WO2023030676A1 - Transmission comportant un premier étage d'engrenage planétaire - Google Patents

Transmission comportant un premier étage d'engrenage planétaire Download PDF

Info

Publication number
WO2023030676A1
WO2023030676A1 PCT/EP2022/025337 EP2022025337W WO2023030676A1 WO 2023030676 A1 WO2023030676 A1 WO 2023030676A1 EP 2022025337 W EP2022025337 W EP 2022025337W WO 2023030676 A1 WO2023030676 A1 WO 2023030676A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
shaft
ring
wheel
planetary
Prior art date
Application number
PCT/EP2022/025337
Other languages
German (de)
English (en)
Inventor
Zili Wu
Original Assignee
Sew-Eurodrive 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
Priority claimed from CN202111052930.8A external-priority patent/CN115773338A/zh
Application filed by Sew-Eurodrive Gmbh & Co. Kg filed Critical Sew-Eurodrive Gmbh & Co. Kg
Publication of WO2023030676A1 publication Critical patent/WO2023030676A1/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
    • F16H57/00—General details of gearing
    • F16H57/0018—Shaft assemblies for gearings
    • F16H57/0025—Shaft assemblies for gearings with gearing elements rigidly connected to a shaft, e.g. securing gears or pulleys by specially adapted splines, keys or methods
    • 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
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/0876—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with axial keys and no other radial clamping
    • 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/46—Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels

