WO2012034727A1 - Unité d'entraînement comprenant au moins un entraînement et au moins un différentiel planétaire - Google Patents

Unité d'entraînement comprenant au moins un entraînement et au moins un différentiel planétaire Download PDF

Info

Publication number
WO2012034727A1
WO2012034727A1 PCT/EP2011/061211 EP2011061211W WO2012034727A1 WO 2012034727 A1 WO2012034727 A1 WO 2012034727A1 EP 2011061211 W EP2011061211 W EP 2011061211W WO 2012034727 A1 WO2012034727 A1 WO 2012034727A1
Authority
WO
WIPO (PCT)
Prior art keywords
planetary
gears
drive
rotation
sun gear
Prior art date
Application number
PCT/EP2011/061211
Other languages
German (de)
English (en)
Inventor
Thorsten Biermann
Tomas Smetana
Original Assignee
Schaeffler Technologies Gmbh & 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 Gmbh & Co. Kg filed Critical Schaeffler Technologies Gmbh & Co. Kg
Publication of WO2012034727A1 publication Critical patent/WO2012034727A1/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
    • 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
    • F16H37/0806—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 a plurality of driving or driven shafts
    • F16H37/0813—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 a plurality of driving or driven shafts with only one input shaft
    • F16H37/082—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 a plurality of driving or driven shafts with only one input shaft and additional planetary reduction gears
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L2220/00—Electrical machine types; Structures or applications thereof
    • B60L2220/40—Electrical machine applications
    • B60L2220/42—Electrical machine applications with use of more than one motor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L2240/00—Control parameters of input or output; Target parameters
    • B60L2240/40—Drive Train control parameters
    • B60L2240/42—Drive Train control parameters related to electric machines
    • B60L2240/423—Torque
    • 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
    • F16H2048/364—Differential gearings characterised by intentionally generating speed difference between outputs using electric or hydraulic motors
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/64—Electric machine technologies in electromobility

