EP3259492A1 - Dispositif de transmission - Google Patents

Dispositif de transmission

Info

Publication number
EP3259492A1
EP3259492A1 EP16705031.9A EP16705031A EP3259492A1 EP 3259492 A1 EP3259492 A1 EP 3259492A1 EP 16705031 A EP16705031 A EP 16705031A EP 3259492 A1 EP3259492 A1 EP 3259492A1
Authority
EP
European Patent Office
Prior art keywords
planetary
drive
shafts
toothing
gears
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP16705031.9A
Other languages
German (de)
English (en)
Inventor
Burkhard Pinnekamp
Mohamed Sfar
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Renk GmbH
Original Assignee
Renk GmbH
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 Renk GmbH filed Critical Renk GmbH
Publication of EP3259492A1 publication Critical patent/EP3259492A1/fr
Withdrawn legal-status Critical Current

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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/2809—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels
    • F16H1/2836—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels by allowing limited movement of the planets relative to the planet carrier or by using free floating planets
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using 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
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
    • F16H1/22—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/18—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes the members having helical, herringbone, or like teeth
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H2003/442—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion comprising two or more sets of orbital gears arranged in a single plane

Definitions

  • the invention relates to a transmission arrangement.
  • the invention is based on the object to provide a novel gear arrangement.
  • the gear arrangement comprises a rotatably mounted, first drive-side shaft on which a first drive toothing is formed; a rotatably mounted, second drive-side shaft on which a second drive toothing is formed; a rotatably mounted, output-side shaft on which an output gear is formed; a first number of first planetary shafts, wherein on each of the first planetary shafts in each case a first planetary gearing and axially offset a third planetary gearing is formed; a second number of second planetary shafts, wherein on each of the second planetary shafts in each case a second planetary gearing and axially offset a fourth planetary gearing is formed; wherein the first drive-side shaft and the second drive-side shaft are coaxial with each other; the
  • CONFIRMATION COPY first planetary gears of the first planetary shafts are engaged with the first driving teeth, and the second planetary gears of the second planetary shafts are engaged with the second driving gears; and wherein the third planetary gears of the first planetary shafts and the fourth planetary gears of the second planetary shafts are engaged with the driven teeth.
  • the first and second drive toothing held ready on the different drive shafts and the first and second planetary toothing held ready on the different planetary shafts are each designed as helical toothings with opposite helix angles.
  • the first number of first planetary shafts and the second number of first planetary shafts are each greater than two; wherein, viewed in the circumferential direction, the first planetary gears and the second planetary gears are distributed uniformly such that in each case a second planetary gear teeth is positioned between each two adjacent first planetary gears; and wherein, viewed in the axial direction, the first planetary gears and the second planetary gears as well as the first drive gear and the second drive gear are offset from one another.
  • This design allows a particularly advantageous transmission of the drive torque provided by two drive-side shafts in the direction of a common output-side shaft.
  • a transmission arrangement according to claim 5 is proposed.
  • the gear arrangement comprises a rotatably mounted, first drive-side shaft on which a first drive toothing is formed; a rotatably mounted, second drive-side shaft on which a second drive toothing is formed; a rotatably mounted, output-side shaft on which an output gear is formed; Planetary waves, wherein on each of the planetary shafts in each case a first planetary gearing, axially offset a second planetary gearing and in turn axially replaced a third planetary gearing is formed; wherein the first drive-side shaft and the second drive-side shaft are coaxial with each other; and wherein the first planetary gears of the planet shafts are engaged with the first drive teeth, the second planetary gears of the planet shafts with the second drive teeth, and the third planetary gears of the planet shafts engage with the driven teeth.
  • a drive power provided on two drive-side shafts can advantageously be transmitted in the direction of