Definitions

  • the invention relates to a transmission with a first planetary gear stage.
  • a planetary gear is an epicyclic gear and has an epicyclic gear.
  • a transmission is also known from CN1 06 274459 A.
  • a wheel drive for a mobile vehicle is known from DE 199 22 651 A1.
  • a multi-stage planetary gear is known from DD 39 725 A1.
  • DE 14 30 245 A discloses an outer end of the axle with planetary gear mechanism.
  • a gear wheel is known from DE 10 2007 034449 A1.
  • the invention is therefore based on the object of making a transmission more precise to produce, ie in particular a longer service life for the bearings and toothed parts.
  • the object is achieved in the transmission according to the features specified in claim 1.
  • first planetary gear stage which has a first sun gear shaft, internal teeth, in particular a first ring gear connected to a housing part or a first ring gear designed in one piece with the housing part, and a planetary gear
  • the planetary gear has a planetary gear into which the cylindrical extension, in particular the pin, of a gear designed as a plug-in pinion is inserted, the teeth of the planetary gear meshing with the teeth of the first sun gear shaft, the teeth of the gear meshing with the teeth of the internal gearing
  • the planet wheel is connected to the gear wheel in a rotationally fixed manner by means of a feather key connection, and/or the extension has a groove, in particular a feather key groove, in which a feather key is accommodated, which also protrudes at least partially into a groove of the gear wheel, in particular for the circumferential direction about the axis of rotation of the planetary gear positive connection of the planetary gear with the gear.
  • the advantage here is that is made possible by an axially bilateral bearing of the planetary wheel and thus a precise alignment of the planetary wheel can be achieved even during operation. This is because the bearing on both sides, which is arranged axially outside the toothing, prevents the planet wheel from tilting.
  • the axially extended design also contributes to this. Because by connecting a plug-in pinion, the planetary gear is axially longer overall.
  • the stabilization is further improved by the large bearing distance. Over and beyond the different tip circle diameters of the gear wheel and the planet wheel not only allow different transmission ratios, but also contribute to a further improved stabilization of the planetary wheel. This is because the radial supports provided by the respective toothing, in particular the sun toothing and the internal toothing, are far apart axially and thus enable an additional leverage effect, which strengthens the stabilization.
  • the first planet wheel is thermally shrunk onto the extension and/or thermally joined, in particular so that the gear wheel is non-positively connected to the first planet wheel.
  • the advantage here is that increased security can be achieved. Because in addition to the form-fitting connection, a non-positive connection is effected.
  • the planetary wheel is slipped onto a planetary pin, the planetary pin being rotatably mounted axially on both sides via a respective bearing accommodated in a planetary carrier of the transmission, in particular with the bearings being spaced apart from the gearwheel and/or from the planetary wheel in the axial direction.
  • the advantage here is that the stability against tilting of the planetary wheel is improved. This enables greater precision.
  • an input shaft of the transmission is rotatably mounted by means of bearings accommodated in a bearing flange of the transmission, the bearing flange being connected to one or the housing part of the transmission, in particular by means of screws, the first sun gear shaft having teeth, in particular splined teeth, which is inserted into a hollow area of the input shaft, in particular a hollow shaft section, for the non-rotatable connection of the input shaft to the sun gear.
  • the input shaft is non-rotatably connected to the first sun wheel shaft via a gear coupling. In this way, deviations from the ideal position of the input shaft have an effect on the input side only slightly. The first sun wheel shaft thus drives the first gear stage more precisely than if this gear coupling were not present.
  • the first sun gear shaft is rotatably mounted at its end region facing away from the input shaft by means of a bearing, which is accommodated in a second sun gear shaft, in particular with the inner ring of the bearing being slipped onto the first sun gear shaft and the outer ring of the bearing in the second sun gear shaft is recorded.
  • the first planet carrier has internal teeth, into which an externally toothed area of the second sun gear shaft is inserted and with which the externally toothed area of the second sun gear shaft is engaged, in particular for the non-rotatable connection of the first planet carrier with the second sun gear shaft, in particular with the first Planet carrier is rotatably mounted on a bearing accommodated in the housing part.
  • the second sun gear shaft has teeth which mesh with the teeth of a second planet wheel which is rotatably mounted on a second planet pin, in particular by means of needle bearings, wherein the second planet pin is accommodated in a planet carrier, the toothing of the second planet wheel being in engagement with the internal toothing of a second ring gear.
  • needle bearings in the second gear stage can be used for the planet gear.
  • the ring gear can be designed to be less extended radially than the planetary carrier is designed to be.
  • the second ring gear is non-rotatably connected to a support ring, in particular by the support ring being at least partially inserted into the ring gear, the support ring having external teeth which mesh with the internal teeth of the ring gear.
