WO2023030677A1 - Transmission dotée d'un second étage d'engrenage planétaire - Google Patents

Transmission dotée d'un second étage d'engrenage planétaire Download PDF

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Publication number
WO2023030677A1
WO2023030677A1 PCT/EP2022/025338 EP2022025338W WO2023030677A1 WO 2023030677 A1 WO2023030677 A1 WO 2023030677A1 EP 2022025338 W EP2022025338 W EP 2022025338W WO 2023030677 A1 WO2023030677 A1 WO 2023030677A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
shaft
ring
wheel
bearing
Prior art date
Application number
PCT/EP2022/025338
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 CN202111052923.8A external-priority patent/CN115773337A/zh
Application filed by Sew-Eurodrive Gmbh & Co. Kg filed Critical Sew-Eurodrive Gmbh & Co. Kg
Priority to EP22751646.5A priority Critical patent/EP4399423A1/fr
Publication of WO2023030677A1 publication Critical patent/WO2023030677A1/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
    • F16H57/08—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
    • 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 second planetary gear stage.
  • a planetary gear is an epicyclic gear and has an epicyclic gear.
  • An axle drive is known from DE 26 01 454 A1.
  • a two-stage planetary gear is known from DE 42 28 815 A1.
  • a planetary gear is known from US Pat. No. 5,024,636 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.
  • 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.
  • the planetary gear stage has a first sun gear shaft, a first planet bolt, a first planet gear and a first ring gear and a first planet carrier, the first planet bolt being accommodated in a first planet carrier, the toothing of the first planetary gear meshes with the internal toothing of a first ring gear and with a toothing of the first sun gear shaft, the first ring gear being non-rotatably connected to a support ring, the support ring being held by a housing part of the transmission, in particular on a cylindrical area and/or is attached to cylindrically designed areas, in particular alignment surfaces, of the housing part.
  • the support ring can be aligned very precisely over the area or areas.
  • the ring gear held by the support ring is also precisely aligned.
  • the internal teeth of the ring gear are used to create a toothed coupling with the support ring. Tilting and other loads can thus be derived and decoupled.
  • the support ring is at least partially inserted into the ring gear, the support ring having external teeth which mesh with the internal teeth of the ring gear and/or are inserted into the internal teeth, in particular the internal teeth being uninterrupted, in particular uninterrupted in the axial direction , is executed.
  • the transmission is designed with a second planetary gear stage, which has a second sun gear shaft, internal teeth, in particular a second ring gear connected to a housing part or a second ring gear designed in one piece with the housing part, and a planetary gear, such that 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, with the toothing of the planetary gear meshing with a toothing of the second sun gear shaft, with the toothing of the gearwheel meshing with a toothing 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. Because the bearing on both sides, which is arranged axially outside the toothing, prevents this Occurrence of tilting of the rotating wheel.
  • 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.
  • the different tip circle diameters of the gear and the planetary gear not only allow different transmission ratios, but also contribute to further improved stabilization of the planetary gear. 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 second 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 second planet wheel.
  • 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 second sun wheel 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 the sun wheel.
  • the input shaft is rotationally connected to the second sun gear shaft via a gear coupling. In this way, deviations from the ideal position of the input shaft that are introduced on the input side only have a minor effect.
  • the second sun gear shaft thus drives the second gear stage more precisely than if this gear coupling were not present.
  • the second 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 first sun gear shaft, in particular with the inner ring of the bearing being slipped onto the second sun gear shaft and the outer ring of the bearing being placed in the first sun gear shaft is recorded.
  • the second planet carrier has internal teeth, into which an externally toothed area of the first sun gear shaft is inserted and with which the externally toothed area of the first sun gear shaft is engaged, in particular for the non-rotatable connection of the second planet carrier with the first sun gear shaft, in particular with the second Planet carrier is rotatably mounted on a bearing accommodated in the housing part.
  • the first sun gear shaft has teeth which mesh with the teeth of a first planet wheel which is rotatably mounted on a first planet pin, in particular by means of needle bearings.
  • the first planet pin is accommodated in a planet carrier, wherein the toothing of the first planetary gear meshes with the internal toothing of a first ring gear.
  • needle bearings can be used for the planet gear in the first gear stage.
  • the ring gear can be designed to be less extended radially than the planetary carrier is designed to be.
  • the first 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 first 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 first sun gear shaft, which have aligning surfaces running in the circumferential direction, onto which the support ring is pushed, in particular for aligning the support ring together with the first 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 first ring gear, thus enabling high precision during production.
  • the second sun gear shaft is aligned coaxially with the first sun gear shaft.
  • the transmission can be designed as a coaxial transmission.
  • the second sun gear shaft is in the first sun gear shaft stored, so that the transmission is very compact executable. It is advantageous that the relative speed of the two sun gear shafts is lower than the speed of the second sun gear shaft relative to the housing part.
  • a sleeve is connected to the first planet carrier, which sleeve surrounds the first ring gear radially, in particular with a gap region being formed between the first ring gear and the sleeve.
  • a second 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 first bearing, in particular an outer ring of a first 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 first bearing is employed.
  • the advantage here is that the sleeve is mounted on the two bearings and thus the first 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 in the sleeve seals towards the housing part, in particular, therefore, a sealing lip of the shaft seal 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 from the housing part.
  • a dust seal in particular a dust seal designed as a V-ring
  • a radial bore passing through the sleeve opens into a spatial area adjoining the second and first 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 first 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 second sun gear shaft 15 of a second planetary gear stage that is inserted into the hollow shaft section.
  • the external spline is arranged on a second axial end area of the second 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 first sun gear shaft 3, the first sun gear shaft 3 belonging to a first planetary gear stage.
  • 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 gear wheel 8 meshes with the internal toothing of the ring gear, and the toothing of planet wheel 11 meshes with the toothing of second 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 second 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 second 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 second planet 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 first sun gear shaft 3 has on its axial end area associated with the second sun gear shaft 15 external teeth, in particular splines, with which the first sun gear shaft 3 is inserted into an internally toothed axial end area of the second planetary carrier 6 .
  • the first sun gear shaft 3 has no direct bearing.
  • the first sun gear shaft 3 is inserted into the second planetary carrier 6 and is thus mounted indirectly via the bearing 19 of the second planetary carrier 6 .
  • the first sun gear shaft 3 has a toothing that acts as a sun gearing, which meshes with, in particular three, first planetary gears 24, each of the first 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 mesh with a first ring gear 1 .
  • the first ring gear 1 has internal teeth which mesh with the teeth of the planet gears 24 .
  • the internal toothing of the first 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 first ring gear 1 and this externally toothed area thus meshes with the internal toothing of the first ring gear 1 is bringable.
  • the first 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 covers an area in the axial direction which is encompassed by the area covered by the first sun gear shaft 3 in the axial direction.
  • the support ring 2 is arranged on the side of the first planet gears 24 facing the second 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 first 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 first planet gear 24 and the second sun gear shaft 15 .
  • the first planet carrier 25 is rotatably mounted via the sleeve 27 in that the sleeve 27 is mounted on the housing part 10 via a bearing 20 on the one hand and on the housing part 10 via another bearing 20 together with the support ring 2 on the other.
  • the area covered by the sleeve 27 in the axial direction overlaps with the area covered by the first planet gears 24 in the axial direction and is encompassed by the area covered by the first 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 thus be refilled, in particular through the sleeve 27 .
  • 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 first ring gear.
  • the sleeve 27 acts as an axial extension of the first planet carrier 25 and surrounds the first 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 first planetary carrier 25, in particular in one piece.