Definitions

  • Drive unit with at least one drive and with at least
  • the invention relates to a drive unit having at least one drive, and having at least one planetary differential, which is operatively connected to the drive via at least one planetary gear and which at least a first set of Ausretesplanetenzier that mesh with a first sun gear, and a second set of compensating planetary gears, which are in meshing engagement with a second sun gear and at the same time each with one of the compensating planetary gears of the first set, wherein the axes of rotation of the first and second sun gears are concentric together on a main axis of the drive unit and the planetary drive has at least a third set of planet gears; which is coupled to the planetary differential.
  • the drive unit has a main drive and a power take-off.
  • the main drive is geared via a planetary gear set with a planetary differential.
  • a planetary differential is characterized essentially by two sets of differential gears, each formed by a set of planetary gears.
  • Each of the Ausretesplanetenrate is rotatably mounted about a rotation axis on a planet shaft, which corresponds to the axis of symmetry of the planetary pin.
  • the axes of rotation of the planet gears are aligned parallel to the axis of rotation of the driven wheels, ie to the axes of rotation of the sun gears of the differential.
  • the coaxial rotation axes of the solar Wheels are concentric to the differential and lie on the main axis of the drive unit.
  • the main axis of the drive unit also combines the rotational axes of the drive shafts of the main and auxiliary drive in itself.
  • the differential shafts of the planetary differential are sun gears each connected to, for example, an output shaft leading to a vehicle wheel. Each of the sun gears is in meshing engagement with one of the sets of differential gears.
  • Main drive and PTO are electric motors in this case, which are arranged coaxially with each other.
  • the superposition gear is formed by three coupled planetary gears.
  • Such drive units are independent of other drive sources, e.g. independent of internal combustion engines, or used together with them.
  • the object of the invention is to provide a drive unit which is compact, whose components have a long service life and which nevertheless can be produced cost-effectively.
  • Each individual axis of rotation of the differential planetary gears of the first set of differential is each spaced at a radial center distance greater than or less than the axis spacing of the respective axis of rotation of each differential planetary gear of the second set in the same differential.
  • the first axis of rotation and the second axis of rotation are each performed parallel to the main axis of the drive unit.
  • the center distance of the rotary axes within a block is the same.
  • the geared between the first drive (main drive) and the differential planetary gear has at least a third set planetary gears, whose respective axis of rotation is also arranged parallel to the main axis.
  • the center distance of the axes of rotation of the planetary gears with each other is the same within the third set.
  • this center distance is just as large as the center distances of the axes of rotation of a set of Ausretetengan in the planetary differential.
  • the distances of the rotational axes of the planetary gears of the planetary gear to the main axis, which is connected between the main drive and the planetary differential are equal to the distances of the axes of rotation of one of the sets Ausretetenrad, either the first or the second set, to the main axis.
  • the center distances of the rotational axes of the planetary gears of the planetary drive to the main axis are at the same time either greater or smaller than the center distances of the axes of rotation of the compensating planetary gears within the other set to the main axis.
  • An embodiment of the invention preferably provides that the axial distance of the axes of rotation of the planetary gears of the planetary drive to the main axis corresponds to the center distance of the axes of rotation of the set of Ausretetenrate to the main axis, which are further away from the main axis.
  • the axial distance of the axes of rotation of the planet gears to the main axis is greater than the axial distance of the axes of rotation of Aus istsplane- tengan a set in the planetary differential to the main axis.
  • the teeth of the first set of compensating planet gears mesh with the teeth of the second set of compensating planetary gears.
  • the number of teeth of the Aus somnsplaneten- wheels of the first set preferably corresponds to the number of teeth of the teeth of the compensating planet gears of the second set, but may also be different.
  • the toothing of the compensating planet wheels of one of the sets meshing with the toothing is only one sun gear, without the teeth of the compensating planet wheels of this set is in mesh with the teeth of the other sun gear.
  • the Aus stressessplanetenrise this one set must be "longer", ie axially wider than the teeth of the Ausreteplaneten elevate the other set and the other sun gear axially overlap without touching it.