  • the advantage here is that the ring gear is connected to the support ring by means of a toothed coupling, in particular for decoupling tilting forces, and the support ring can be slipped onto finely machined alignment surfaces provided on annular elevations formed on the housing part. The support ring can thus be precisely aligned and holds the second ring gear in the desired position.
  • radially directed, annular elevations, in particular elevations are formed on the housing part, in particular in relation to the axis of rotation of the second sun gear shaft, which have aligning surfaces running around in the circumferential direction, onto which the support ring is pushed, in particular for aligning the support ring together with the second ring gear, in particular wherein the alignment surfaces are spaced from each other in the axial direction.
  • the advantage here is that surfaces which are as finely machined as possible are provided for aligning the support ring and thus the second ring gear, thus enabling high precision during production.
  • the first sun gear shaft is aligned coaxially with the second sun gear shaft.
  • the transmission can be designed as a coaxial transmission.
  • the first sun gear shaft can be mounted in the second sun gear shaft, so that the transmission can be made very compact. It is advantageous that the relative speed of the two sun gear shafts is lower than the speed of the first sun gear shaft relative to the housing part.
  • a sleeve is connected to the second planet carrier, which sleeve surrounds the second ring gear radially, in particular with a gap region being formed between the second ring gear and the sleeve.
  • the advantage here is that the ring gear is surrounded radially by the rotating part, namely the sleeve and the second planet carrier.
  • a first bearing is fitted with its inner ring onto a cylindrical section of the housing part and its outer ring is accommodated in the sleeve and/or a second bearing, in particular an outer ring of a second bearing, is accommodated in the sleeve, the inner ring of which is placed on the Support ring is attached, in particular wherein the support ring has a step against which the second bearing is employed.
  • the advantage here is that the sleeve is mounted on the two bearings and thus the second planet carrier is mounted on the sleeve. In this way, a large axial distance between the two bearings and the planet carrier can be achieved, so that tilting can be avoided.
  • the sleeve can be designed as a hollow part, in particular essentially as a hollow cylinder.
  • the support ring is delimited in the axial direction by a shaft nut screwed onto a screw thread applied to the housing part.
  • a shaft sealing ring accommodated by the sleeve seals towards the housing part, i.e. in particular a sealing lip of the shaft sealing ring rests against a finely machined surface of the housing part, in particular a dust seal, in particular a dust seal designed as a V-ring, additionally seals the sleeve towards the housing part.
  • a dust seal in particular a dust seal designed as a V-ring
  • a radial bore running through the sleeve opens into a spatial area adjacent to the first and second bearings, in particular an axial bore introduced into the sleeve crossing the radial bore and opening into a spatial area in which the toothing of the second planet wheel is located.
  • the advantage here is that oil can be supplied through the radial bore.
  • the radial bore is preferably sealed off from the environment with a sealing plug.
  • FIG. 1 shows a sectional view of a transmission according to the invention.
  • FIG. 2 shows an oblique view of a multi-part planetary wheel of the transmission.
  • the transmission has two planetary gear stages.
  • a bearing flange 17 is connected to the housing part 10 of the transmission, in which bearings are accommodated which support the input shaft 14 in a rotatable manner.
  • the input shaft 14 has a hollow shaft section in which internal splines are incorporated, which mesh with an external spline of a first sun gear shaft 15 of a first planetary gear stage that is inserted into the hollow shaft section.
  • the external spline is arranged on a first axial end area of the first sun gear shaft 15 .
  • This sun gear shaft 15 is rotatably mounted by means of a bearing 18 at its other axial end region, in particular that which faces away from the input shaft 14 .
  • the bearing 18 is accommodated in a second sun gear shaft 3, the second sun gear shaft 3 belonging to a second planetary gear stage.
  • the toothing of the planet gear 11 meshes with the toothing of the first sun gear shaft 15 .
  • Gear wheel 8 designed as an insert pinion is inserted into a recess in planet wheel 11 and connected to planet wheel 11 in a form-fitting manner by means of a feather key 9 .
  • the hollow planetary wheel 11 is slipped onto a cylindrical extension of the gearwheel 8 , a keyway being incorporated in the cylindrical extension, into which the keyway 9 is inserted, which also protrudes into an axial groove of the planetary wheel 11 .
  • An internally toothed ring gear is connected to the housing part 10 or constructed in one piece, in particular in one piece.
  • the toothing of the gear wheel 8 meshes with the internal toothing of the ring gear, the toothing of the planet wheel 11 meshes with the toothing of the first sun wheel shaft 15 .
  • the toothing of gear wheel 8, which is preferably designed as an involute toothing, has a smaller outside diameter, in particular the addendum circle diameter, than the toothing of planet wheel 11, which is preferably designed as involute toothing.
