bearing 23, via which the hollow shaft 16 and the planet carrier 14 are radially supported on each other and via which the hollow shaft 16 is axially supported on the planet carrier 14.
  • the third bearing 14.3 of the Planetenträges 14 is formed by an axial rolling bearing 27.
  • the thrust roller bearing 27 can not support in radial directions. It is designed as an axial needle bearing.
  • the sun gear 15 is rotatable at a bearing point 15.1 in the hollow shaft 16 radially relative to the hollow shaft
  • the hollow shaft 16 is a rotationally fixed connection between a sun gear 24a of a planetary gear 24 and a ring gear 25a of the control gear 25.
  • the planetary gear 24 is formed from the sun gear 24a, the planet carrier 14 and planet gears 24b on the planet carrier 14 and a ring gear 24c.
  • the planet gears 24b mesh with the sun gear 24a and the ring gear 24c.
  • the ring gear 24c is fixed to a planet carrier 25b of the control gear 25.
  • the planet carrier 25b is rotatably supported axially about the central axis 10 to one side at a first bearing point 25.1 axially on the ring gear 25a and at the second bearing point 25.2 to the other side axially on the sum shaft 2.
  • the bearings 25.1 and 25.2 have Axialskylzlager 28 and take on no radial forces.
  • first planetary gear 25c On the planet carrier 25b sit at a radial distance from the central axis rotatable first planetary gears 25c and second planetary gears 25d of which in each case a first planetary gear 25c with a second planetary gear 25d is in meshing engagement.
  • the first planet gears 25c are also in meshing engagement with the ring gear 25a and with a first sun gear 26a of the control gear 25.
  • the second planet gears 25d are in meshing engagement with a second sun gear 26b of the control gear 25.
  • the sun gears 26a and 26b are rotatably supported on the first bearing 26.1 to each other radially and axially relative to each other about the central axis.
  • the bearing 26.1 may be formed by a radial bearing and by a thrust bearing.
  • the first bearing 26.1 is formed by a combined axial-radial bearing 29, the axial and radial bearing components are plain bearings.
  • the Sun gear 26a is also rotatably supported at a second bearing 26.2 about the central axis 10 relative to the ring gear 25a axially and radially on the ring gear 25a.
  • the second bearing 26.2 has an angular contact ball bearing 31.
  • the sun gear 26b is radially and axially supported on the sum shaft 2 at a third bearing point 26.3.
  • the third bearing 26.3 is provided with an angular contact ball bearing 32.
  • FIG. 3 shows a transfer case 40 for distributing drive torques via a differential 40 'to at least two drive shafts, not shown, in a partial section along the central axis 35 of the transfer case 40.
  • the transfer case 40 is the differential 40'.
  • the geared connection is the planetary gear of the differential 40 'with gears, which are designed as spur gears.
  • the differential 40 ' has as a sum shaft 4 a differential basket 36 which is a 37a and 37b composed of two parts planet carrier 37.
  • Power input is a spur gear 33 which sits firmly on a flange 34 of the planet carrier 37.
  • Differential gears of the differential 40 ' are a set of long first planetary gears 38 and a set of short second planetary gears 39. In each case, a first planetary gear 38 meshes with a second planetary gear 39.
  • Output gears of the differential 40 ' are a first sun gear 41 and a second sun gear 42.
  • the short second planet gears 39 are in meshing engagement with the first sun gear 41 and the long first planetary gears 38 in mesh with the second sun gear 42.
  • the planet gears 38 and 39 are with Radial distance to the central axis 35 rotatably supported by the planet carrier 37.
  • the planet carrier 37 and the sun gears 41 and 42 are rotatable about the central axis 35.
  • the sun gears are connected via the designed as a hollow shaft extensions 41 a and 42 a with the drive shafts, not shown.
  • the sum shaft 4 is rotatably supported at two bearing points 4.1 and 4.2 respectively by means of a rolling bearing 43 about the central axis 35 on a housing 44.
  • the rolling bearing 43 is formed of an inner race 43a, an outer race 43b, and rolling elements 43c in the form of balls.
  • the rolling elements 43c are arranged radially between a rotationally fixed to the housing 44 first Wälzlaufbahn 45 and a rotation to the sum of shaft 4 and with the sum shaft 4 about the central axis 35 rotating second Wälzlaufbahn 46.
  • the Wälzlaufbahnen 45 and 46 are ball grooves with which the rolling elements 43c are in contact.
  • the rolling elements 43c are radially outwardly circumferentially of the first Wälzlaufbahn 45 with the first Wälzlaufbahn 45 and radially inwardly circumferentially the second Wälzlaufbahn 46 with the second Wälzlaufbahn 46 in contact.
  • the outer bearing ring 43b has the second Wälzlaufbahn 46 and is firmly seated in a bearing seat 37c of the planet carrier 37.
  • the inner bearing ring 43a has the first Wälzlaufbahn 45 and is firmly seated on a pin 44a of the housing 44th Accordingly, the sum wave 4th via the outer bearing ring 43b, the rolling elements 43c and the inner bearing ring 43a radially mounted on the pin 44a, wherein the outer bearing ring 43b is rotatable with the planet carrier 37 about the central axis 35.