  • the axially overlapped sun gear a smaller number of teeth, so a smaller diameter, have than the adjacent sun gear.
  • the toothing of the axially overlapped sun gear has the same number of teeth as the other, but is designed with a smaller tip circle. The same number of teeth and the same diameter of the Ausreteplanetenz both sets are mutually assumed in this case.
  • the different tip diameter of the sun gears can be achieved by the profile shift known in the art.
  • the tooth contact of the sun gears with the larger tip circle is achieved by positive profile shift and corresponding to the tooth contact of the smaller circle in the top circle sun wheels by negative professional shift.
  • the head circle is an imaginary circle that surrounds the teeth of a toothing with equal teeth outside.
  • the tip diameter is accordingly the outside diameter of such a face gear. It determines from the axis of rotation or axis of rotation of the space required by a gear in all radial directions.
  • the center distance of the overlapped sun gear to the counterbalancing planetary gear meshing therewith is smaller so that the short gears can mesh with it.
  • the matching gear ratios between the first planetary gear balancing wheels and the first sun gear and between the second planetary gear balancing wheels and the second Sun gear are required in this case.
  • the first sun gear preferably has the larger and the second sun gear on the smaller tip circle.
  • the axial distance between the first sun gear and the axes of rotation of the long compensation planetary gears of the first set is greater than the axial distance of the axis of rotation of the second sun gear to the respective axis of rotation of the second set with the short compensation planetary gears.
  • the balancing planetary gears of the first set are the long balancing planetary gears that axially overlap the second sun gear.
  • the second sun gear meshes only with the shorter counterbalance planetary gears.
  • This arrangement can also be reversed, so that the center distance between the axes of rotation of the second set of Ausretetenrate and the axis of rotation of the respective second sun gear is greater than the axial distance between the axis of rotation of the first sun gear and the axes of rotation of the compensating planetary gears of the first set.
  • the compensating planet wheels of the second set are the long and the first set of short balancing wheels.
  • the invention provides with an embodiment that the center distance of the axes of rotation of the planetary gears in the planetary drive to the main axis first either with the longer center distance between the axis of rotation of the larger sun gear in the tip circle and the axis of rotation of the long Aus somnsplanetengan or secondly with the shorter center distance between the axis of rotation the other in the top circle smaller sun gear and the axes of rotation of the short Ausretetenrädem is the same.
  • the respective forces transmitting proportion of the toothings of all gears of the planetary drive and the differential must be designed comparatively axially wider.
  • the drive unit In the case where the center distances in the planetary gear is equal to the smaller center distances between the smaller sun and the short planetary gear, the drive unit, the same torques as in a. provided, designed axially narrow and the space to be expanded radially.
  • the combination a. can be selected if there is little radial space available for the design of the drive unit but axially sufficient space available.
  • the combination b. is preferably used when axially little space but radially larger space is available.
  • An embodiment of the invention provides that with the planetary differential driven by a PTO superposition gearbox is coupled by gearing.
  • the planet gears of the second set must be the short planetary gears.
  • the additional drive power can, for example, via an operatively connected to the superposition gear second drive shaft of another drive, the auxiliary drive; be introduced into the superposition gear, wherein the axis of rotation of the drive shaft is preferably concentric with the main axis.
  • the superposition gearing comprises at least a fourth set of planetary gears, in which the axes of rotation of the planet gears parallel to the main axis are just as far away from the main axis as the axes of rotation of the planet gears of the third set.
  • Another advantage of the invention is that the housing of the planet carrier and the differential can be made in one piece.
  • the planet carrier of the planets of the planetary differential is at the same time a planet carrier of the planetary drive arranged between the main drive and the planetary differential. It is also possible to extend the planetary pin and at the same time to store the differential gears and the planets on the same shaft. Furthermore, under certain circumstances the same or at least similar planet carriers can be installed, so that overall the number of individual parts required for the production of the drive unit is low.
  • the drive unit 1 shows a drive unit 1 in a longitudinal section along the main axis 9.