  • the inner diameter of the ring gear is smaller than the addendum circle diameter of the toothing of the planetary gear 11.
  • the inner toothing of the ring gear is thus arranged at a radial distance from the toothing of the planetary gear 11, in particular at a smaller radial distance from the axis of rotation of the first sun gear shaft 15.
  • the gear wheel 8 is hollow and slipped onto a planet pin 13, which is mounted axially on both sides in the first planet carrier 6 via bearings (7, 12), in particular roller bearings.
  • the bearings 7 and 12 are arranged axially outside the teeth of the gear wheel 8 and the planet wheel 11 .
  • the first planetary carrier 6 is mounted on the one hand via a bearing 16 accommodated in the bearing flange 17 and on the other hand via a bearing 19 which is accommodated in the housing part 10 .
  • the second sun gear shaft 3 has, on its axial end region associated with the first sun gear shaft 15, external teeth, in particular splines, with which the second sun gear shaft 3 is inserted into an internally toothed axial end area of the first planet carrier 6 .
  • the second sun gear shaft 3 has no direct bearing.
  • the second sun gear shaft 3 is inserted into the first planetary carrier 6 and is thus mounted indirectly via the bearing 19 of the first planetary carrier 6 .
  • the second sun gear shaft 3 has a toothing that acts as a sun gearing, which meshes with, in particular three, second planetary gears 24, each of the second planetary gears 24 being rotatably mounted on a respective planetary pin 23 via bearings, in particular needle bearings .
  • the planet bolts 23 are accommodated in a double-sided planetary carrier 25 .
  • the teeth of the planet gears 24 are also in engagement with a second ring gear 1.
  • the second ring gear 1 has internal teeth which are in mesh with the teeth of the planet gears 24.
  • the internal toothing of the second ring gear 1 is axially extended, i.e. protrudes axially beyond the planetary gears 24, so that an externally toothed area of a support ring 2 can be inserted into the second ring gear 1 and this externally toothed area thus meshes with the internal toothing of the second ring gear 1 is bringable.
  • the second ring gear 1 can be positively connected to the support ring 2 in the circumferential direction, i.e. in particular can be connected in a torque-proof manner.
  • the support ring 2 is slipped onto ring-shaped elevations, which have finely machined alignment surfaces 21 on their radial outside and 22.
  • These ring-shaped elevations are formed on a cylindrical area of the housing part 10 which in the axial direction covers an area which is encompassed by the area covered by the second sun gear shaft 3 in the axial direction.
  • the support ring 2 is arranged on the side of the second planet gears 24 facing the first sun gear shaft 15 .
  • An inner ring of a bearing 20 is slipped onto the support ring 2, the outer ring of which is accommodated in a sleeve 27, in particular a bearing bush, which is non-rotatably connected to the planetary carrier 25, in particular by means of screws.
  • the sleeve 27 also accommodates the outer ring of a second bearing 20, the inner ring of which is slipped onto a cylindrically shaped area, in particular a bearing receiving area, of the housing part d10.
  • the sleeve 27 is arranged axially between the second planet gear 24 and the first sun gear shaft 15 .
  • the second planet carrier 25 is rotatably mounted via the sleeve 27 in that the sleeve 27 is mounted on the housing part 10 on the one hand via a bearing 20 and on the other hand via another bearing 20 together with the support ring 2 on the housing part 10 .
  • the area covered by the sleeve 27 in the axial direction overlaps with the area covered by the second planet gears 24 in the axial direction and is encompassed by the area covered by the second sun gear shaft 3 in the axial direction.
  • a seal accommodated in the sleeve 27 comprises a shaft sealing ring 4 whose sealing lip 4 runs on a finely machined surface of the housing part 10 and thus seals the sleeve 27 towards the housing part 10 .
  • the sealing lip thus touches the housing part 10.
  • the sleeve 27 has a seat for the shaft sealing ring 4.
  • the finely machined surface of the housing part 10 is arranged radially inside the sealing ring 3 and/or the sleeve 27 .
  • a dust seal 5 preferably designed as a V-ring, seals the housing part 10 from the sleeve 27 .
  • the sleeve 27 has a radially continuous bore which is closed with a sealing plug 28 .
  • oil can be refilled, in particular through the sleeve 27 through.
  • the sleeve 27 is a rotating part and the oil refilling is therefore not executable.
  • An axially directed bore into which the radial bore opens or which crosses the radial bore, opens into a gap region, in particular an annular gap, arranged radially between sleeve 27 and the second ring gear.
  • the sleeve 27 acts as an axial extension of the second planet carrier 25 and surrounds the second ring gear 1 radially.
  • the gear wheel 8 is positively connected to the planet wheel 11 by means of the feather key 9, but the gear wheel 8 designed as a plug-in pinion is also inserted with its cylindrical extension into the planet wheel 11, this planet wheel being thermally shrunk on. During manufacture, the gear wheel 8 is heated before it is inserted, so that there is a temperature difference of more than 40° C. between the gear wheel 8 and the planet wheel 11 .
  • connection between the gear wheel 8 and the planet wheel 11 is not only designed in a form-fitting manner, but also in a force-fitting manner.
  • the sleeve 27 is designed in one piece with the second planetary carrier 25, in particular in one piece.

