WO2021023338A1 - Agencement de transmission compact doté d'un train planétaire étagé et d'un différentiel à engrenage droit - Google Patents

Agencement de transmission compact doté d'un train planétaire étagé et d'un différentiel à engrenage droit Download PDF

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Publication number
WO2021023338A1
WO2021023338A1 PCT/DE2020/100616 DE2020100616W WO2021023338A1 WO 2021023338 A1 WO2021023338 A1 WO 2021023338A1 DE 2020100616 W DE2020100616 W DE 2020100616W WO 2021023338 A1 WO2021023338 A1 WO 2021023338A1
Authority
WO
WIPO (PCT)
Prior art keywords
differential
gear
spur
gears
planetary
Prior art date
Application number
PCT/DE2020/100616
Other languages
German (de)
English (en)
Inventor
Florian Reinle
Jochen Loeffelmann
Bastian Rupp
Sebastian Langhans
Jörg BAUER
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 CN202080055478.8A priority Critical patent/CN114207321B/zh
Publication of WO2021023338A1 publication Critical patent/WO2021023338A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0806—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
    • 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
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/0427—Guidance of lubricant on rotary parts, e.g. using baffles for collecting lubricant by centrifugal force
    • 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
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0469—Bearings or seals
    • F16H57/0471—Bearing
    • 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
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0479—Gears or bearings on planet carriers
    • 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
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0482—Gearings with gears having orbital motion
    • F16H57/0483—Axle or inter-axle differentials
    • 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
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0482—Gearings with gears having orbital motion
    • F16H57/0486—Gearings with gears having orbital motion with fixed gear ratio
    • 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
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B60K2001/001—Arrangement or mounting of electrical propulsion units one motor mounted on a propulsion axle for rotating right and left wheels of this axle
    • 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
    • F16H2048/104—Differential gearings with gears having orbital motion with orbital spur gears characterised by two ring 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
    • 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
    • F16H48/38—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
    • 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
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H2057/085—Bearings for orbital gears