  • the drive unit 1 is an independent compact unit in which a main drive 2, a transmission 3, which consists of a planetary differential 4 and a superposition gear 5, a Secondary drive 6, a first output shaft 7 and a second output shaft 8 with respect to their main axes 9 (axes of rotation of the rotors and axes of symmetry of the sun gears) in a common housing 10 coaxial or concentric with each other.
  • the drives 2 and 6 are electric motors.
  • the housing 10 is formed in three parts.
  • a middle housing part 101 receives the gear 3 and is open to the left and right to the drives 2 and 6 out.
  • a left housing part 102 receives the gear 3 and is open to the left and right to the drives 2 and 6 out.
  • a right housing part 103 sit a power take-off 6 and a further sensor 12.
  • the right housing part 103 is left closed to the transmission 3 with an intermediate wall, which is a concentric to the main axis 9 implementation 108 has.
  • the output shaft 7 and the output shaft 8 are inserted concentrically to the main axis 9 centrally in the passages 105 to 109.
  • FIG. 2 shows the longitudinal section through the drive unit according to FIG. 2.
  • a first rotor shaft 20 of the main drive 2 is connected in a rotationally fixed manner to a third sun gear 40 about the rotor axis 9 or main axis 9.
  • the main drive 2 is coupled via the rotor shaft 20 with the third sun gear 40 transmission technology.
  • the rotor shaft 20 and the third sun gear 40 are rotatably supported by means of the ball bearing 21 and the ball bearing 22.
  • the ball bearings 21 and 22 are against each other employed angular contact ball bearings and sitting in the left housing part 102.
  • Differential shafts of the planetary differential 4 are a first sun gear 41 and a second sun gear 42nd
  • the first sun gear 41 is non-rotatably mounted on the first output shaft 7 about the main axis 9.
  • the first rotor shaft 20 is a hollow shaft in which the first output shaft 7 is rotatably supported by means of a needle bearing 23 and by means of a needle bearing 24.
  • the shaft 401 of the third sun gear 40 extends axially partially into the rotor shaft 20 as far as the needle bearing 24.
  • the second sun gear 42 is rotatably mounted on the second output shaft 8 about the main axis 9.
  • the second output shaft 8 is rotatably supported about the main axis 9 by means of a needle bearing 63 and a needle bearing 64 in a rotor shaft 60 of the auxiliary drive 6 designed as a hollow shaft.
  • the rotor shaft 60 is rotatably supported in the passages 108 and 109 in the right-hand housing part 103 by means of a ball bearing 61 and a ball bearing 62.
  • the ball bearings 61 and 62 are against each other employed Schrägkuge Ilager.
  • the rotor shaft 60 projects out of the auxiliary drive 6 axially concentrically with the main axis 9 into the superposition gearing 5.
  • a sun gear 50 is rotationally fixed on the rotor shaft 60 about the main shaft 9.
  • the auxiliary drive 6 is coupled via the sun gear 50 to the transmission 3 in terms of transmission technology.
  • the superposition gearing 5 and the planetary differential 4 are coupled via a ring gear 51 of the superposition gearing 5 and planet gears 43.
  • FIG. 2 shows the planetary differential 4 of the drive unit 1 integrated into the drive unit 1 in a detail from FIG. 1.
  • the planetary differential 4 has two planetary gear sets and a lubricating device 13.
  • a planetary drive which is connected between the main drive 2 and the actual planetary differential 4, has planet gears 44 which mesh with the sun gear 40 and a ring gear 45.
  • the ring gear 45 is stationary held the middle housing part 101.
  • the planet gears 44 are each rotatably supported by planet bearings 441 on planet pins 442.
  • the planet pins 442 are each fixed to a planet carrier 46.
  • the planet carrier 46 of the planetary differential 4 is formed of four carrier segments 461, 462, 463 and 464 and rotatable about the main axis 9.
  • the carrier segments 461, 462, 463 and 464 are rotatably connected to the planet carrier 46 and held together or in cooperation with the planet pins 481 and 442, the elements of the planetary differential 4 and other elements together.
  • the planet pins 442 are respectively held at three bearings 443, 444 and 445 in the first planet carrier 46, each of which is formed on one of the support segments 461, 462 and 463.
  • a first planetary gearset of the planetary differential 4 has long third counterbalancing planetary gears 47 meshing with the first sun gear 41 and with counterbalance gears 48 of a second planetary gearset.
  • the Ausretesplanetenrate 47 are rotatably supported between the support segments 463 and 464 as well as the planetary gears 44 on the planetary pin 442 about the rotation axis 490.
  • the second planetary gear set is formed by the balancing planet gears 48 meshing with the balancing planetary gears 47 and the second sun gear 42 and supported on a planetary pin 481.
  • the planetary pin 481 is supported at two bearings 482 and 483 of the carrier segments 462 and 464.
  • FIG. 3 shows the superposition gearing 5 integrated into the drive unit as a section of the illustration according to FIG. 1.
  • the superposition gearing 5 has a housing 53 with a ring gear 531.