Abstract

L'invention divulgue une transmission comportant un premier étage d'engrenage planétaire qui comprend un premier arbre d'engrenage solaire, une denture intérieure et un pignon, le pignon étant pourvu d'un engrenage planétaire dans lequel la saillie cylindrique, en particulier le tourillon, d'une roue dentée se présentant sous la forme d'un pignon d'insertion est inséré, les dents de l'engrenage planétaire s'engrenant avec les dents du premier arbre d'engrenage solaire, les dents de la roue dentée s'engrènent avec les dents de la denture intérieure, et l'engrenage planétaire est relié solidairement en rotation à la roue dentée au moyen d'une liaison à clé parallèle.
PCT/EP2022/025337 2021-09-06 2022-07-20 Transmission comportant un premier étage d'engrenage planétaire WO2023030676A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN202111052930.8 2021-09-06
CN202111052930.8A CN115773338A (zh) 2021-09-06 2021-09-06 具有第一行星齿轮传动级的减速器
DE102021005345.1 2021-10-27
DE102021005345 2021-10-27

Publications (1)

Publication Number Publication Date
WO2023030676A1 true WO2023030676A1 (fr) 2023-03-09

Family

ID=82846359

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2022/025337 WO2023030676A1 (fr) 2021-09-06 2022-07-20 Transmission comportant un premier étage d'engrenage planétaire

Country Status (2)

Country Link
DE (1) DE102022002656A1 (fr)
WO (1) WO2023030676A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20230019363A1 (en) * 2021-07-16 2023-01-19 Ge Avio S.R.L. Damper system for an engine shaft

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1968604A (en) 1931-05-09 1934-07-31 Hertz Stanislas Transmitting gear
US1985964A (en) 1932-09-13 1935-01-01 Gen Electric Elastic fluid turbine
DD39725A1 (de) 1964-02-04 1965-06-15 Herbert Brandt Mehrstufiges Planetengetriebe
DE1430245A1 (de) 1961-05-19 1968-11-07 Rockwell Standard Co Achsaussenende mit Planetengetriebe
DE19922651A1 (de) 1999-05-18 2000-11-23 Zahnradfabrik Friedrichshafen Radantrieb für ein Mobilfahrzeug
DE10160685A1 (de) * 2001-12-11 2003-06-26 Sew Eurodrive Gmbh & Co Planetengetriebe, Getriebemotor und Baureihe von Getriebemotoren
DE102007034449A1 (de) 2007-07-20 2009-01-22 Sew-Eurodrive Gmbh & Co. Kg Zahnrad, Welleneinheit, Getriebe, Getriebe-Baureihe und Verfahren zur Herstellung eines Getriebes
CN103791033A (zh) 2012-10-30 2014-05-14 吴小杰 轴承用脂润滑双联双臂式风电增速箱
DE102014213669A1 (de) 2014-07-15 2016-01-21 Zf Friedrichshafen Ag Windkraftgetriebe mit Stufenplanet
CN106274459A (zh) 2016-08-31 2017-01-04 成都雅骏新能源汽车科技股份有限公司 一种集成式电驱动桥
DE102019006068A1 (de) 2018-09-18 2020-03-19 Sew-Eurodrive Gmbh & Co. Kg Getriebe mit zumindest einer ersten und einer zweiten Planetengetriebestufe