  • the first and second drive toothings provided on the different drive shafts and the first and third planetary toothings held ready on the same planetary shafts are in each case designed as helical toothings with opposite, preferably equally large, helix angles.
  • the number of planetary shafts is greater than three; wherein, seen in the circumferential direction, the planetary gears are equally distributed; and wherein, viewed in the axial direction, the first planetary gears and the second planetary gears as well as the first drive gear and the second drive gear are offset from one another.
  • axial bearing surfaces between the first and second drive toothings of the helical toothing of the same resulting axial forces from, and / or the first and second drive toothings are coupled via axial force transmitting elements .
  • This embodiment of the gear arrangement allows a particularly advantageous transmission of the drive power provided on two drive-side shafts in the direction of a common output-side shaft.
  • FIG. 1 shows a schematic axial section of a first gear arrangement according to the invention
  • FIG. 2 is a schematic, perspective view of a driven side
  • FIG. 3 shows a schematic axial section of a second invention
  • the invention relates to a transmission arrangement.
  • Figs. 1 and 2 show details of a preferred embodiment of a transmission assembly 10 according to a first aspect of the present invention.
  • the gear arrangement 10 comprises two rotatably mounted, drive-side shafts, namely a rotatably mounted, first drive-side shaft 11 and a rotatably mounted, second drive-side shaft 12.
  • the two drive-side shafts 11, 12 extend coaxially to each other, wherein in the illustrated embodiment, the first drive-side shaft 11th the second drive-side shaft 12 radially outwardly partially surrounds.
  • a first drive toothing 13 is formed, which is provided in the embodiment shown by a gear.
  • On the second drive-side shaft 12, a second drive toothing 14 is formed, which is also provided by a gear.
  • the gear arrangement 10 comprises a rotatably mounted, drive-side shaft 15 with a Antriebsveriereurig 16, which is provided by a gear.
  • the gear arrangement 10 further has a first number of first rotatably mounted planetary shafts 17 and a second number of second rotatably mounted planetary shafts 18.
  • a second planetary toothing 20 and axially spaced fourth planetary toothing 22 is formed in each case, again in the form of gears.
  • the first planetary gears 19 of the first planetary shafts 17 are engaged with the first driving teeth 13 of the first driving-side shaft 11.
  • the second planetary gears 20 of the second planetary shafts 18 are engaged with the second drive gears 14 of the second drive-side shaft 12.
  • the third planetary gears 21 of the first planetary shaft 17 and the fourth planetary gears 22 of the second planetary shaft 18 are respectively in engagement with the output gear 16 of the output-side shaft 15.
  • the two drive teeth 13, 14 of the two drive-side shafts 11, 12 are offset from each other in the axial direction.
  • the first planetary gears 19 of the first planetary shafts 17 and the second planetary gears 20 of the second planetary shafts 18 are offset from each other in the axial direction.
  • first planetary gears 19 of the first planetary shafts 17 are arranged together with the first drive teeth 13 of the first drive-side shaft 11 in a first plane, wherein the second planetary gears 20 of the second planetary shafts 18 together with the second drive teeth 14 of the second drive-side shaft 12 in a thereto axially offset second level are arranged.
  • the third planetary gears 21 of the first planetary shafts 17 and the fourth planetary gears 22 of the second planetary shafts 18 are positioned together with the output teeth 16 of the driven-side shaft 15 in a third plane which in turn is positioned to the two planes in which the drive gears 13, 14 are positioned. axially offset.
  • the number of the first planetary shafts 17 and the number of the second planetary shafts 18 are each greater than or equal to 2, more preferably the first number of the first planetary shafts 17 corresponds to the second number of the second planetary shafts 18.
  • the first planetary gears 19 and the second planetary gears 20 are the same as the third planetary gears 21 and the fourth planetary gears 22, equally distributed in the circumferential direction, namely such that between each two adjacent first planetary gears 19 each have a second planetary toothing 20 and between each two adjacent third Planetary gears 21 each have a fourth planetary toothing 22 is positioned.
  • drive power is accordingly provided on two drive-side shafts 11 and 12 running coaxially with one another.
  • gears are rotatably mounted, which provide the drive gears 13 and 14. This can be done via angle-compensating couplings, such as curved tooth couplings.
  • the drive gears 13, 14 are formed as well as the first and second planetary gears 19 and 20 cooperating with them as Schrägver- toothing each with opposite helix angle, wherein the amount of the opposite helix angle is preferably the same size.