Definitions

  • Transmission arrangement for a motor vehicle comprising a stepped planetary set and a spur gear differential connected via a common planet carrier, according to the features of the preamble of claim 1.
  • DE 102015214031 A1 shows a transmission arrangement for a motor vehicle, which comprises a transmission input stage and a differential connected to it via a common planet carrier.
  • the differential constructed as a spur gear differential, has two planetary sets, the planetary gears of which are toothed with separate sun gears. Furthermore, the two planetary sets of the differential are toothed with each other in pairs.
  • the transmission input stage has a drive sun that meshes with a first planetary gear set that is connected to the second planetary gear set in a rotationally fixed manner.
  • a transmission arrangement assigned to an electric drive unit comprising a rotor shaft as input shaft and a differential gear and a stepped planetary set designed as a planetary gear, also called gear input stage, whose sun gear is assigned to the input shaft.
  • the differential gear designed as a spur gear differential, includes planet gears as differential gears and sun gears as output gears, with an output shaft being assigned to each sun gear.
  • a torque introduced via the input shaft is introduced into the spur gear differential via the stepped planetary set and from there it is transferred to the output shafts and then to the driven vehicle wheels.
  • the input shaft forms a hollow shaft through which one of the output shafts is guided.
  • the invention is based on the object of creating a gear arrangement for a drive device which is compact at least in the axial direction and which can be easily installed and implemented at low cost. This object is achieved by a gear arrangement with the features of claim 1. Preferred and / or advantageous embodiments of the invention emerge from the subclaims, the following description and the accompanying figures.
  • planetary gear bolts of the stepped planetary set are arranged by a toothing plane of the spur gear at a radial distance from the sun gears and the pinion bolts continue to fix a differential cover radially and axially fi at the end facing away from the stepped planets.
  • To support the planet carrier it is provided that it is supported on the drive side of the gear arrangement via the running teeth of the large planet gears as a floating bearing and mutually by means of the differential cover via a fixed bearing in the housing of the gear arrangement.
  • an axially compact spur gear differential can advantageously be implemented, which at the same time has a positive effect on the space required for the entire transmission arrangement. Because of the spur gear differential that is expanded in the radial direction, a radial overlap occurs at least between the stepped planetary sets and a toothing plane of the spur gear differential. To implement this solution, the planetary gear bolt is axially extended from the stepped planetary set to such an extent that it enables the differential cover to be guided and fixed.
  • the compact concept according to the invention advantageously leads to a desired smaller deformation of the planet carrier, which has a positive effect on the torsional rigidity of the gear arrangement.
  • the bearing of the planet carrier constructed according to the invention comprises a floating bearing on the drive side which results from the meshing engagement of the large double planets with the input sun.
  • the differential cover which is non-rotatably connected to the planet carrier, is preferably mounted in the gear housing of the gear arrangement via a fixed bearing designed as a deep groove ball bearing.
  • a sun gear of the spur gear differential is placed close to the planet carrier.
  • a recess is made locally in the guide support structure of the planet carrier near the pinion pin, which allows unhindered rotation of the sun gear.
  • a preferred structural design of the spur gear differential provides for the outer enveloping circle of the spur gear differential to be designed to be smaller than the tip circle of an internal toothing of the associated ring gear. This measure results in a simplified assembly sequence, since there is no need to join the ring gear before assembling the spur gear differential over the planet gears.
  • the pinion pin of the spur gear in the installation was positively fixed on the component geometries of the differential cover and the plane carrier axially.
  • the differential gear bolt is inserted with one end side into a blind hole of the planet carrier and with the other end side fitted into a hole in the differential cover and supported on a radially inwardly directed rim of the differential cover.
  • a complementary form-fitting and / or material-locking anti-rotation device can be dispensed with for reasons of cost.
  • the planet gear bolts of the stepped planetary sets are permanently secured in position by means of caulking at both soft ends of the planet gear bolts.
  • the caulking of the planetary gear pin creates backlash-free attachment to the differential cover and the planetary carrier, which does not require any additional interference fit of the pin in the planetary carrier.
  • the caulking results in a permanent connection that can withstand high mechanical requirements, such as vibrations that occur when the gear assembly is in operation.
  • a caulking tool with a special contour is preferably used for caulking the planetary gear pin, which initially has an acute angle which is then increasingly flatter, so that the deformation increases as the axial caulking path increases. With this measure, the resilience of the caulking can be increased while the caulking force remains the same.
  • the caulking of the planetary gear pin also known as caulking marks, also leads to improved torsional rigidity of the planetary carrier, which for example has a positive effect on the bearing of the planetary gears, reduces the toothing forces of the gears and consequently optimizes the service life of the entire transmission arrangement.
  • the stepped planetary sets are free-flying, with the planetary gears also called spur gears being mounted on roller bearings designed as a needle roller ring. All of the planet gears are centered on the planet gear pin and the needle roller and cage assembly. The release of the planetary gear sets necessary for load balancing takes place via the associated ring gear. An axial distance of at least 6 mm is provided for the spur gears of the stepped planetary set, which are also referred to as transmission gears, which are assigned to a planetary gear pin in each case.