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1968604A (en) 1931-05-09 1934-07-31 Hertz Stanislas Transmitting gear
US1985964A (en) 1932-09-13 1935-01-01 Gen Electric Elastic fluid turbine
DE1430245A1 (de) 1961-05-19 1968-11-07 Rockwell Standard Co Achsaussenende mit Planetengetriebe
DD39725A1 (de) 1964-02-04 1965-06-15 Herbert Brandt Mehrstufiges Planetengetriebe
DE19922651A1 (de) 1999-05-18 2000-11-23 Zahnradfabrik Friedrichshafen Radantrieb für ein Mobilfahrzeug
DE10160685A1 (de) * 2001-12-11 2003-06-26 Sew Eurodrive Gmbh & Co Planetengetriebe, Getriebemotor und Baureihe von Getriebemotoren
DE102007034449A1 (de) 2007-07-20 2009-01-22 Sew-Eurodrive Gmbh & Co. Kg Zahnrad, Welleneinheit, Getriebe, Getriebe-Baureihe und Verfahren zur Herstellung eines Getriebes
CN103791033A (zh) 2012-10-30 2014-05-14 吴小杰 轴承用脂润滑双联双臂式风电增速箱
DE102014213669A1 (de) 2014-07-15 2016-01-21 Zf Friedrichshafen Ag Windkraftgetriebe mit Stufenplanet
CN106274459A (zh) 2016-08-31 2017-01-04 成都雅骏新能源汽车科技股份有限公司 一种集成式电驱动桥
DE102019006068A1 (de) 2018-09-18 2020-03-19 Sew-Eurodrive Gmbh & Co. Kg Getriebe mit zumindest einer ersten und einer zweiten Planetengetriebestufe

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20230019363A1 (en) * 2021-07-16 2023-01-19 Ge Avio S.R.L. Damper system for an engine shaft

Also Published As

Publication number Publication date
DE102022002656A1 (de) 2023-03-09

Similar Documents

Publication Publication Date Title
EP1343982B2 (fr) Boite planetaire
EP3371482B1 (fr) Transmission comportant un flasque de butée
EP3322908B1 (fr) Mécanisme de transmission comprenant un flasque de butée pour le blocage axial d'éléments roulants d'un palier
DE1951427B2 (de) Ins Langsame übersetzendes Getriebe
DE10129450A1 (de) Stellglied für eine Fahrzeug-Lenkvorrichtung
EP1188002B1 (fr) Boite planetaire
WO2023030676A1 (fr) Transmission comportant un premier étage d'engrenage planétaire
WO2002053941A1 (fr) Engrenage angulaire avec repartition de couple
DE10054798A1 (de) Elektrisch angetriebene Vorrichtung zur Drehwinkelverstellung einer Welle gegenüber ihrem Antrieb
EP3322916B1 (fr) Transmission comprenant au moins un arbre à excentrique
EP1915553A1 (fr) Adaptateur, engrenage planetaire, entrainement, et procede
DE102010038597A1 (de) Zentrierung eines Planetengetriebes
EP3308055A1 (fr) Transmission pourvue d'un carter et d'un engrenage planétaire
DE102019118187A1 (de) Differenzialgetriebe
WO2023030677A1 (fr) Transmission dotée d'un second étage d'engrenage planétaire
DE102005029537A1 (de) Planetengetriebe
EP3684639B1 (fr) Unité carter et ensemble tourillon
DE10232247B3 (de) Exzentergetriebe, insbesondere Rollenexzentergetriebe
DE3614803A1 (de) Getriebe zum antrieb der walzen einer walzstrasse
DE102004011057B4 (de) Differenzialgetriebe für Kraftfahrzeuge
DE112022002761T5 (de) Planetenuntersetzungsgetriebe mit mindestens einem Planetenrad mit mindestens einem Außengewindeabschnitt
WO2023104233A1 (fr) Boîte de vitesses à trains épicycloïdaux avec rondelle de butée pour deux couronnes, support axial pour couronne, rondelle de butée pour couronne, et chaîne cinématique de véhicule électrique avec couronnes supportées axialement
WO2022242907A2 (fr) Boîte de vitesses comportant une partie carter et un arbre creux
DE102006042212A1 (de) Getriebe mit Axialkraftabstützung für ein Zahnrad
DE102018130118A1 (de) Stirnraddifferentialgetriebe

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: 22751645

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 2022751645

Country of ref document: EP

ENP Entry into the national phase

Ref document number: 2022751645

Country of ref document: EP

Effective date: 20240408