  • the ring gear 51 of the planetary differential 4 is also integrated into the housing 53.
  • the ring gears 51 and 531 are fixed to the housing held in the housing 53.
  • the housing can also be formed integrally with the ring gears by the teeth of the ring gears are introduced into the housing.
  • the housing 53 is rotatably mounted with a ball bearing 25 radially on a fixed to the right housing part 103 sun gear 532.
  • a planet carrier 54 is centered on a shaft 533 of the housing 53 to the main axis 9.
  • the planet carrier 54 is formed from two carrier segments 541 and 542.
  • Planet pins 56 are received on both sides and on each side in one of the carrier segments 541 and 542.
  • planetary gears 57 and planetary gears 58 are mounted in pairs by planetary bearings 571 and 581 about the axis of rotation 590 in pairs.
  • a concentric in the housing 53 seated ring gear 55 is centered on the sun gear 52 which is rotatably mounted on a shaft 421 of the second sun gear 42, and is rotatably screwed with this.
  • the sun gear 52 is in the mounted drive unit in meshing engagement with the planetary gears 43.
  • the planetary gears 43 are in meshing engagement with the ring gear 51.
  • the planetary gears 57 mesh with the sun gear 50 and with the ring gear 55.
  • the planet gears 58 mesh with the sun gear 532 and mesh with the ring gear 531.
  • the sun gear 532 is bolted to an intermediate wall.
  • FIG. 4 shows schematically and not to scale the structure of the drive unit 1.
  • the rotor 201 of the main drive 2 is connected to the sun gear 40 via the rotor shaft 20.
  • Rotor 201, rotor shaft 20 and sun gear 40 are rotatable relative to the housing 10 about the main axis 9.
  • the sun gear 40 meshes with planet gears 44.
  • the planet gears 44 mesh with the ring gear 45 and are rotatably supported about the pin axis 446 on a respective planetary pin 442.
  • the ring gear 51 is fixed to the housing 0.
  • the planet pins 442 are fixed parallel to the main axis 9 and with the radius A to the main axis 9 on the planet carrier 46.
  • the planet carrier 46 is rotatably mounted about the main axis 9 relative to the housing 10.
  • each planetary pin 442 except a planetary gear 44 is a Ausretesplanetenrad 47 each having the radius A to the main axis about the rotation axis 490 and rotatably mounted relative to the planetary gears 44.
  • Each of these so-called long Ausretesplanetenrate 47 extends in the axial direction via the first sun gear 41 and the second sun gear 42, each Ausretesplanetenrad 47 is respectively meshed with the first sun gear 41 and one of the Ausretetenrate 48.
  • the Austiciansplanetenrate 47 are arranged contactless.
  • Ausretetenraten 48 each rotatable about the rotational axis 485 rotatably connected to a planetary gear 43 and rotatably mounted together with this on each of a planetary pin 481.
  • the planetary pin 481 are fixed as well as the planetary pin 442 with its axis of rotation 485 with the radius A1 to the main axis 9 on the planet carrier 46.
  • the Ausretetenrate 48 are in meshing engagement with the second sun gear 42.
  • the Ausretetenrate 43 are each in meshing engagement with the ring gear 51 and the sun gear 52.
  • A1 is smaller than A.
  • the ring gear 51 is rotatably held on the housing 53.
  • the housing 53 is rotatably mounted on the sun gear 532 relative to the housing 10 and relative to the sun gear 532.
  • the sun gear 532 is fixed to the housing 10.
  • the sun gear 52 is fixedly connected to the ring gear 55 and rotatably supported with the ring gear 55 relative to the housing 10.
  • the ring gear 55 is in meshing engagement with the planet gears 57.
  • the planet gears 57 are rotatably mounted about the pin axis 561 rotatably mounted on the planet pins 56.
  • the planet pins 56 are, like the planet pins with its pin axis 446 and the n planet pins 481 spaced with its axis of rotation 485 with the radius A of its pin axis 561 to the main axis 9.
  • the planet pins 56 are fixed on both sides of the planet carrier 54.
  • the planetary carrier 54 is rotatably mounted relative to the housing 53 rotatably mounted on the fixed housing 10 to the sun gear 532.
  • the planetary gears 57 are in meshing engagement with the sun gear 50, which rotatably connected to the rotor shaft 60 of the servo motor 6 and is relatively rotatable to the housing 10.
  • the planetary gears 58 are mounted rotatably about the axis of rotation 485 and thereby relative to the planetary gears 57 on the planet pins 56.
  • the planet gears 58 mesh with the sun gear 532 and mesh with the ring gear 531.
  • the sun gear is bolted to an intermediate wall and thus supported on the housing 10.
  • the third ring gear 531 is like the first ring gear 51 fixed to the housing 53 and rotatable relative to the housing 0 with this.
  • the first sun gear 41 is rotatably supported relative to the third sun gear 40 about the main axis 9 in the hollow rotor shaft 20 and rotatably connected to the first output shaft 7.
  • the second sun gear 42 is rotatably mounted relative to the third sun gear 40 and the rotor shaft 60 of the rotor 601 in the form of a hollow shaft rotor shaft 60 and rotatably connected to the second output shaft 8.