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

Abstract

L'invention concerne une boîte de transfert (1,40) servant à répartir des couples d'entraînement sur au moins deux arbres primaires par l'intermédiaire d'un différentiel (12, 40'), comprenant un arbre totalisateur (4) et au moins une liaison de transmission composée de roues dentées et couplée à l'arbre totalisateur (4). L'arbre totalisateur (4) est logé en au moins un point d'appui (4.1) dans un carter (2, 44), rotatif autour d'un axe central (10) de la boîte de transfert (1,40) au moyen d'au moins un palier à roulements (5, 43). Le palier à roulements (5, 43) comprend au moins un premier chemin de roulement (21, 45) solidaire en rotation avec le carter (2, 44) et au moins un deuxième chemin de roulement (22, 46) rotatif, solidaire en rotation avec l'arbre totalisateur (4) et tournant avec ledit arbre totalisateur (4) autour de l'axe central (10), ainsi que des corps roulants (5c, 43c) en contact avec les chemins de roulement (21, 22, 45, 46) et disposés à la périphérie de l'axe central (10) entre les chemins de roulement (21, 22, 45, 46).
PCT/EP2012/058337 2011-07-07 2012-05-07 Boîte de transfert WO2013004416A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201290000661.9U CN203784226U (zh) 2011-07-07 2012-05-07 分动器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110078774 DE102011078774A1 (de) 2011-07-07 2011-07-07 Verteilergetriebe
DE102011078774.7 2011-07-07

Publications (1)

Publication Number Publication Date
WO2013004416A1 true WO2013004416A1 (fr) 2013-01-10

Family

ID=46124312

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2012/058337 WO2013004416A1 (fr) 2011-07-07 2012-05-07 Boîte de transfert

Country Status (3)

Country Link
CN (1) CN203784226U (fr)
DE (1) DE102011078774A1 (fr)
WO (1) WO2013004416A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114483779A (zh) * 2022-01-28 2022-05-13 中国铁建重工集团股份有限公司 一种盾机刀盘驱动回转机构

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013204930B3 (de) * 2013-03-20 2014-07-10 Schaeffler Technologies Gmbh & Co. Kg Getriebeanordnung mit einer Armierungsbuchse sowie Verfahren zur Montage der Getriebeanordnung
DE102013216798B3 (de) * 2013-08-23 2014-12-31 Schaeffler Technologies Gmbh & Co. Kg Antriebsvorrichtung mit einer elektrischen Antriebsmaschine, mit einer Schaltkupplung und mit einem Getriebe
DE102017204167A1 (de) * 2017-03-14 2018-09-20 Zf Friedrichshafen Ag Lagerung einer Welle

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US792690A (en) * 1903-05-27 1905-06-20 Baker Motor Vehicle Co Bevel-gear driving and compensating mechanism.
US2142575A (en) * 1936-09-29 1939-01-03 Gen Motors Corp Differential gearing
EP0614778A1 (fr) * 1993-03-09 1994-09-14 Regie Nationale Des Usines Renault S.A. Différentiel de transmission pour boîte de vitesses étanche
DE19954590A1 (de) * 1999-11-12 2001-05-17 Linde Ag Antriebsanordnung mit einem Elektromotor
DE102007003675A1 (de) 2007-01-25 2008-07-31 Schaeffler Kg Stirnraddifferenzial mit einem Planetentrieb
DE102007040475A1 (de) 2007-08-28 2009-03-05 Schaeffler Kg Stirnraddifferential
DE102008056622A1 (de) 2008-11-10 2010-05-12 Volkswagen Ag Aktive Differentialanordnung für ein Kraftfahrzeug

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US792690A (en) * 1903-05-27 1905-06-20 Baker Motor Vehicle Co Bevel-gear driving and compensating mechanism.
US2142575A (en) * 1936-09-29 1939-01-03 Gen Motors Corp Differential gearing
EP0614778A1 (fr) * 1993-03-09 1994-09-14 Regie Nationale Des Usines Renault S.A. Différentiel de transmission pour boîte de vitesses étanche
DE19954590A1 (de) * 1999-11-12 2001-05-17 Linde Ag Antriebsanordnung mit einem Elektromotor
DE102007003675A1 (de) 2007-01-25 2008-07-31 Schaeffler Kg Stirnraddifferenzial mit einem Planetentrieb
DE102007040475A1 (de) 2007-08-28 2009-03-05 Schaeffler Kg Stirnraddifferential
DE102008056622A1 (de) 2008-11-10 2010-05-12 Volkswagen Ag Aktive Differentialanordnung für ein Kraftfahrzeug

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114483779A (zh) * 2022-01-28 2022-05-13 中国铁建重工集团股份有限公司 一种盾机刀盘驱动回转机构

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Publication number Publication date
DE102011078774A1 (de) 2013-01-10
CN203784226U (zh) 2014-08-20

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