  • the gear arrangement includes a lubrication device, with the associated pinion pin or a blind hole or a longitudinal hole closed on one side due to installation for specific lubrication of the rotatably mounted differential gears or spur gears of the spur gear differential and the stepped planetary set.
  • a lubrication device with the associated pinion pin or a blind hole or a longitudinal hole closed on one side due to installation for specific lubrication of the rotatably mounted differential gears or spur gears of the spur gear differential and the stepped planetary set.
  • egg ne oil pan is used in the differential pin of the spur gear end.
  • Oil or oil mist is absorbed within the gear arrangement due to centrifugal forces in the operating state via the oil pan, which can also be referred to as a baffle and which preferably connects all the planetary gear bolts around the circumference. then passed into the longitudinal bore and fed from there through radial bores of the plane pin of the bearing.
  • the planetary gear bolt assigned to the stepped planetary set preferably forms a partition wall in the middle of the longitudinal bore to form a blind bore so that lubricating oil can then flow into the axially offset bearings of the spur gears via radial bores.
  • Skiving is preferably suitable for producing the toothing of the stepped planetary set and / or of the spur gear differential. Skiving is a continuous cutting process for the production of gears. This production process combines hobbing and shaping through continuous rolling with axial feed and enables the production of internal and external gears. The envisaged power skiving enables a higher cross-axis angle with a larger distance, which can reduce tool wear and thus costs.
  • the toothings of the stepped planetary set are preferably arranged axially at a distance of at least 6 mm from one another.
  • a spur gear differential and a stepped planetary gear assembly including is preferably suitable for the drive train of an electric drive unit of a motor vehicle.
  • the e-axle is a solution for the electric drive of purely electric vehicles or for hybrid applications.
  • components such as the motor, axle and gearbox, which are used separately in a conventional design, are combined into one structural unit.
  • Fig. 1 In a longitudinal section, a constructed according to the invention, a spur gear differential and a stepped planetary including gear arrangement;
  • FIG. 2 in a three-dimensional view, a section of a spur gear differential and a stepped planetary set of the gear arrangement according to FIG. 1;
  • a stepped planetary set 2 which is also known as a gear ratio section or reduction step, for example, an electric motor (not shown) introduced drive torque translated or reduced from a high input speed to a low output speed.
  • the converted output torque is then distributed via the spur gear differential 3 to its output shafts connected to the drive wheels of the motor vehicle.
  • a planet carrier 4 is vorgese hen, which is inserted in a housing 5 of the transmission arrangement 1.
  • the planetary carrier 4 is on the drive side via the toothing engagement between the input sun 39, which is the output shaft, for example as a floating bearing 34 15 encloses, and the large planet gears 17 rotatably mounted.
  • the output-side bearing of the planetary carrier 4 is via a fixed bearing 36.
  • a Rillenkugella ger is provided, which is inserted between a receptacle 37 of the gear housing 5 of the Ge transmission arrangement 1 and a cylindrical, axially protruding projection 38 of the Differen tialdeckels 12, which is torsionally rigid with the Planet carrier 4 is connected.
  • the spur gear differential 3 comprises, as shown in Fig. 2, two planetary sets 6, 7 with differently dimensioned differential gears, a wide differential gear 8 and a narrow differential gear 9, which are each rotatably mounted on an associated balance wheel bolts 10, 11, which rotatably in associated bores of the planetary gear carrier 4 and a differential cover 12 are used.
  • the differential gears 8, 9 are each toothed with a sun gear 13, 14, each sun gear 13, 14 being connected to an output shaft 15, 16 in a rotationally fixed manner.
  • the stepped planetary set 2 includes transmission gears, with two axially offset, helical and interconnected, also planet gears called spur gears 17, 18 via roller bearings 19, 20 rotatably mounted on a planet gear pin 21, which are in engagement with other gears (not shown) . Needle roller and cage assemblies (KZK) are preferably suitable as roller bearings 19, 20. To achieve a cost-effective production, the two mutually offset, differently dimensioned spur gears 17, 18 are arranged at an axial distance of> 6 mm. Furthermore, the stepped planetary set 2 or its planetary gear pin 21 overlaps the sun gears 13, 14 when installed and consequently a toothing plane of the spur gear 3.
  • the axially compact design of the transmission arrangement 1 is emphasized by the toothing plane of the sun gear 13 of the spur gear 3 axially close to the planet carrier 4 placed.
  • a recess 33 for the sun gear 13 is made locally in the guide support structure of the planetary carrier 4.
  • the planetary gear bolts 21 of the stepped planetary set 2 are permanently secured in position by means of caulking 22, 23 at both soft ends of the planetary gearbol 21.
  • the caulking 22, 23 over the circumference of the planetary gear is advantageous.
  • Bolt 21 arranged distributed, whereby the planet gear pin 21 is non-positively and / or positively connected to the differential cover 12 or the planet carrier 4 and secured in a rotationally and positionally fixed manner.
  • a blind hole 24 is made in the planet gear bolt 21, into which in operating state 1 lubricating oil flows in from the side facing the output shaft 16 and into one via radial bores 25 of the planet gear bolt 21 Annular space 26 bounded axially by the roller bearings 19, 20 occurs.
  • Fig. 2 and Fig. 3 illustrate in different views the arrangement or installation positions of the planetary sets 6, 7 of the spur gear differential 3 and the transmission gears forming, also called double planetary spur gears 17, 18 of the stepped planetary set 2, to create a compact in the axial direction Ge gear arrangement 1.
  • Fig. 2 is a through the toothing plane of the spur gear differential 3 guided planetary gear pin 21 from the stepped planetary set 2, which runs at a radial distance from the sun gears 13, 14 of the spur gear 3.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
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Abstract