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

Abstract

Est divulguée une transmission dotée d'un second étage d'engrenage planétaire qui comprend un second 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 insérée, les dents de l'engrenage planétaire s'engrenant avec les dents du second 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/EP2022/025338 2021-09-06 2022-07-20 Transmission dotée d'un second étage d'engrenage planétaire WO2023030677A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP22751646.5A EP4399423A1 (fr) 2021-09-06 2022-07-20 Transmission dotée d'un second étage d'engrenage planétaire

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN202111052923.8A CN115773337A (zh) 2021-09-06 2021-09-06 具有第二行星齿轮传动级的减速器
CN202111052923.8 2021-09-06
DE102021005347 2021-10-27
DE102021005347.8 2021-10-27

Publications (1)

Publication Number Publication Date
WO2023030677A1 true WO2023030677A1 (fr) 2023-03-09

Family

ID=82846306

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2022/025338 WO2023030677A1 (fr) 2021-09-06 2022-07-20 Transmission dotée d'un second étage d'engrenage planétaire

Country Status (3)

Country Link
EP (1) EP4399423A1 (fr)
DE (1) DE102022002657A1 (fr)
WO (1) WO2023030677A1 (fr)

Citations (10)

* 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
DE1430245A1 (de) 1961-05-19 1968-11-07 Rockwell Standard Co Achsaussenende mit Planetengetriebe
DE1904831A1 (de) 1968-02-15 1969-09-04 Malmsvets Ab Stufengetriebe,insbesondere fuer den Einbau in die Nabe eines Fahrzeugantriebsrades mit einem eigenen Antriebsmotor
DE2601454A1 (de) 1975-02-14 1976-09-09 Magyar Vagon Es Gepgyar Achsantrieb, insbesondere fuer landfahrzeuge
DE2831458A1 (de) 1978-07-18 1980-01-31 Zahnradfabrik Friedrichshafen Radantrieb fuer hydrostatisch angetriebene arbeitsmaschinen, insbesondere fuer kettenfahrzeuge
DE3245226A1 (de) 1982-12-07 1984-06-07 Liebherr-Werk Biberach Gmbh, 7950 Biberach Lagerung fuer kettenantriebsraeder von raupenketten
US5024636A (en) 1989-06-27 1991-06-18 Fairfield Manufacturing Company, Inc. Planetary wheel hub
DE19922651A1 (de) 1999-05-18 2000-11-23 Zahnradfabrik Friedrichshafen Radantrieb für ein Mobilfahrzeug
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 (10)

* 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
DE1430245A1 (de) 1961-05-19 1968-11-07 Rockwell Standard Co Achsaussenende mit Planetengetriebe
DE1904831A1 (de) 1968-02-15 1969-09-04 Malmsvets Ab Stufengetriebe,insbesondere fuer den Einbau in die Nabe eines Fahrzeugantriebsrades mit einem eigenen Antriebsmotor
DE2601454A1 (de) 1975-02-14 1976-09-09 Magyar Vagon Es Gepgyar Achsantrieb, insbesondere fuer landfahrzeuge
DE2831458A1 (de) 1978-07-18 1980-01-31 Zahnradfabrik Friedrichshafen Radantrieb fuer hydrostatisch angetriebene arbeitsmaschinen, insbesondere fuer kettenfahrzeuge
DE3245226A1 (de) 1982-12-07 1984-06-07 Liebherr-Werk Biberach Gmbh, 7950 Biberach Lagerung fuer kettenantriebsraeder von raupenketten
US5024636A (en) 1989-06-27 1991-06-18 Fairfield Manufacturing Company, Inc. Planetary wheel hub
DE19922651A1 (de) 1999-05-18 2000-11-23 Zahnradfabrik Friedrichshafen Radantrieb für ein Mobilfahrzeug
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

Also Published As

Publication number Publication date
DE102022002657A1 (de) 2023-03-09
EP4399423A1 (fr) 2024-07-17

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