Abstract

L'invention concerne une unité d'entraînement (1) comprenant au moins un entraînement (2, 6) et au moins un différentiel planétaire (4), qui est relié activement à l'entraînement (2, 6) par l'intermédiaire d'au moins un train planétaire et qui possède au moins un premier jeu de pignons satellites de différentiel (47) qui sont en prise avec une première roue planétaire (41), ainsi qu'un deuxième jeu de pignons satellites de différentiel (48) qui sont en prise avec une deuxième roue planétaire (42) et en même temps chacun avec l'un des pignons satellites de différentiel (47) du premier jeu, les axes de rotation des première et seconde roues planétaires (41, 42) se trouvant ensemble concentriquement sur un axe principal (9) de l'unité d'entraînement (1), et le train planétaire présentant au moins un troisième jeu de pignons satellites (44), qui est accouplé au différentiel planétaire, cependant que les axes de rotation (490) parallèles à l'axe principal (9) de chacun des pignons satellites de différentiel (47) du premier jeu présentent un entre-axes radial avec l'axe principal (9) qui est différent de celui des axes de rotation (485) de chacun des pignons satellites de différentiel (48) du deuxième jeu, de même que les axes de rotation (490) des pignons satellites (44) du troisième jeu qui sont parallèles à l'axe principal (9) présentent un entre-axes radial (A) avec l'axe principal (9), qui correspond à l'un des entre-axes (A, A1) des axes de rotation (485, 490) du premier jeu ou du deuxième jeu.
PCT/EP2011/061211 2010-09-17 2011-07-04 Unité d'entraînement comprenant au moins un entraînement et au moins un différentiel planétaire WO2012034727A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010045876.7 2010-09-17
DE102010045876A DE102010045876A1 (de) 2010-09-17 2010-09-17 Antriebseinheit mit wenigstens einem Antrieb und mit mindestens einem Planetendifferenzial

Publications (1)

Publication Number Publication Date
WO2012034727A1 true WO2012034727A1 (fr) 2012-03-22

Family

ID=44508458

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/061211 WO2012034727A1 (fr) 2010-09-17 2011-07-04 Unité d'entraînement comprenant au moins un entraînement et au moins un différentiel planétaire

Country Status (2)

Country Link
DE (1) DE102010045876A1 (fr)
WO (1) WO2012034727A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015223131A1 (de) 2015-11-24 2017-05-24 Schaeffler Technologies AG & Co. KG Antriebseinrichtung für ein Kraftfahrzeug
DE102015223130B4 (de) * 2015-11-24 2020-02-06 Schaeffler Technologies AG & Co. KG Antriebseinrichtung mit einem Differentialgetriebe und einer Torque-Vectoring-Einheit

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006028790A1 (de) * 2006-06-23 2008-01-03 Zf Friedrichshafen Ag Einrichtung zum Verteilen eines Antriebsmonentes auf wenigstens zwei Abtriebswellen einer Fahrzeugachse bzw. eines Achsgetriebes
DE102008061946A1 (de) 2008-12-12 2010-06-17 Schaeffler Kg Elektrische Antriebseinheit mit variabler Momentenverteilung
DE102009032286A1 (de) * 2008-12-18 2010-06-24 Schaeffler Kg Stirnraddifferenzial
WO2011064041A1 (fr) * 2009-11-30 2011-06-03 Schaeffler Technologies Gmbh & Co. Kg Système d'entraînement pour un véhicule automobile
WO2011076542A1 (fr) * 2009-12-21 2011-06-30 Schaeffler Technologies Gmbh & Co. Kg Système de répartition variable du couple