La présente invention concerne un agencement de transmission (1) pour un véhicule automobile, comprenant un train planétaire étagé (2) et un différentiel à engrenage droit (3) raccordés par l'intermédiaire d'un support d'engrenages planétaires commun (4), ledit différentiel présente un premier et un second train planétaire (6, 7), qui s'engrènent par paires, chaque train planétaire (6, 7) comprenant un planétaire (13, 14) qui est fixé en rotation à un arbre de sortie (15, 16) du différentiel à engrenage droit (3) ; des couples introduits par l'intermédiaire d'un arbre d'entrée dans l'agencement de transmission (1) à partir du train planétaire étagé (2) sont transférés dans le différentiel à engrenage droit (3) puis aux arbres de sortie (15, 16), puis à des roues entraînées du véhicule ; un plan d'engrènement du train planétaire étagé (2) chevauchant radialement au moins un planétaire (13, 14) du différentiel à engrenage droit (3) ; des tourillons de pignon différentiel (10, 11) dans le train planétaire étagé (2) passant à travers un plan d'engrènement du différentiel à engrenage droit (3) à une distance radiale par rapport aux planétaires (13, 14) et fixant radialement et axialement un couvercle de différentiel (12) au niveau des extrémités ; et le support d'engrenages planétaires (4) est monté dans le logement (4) par l'intermédiaire d'un palier flottant (34) créé par la mise en prise d'un planétaire d'entrée (39) et des satellites doubles sous la forme d'engrenages droits (17) dans le train planétaire étagé (2), et sur le côté opposé au moyen du couvercle de différentiel (12) par l'intermédiaire d'un palier fixe (36).
PCT/DE2020/100616 2019-08-05 2020-07-15 Agencement de transmission compact doté d'un train planétaire étagé et d'un différentiel à engrenage droit WO2021023338A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202080055478.8A CN114207321B (zh) 2019-08-05 2020-07-15 具有多级行星齿轮组和正齿轮差速器的紧凑的变速器装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019121079.8A DE102019121079B3 (de) 2019-08-05 2019-08-05 Kompakte Getriebeanordnung mit Stufenplanetensatz und Stirnraddifferential
DE102019121079.8 2019-08-05

Publications (1)

Publication Number Publication Date
WO2021023338A1 true WO2021023338A1 (fr) 2021-02-11

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Country Link
CN (1) CN114207321B (fr)
DE (1) DE102019121079B3 (fr)
WO (1) WO2021023338A1 (fr)

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DE102021123097B3 (de) * 2021-09-07 2022-12-29 Schaeffler Technologies AG & Co. KG Planetengetriebe sowie Schmiermittelfangschale für ein Planetengetriebe
TWM628316U (zh) * 2022-02-25 2022-06-11 如陽科技股份有限公司 減速機之傳動系統

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WO2018188691A1 (fr) * 2017-04-11 2018-10-18 Schaeffler Technologies AG & Co. KG Dispositif d'entraînement pour un véhicule automobile
DE102017114480A1 (de) * 2017-06-29 2019-01-03 Schaeffler Technologies AG & Co. KG Getriebeanordnung für ein Fahrzeug, elektrische Achse sowie Fahrzeug mit der elektrischen Achse

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