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006028790A1 (de) * 2006-06-23 2008-01-03 Zf Friedrichshafen Ag Einrichtung zum Verteilen eines Antriebsmonentes auf wenigstens zwei Abtriebswellen einer Fahrzeugachse bzw. eines Achsgetriebes
DE102008061946A1 (de) 2008-12-12 2010-06-17 Schaeffler Kg Elektrische Antriebseinheit mit variabler Momentenverteilung
DE102009032286A1 (de) * 2008-12-18 2010-06-24 Schaeffler Kg Stirnraddifferenzial
WO2011064041A1 (fr) * 2009-11-30 2011-06-03 Schaeffler Technologies Gmbh & Co. Kg Système d'entraînement pour un véhicule automobile
WO2011076542A1 (fr) * 2009-12-21 2011-06-30 Schaeffler Technologies Gmbh & Co. Kg Système de répartition variable du couple

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
THORSTEN BIERMANN ET AL: "Schaeffler Leichtbaudifferenziale. Eine Differenzialfamilie mit reduziertem Bauraum und Gewicht", INTERNET CITATION, 6 April 2010 (2010-04-06), pages 94 - 105, XP007913986, Retrieved from the Internet <URL:http://www.schaeffler.com/remotemedien/media/_shared_media/library/do wnloads/Schaeffler_Kolloquium_2010_06_de.pdf> [retrieved on 20100715] *

Also Published As

Publication number Publication date
DE102010045876A1 (de) 2012-03-22

Similar Documents

Publication Publication Date Title
EP1279867B1 (fr) Transmission à division de puissance
DE102012024863B4 (de) Serie von Drehzahlminderern der exzentrisch umlaufenden Bauart
DE102011102749B4 (de) Getriebeanordnung für ein Kraftfahrzeug
WO2012028372A1 (fr) Unité d&#39;entraînement
WO2012052201A1 (fr) Dispositif d&#39;entraînement
DE102005018956A1 (de) Vorrichtung zur Nockenwellenverstellung einer Brennkraftmaschine
DE202012009415U1 (de) Industriegetriebe
DE102018101408B3 (de) Antriebsvorrichtung mit einer elektrischen Maschine und einem Hohlradtopf
DE102012015051A1 (de) Planetengetriebe
DE102010041474B4 (de) Leistungsverzweigungsgetriebe
DE10054798B4 (de) Elektrisch angetriebene Vorrichtung zur Drehwinkelverstellung einer Welle gegenüber ihrem Antrieb
DE102015223914B4 (de) Umlaufrädergetriebe mit Untersetzungsstufe für eine Kraftfahrzeugantriebseinheit
DE102006046581A1 (de) Mehrstufiges Untersetzungsgetriebe
EP2397304A1 (fr) Appareil d&#39;entraînement pour une extrudeuse à double vis à vis tournant dans le même sens
DE4325403A1 (de) Verspannungsprüfstand
WO2012034727A1 (fr) Unité d&#39;entraînement comprenant au moins un entraînement et au moins un différentiel planétaire
DE102017216159B4 (de) Hybridgetriebe mit zwei erweiterten Funktionalitäten für ein Kraftfahrzeug sowie entsprechendes Kraftfahrzeug
DE102012204281A1 (de) Antriebsvorrichtung mit einem Verteilergetriebe und mit einer Torque – Vectoring – Einheit
DE102012217102A1 (de) Getriebeanordnung
DE102011088888A1 (de) Verteilergetriebe
DE102012204285B4 (de) Getriebevorrichtung mit einem Verteilergetriebe und einer Torque – Vectoring – Einheit und Antriebsvorrichtung mit einer derartigen Getriebevorrichtung
EP2761204B1 (fr) Entraînement avec mécanisme de transmission
DE102008001491A1 (de) Taumelradgetriebe mit Stirnverzahnung
AT505628B1 (de) Getriebe zur umkehrspielfreien kraftübertragung
DE3600494C2 (fr)

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 11728877

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 11728877

Country of ref document: EP

Kind code of ref document: A1