  • first planetary gears 19 of the first planetary shafts 17 cooperate, whereas the second planetary gears 20 of the second planetary shafts 18 cooperate with the second drive teeth 14 of the second drive-side shaft 12.
  • the first and second planetary gears 19, 20 are preferably provided by gears, which are rotatably attached to the respective planetary shafts 17, 18.
  • the third and fourth planetary gears 21, 22 of the first and second planetary shafts 17, 18 are also preferably provided by gears, which in turn are rotatably connected to the respective planetary shaft.
  • the third and fourth planetary gears 21, 22 of the first and second planetary shafts 17, 18, which cooperate with the driven teeth 16 of the driven-side shaft 15 or mesh in this, are preferably helically toothed.
  • the third planetary toothing 21 preferably has the same helix angle as the fourth planetary toothing 22.
  • a second transmission arrangement 30 according to the invention which serves to transmit drive power provided on two drive-side shafts in the direction of a common output-side shaft, is shown in FIGS. 3 and 4.
  • FIG. 3 in turn shows two coaxial with each other, drive-side shafts 31 and 32, wherein each of these two drive-side shafts 31 and 32, a drive teeth 33 and 34 is assigned, which is preferably provided by a respective gear which at one end of the respective drive-side shaft 31 and 32 is rotatably connected to the same.
  • the transmission arrangement 30 of FIGS. 3 and 4 furthermore has an output-side shaft 35 with a driven toothing 36, which in turn is provided by a toothed wheel which is connected in a rotationally fixed manner to the output-side shaft 35.
  • the planetary gear 30 of FIGS. 3 and 4 has a plurality of planetary shafts 37.
  • Each of the planetary shafts 37 has a total of three planetary gears, namely a first planetary gear 38, offset axially thereto a second planetary gearing 39 and in turn axially offset thereto via a third planetary gearing 40.
  • the first planetary gearing 38 of the planetary shafts 37 mesh with the first drive gearing 33 of the first drive-side shaft 31 and are positioned with the same in a first plane.
  • the second planetary gears 39 of the planetary shafts 37 mesh with the second driving teeth 34 of the second driving-side shaft 32 and are positioned therewith in a second plane offset axially of the first plane.
  • the third planetary gears 40 of the planetary shafts 37 mesh with the output teeth 36 of the common output side shaft 35, the third planetary gears 40 are disposed together with the output teeth 36 in a third plane which are axially offset to the first and second planes.
  • three planetary shafts 37 are provided, each having a first planetary toothing 38, in each case a second planetary toothing 39 and in each case a third planetary toothing 40, the planetary toothings 38, 39 and 40 being distributed identically in the circumferential direction.
  • the planetary gears 38, 39 and 40 are provided by gears which are rotatably connected to the respective planetary shaft 37.
  • the first and second planetary gear teeth 38, 39 of the planetary shafts 37 are each helically opposing helical.
  • the planetary shafts 37 are preferably freely movable in the axial direction in order to allow an axial load balance between the drive teeth 33, 34.
  • the third planetary gears 40 are preferably straight teeth, as well as the output gear 36th
  • axial forces F which can act on the drive teeth 3, 14 during operation and which result from the helical toothings of the drive toothings 13, 14 are preferably provided by axial bearing surfaces 50 to support the drive teeth 13, 40. In the prevailing torque direction, these axial forces are endeavored, as shown in FIGS. 1 and 3, to move the drive gears 13, 14 and 33, 34 towards each other.
  • the desired distribution of torques is effected by the balance of the axial forces on the drive teeth, wherein the ratio of the radial forces is determined by the helix angle of these teeth. At the same axial forces and the same helix angles result in the same circumferential forces or radial forces.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Gear Transmission (AREA)
  • Transmission Devices (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
  • Power Steering Mechanism (AREA)

Abstract

L'invention concerne un dispositif de transmission (10), présentant un premier arbre (11) côté entrée, logé de manière rotative, auquel est associée une première denture (13) d'entraînement, un deuxième arbre (12) côté entrée, logé de manière rotative, auquel est associée une deuxième denture (14) d'entraînement, un arbre (15) côté sortie, logé de manière rotative, auquel est associé une denture (16) de sortie, un premier nombre de premiers arbres (17) planétaires, une première denture (19) planétaire et une troisième denture (21) planétaire, axialement décalée, étant à chaque fois associées à chacun des premiers arbres (17) planétaires, un deuxième nombre de deuxièmes arbres (18) planétaires, une deuxième denture (20) planétaire et une quatrième denture (22) planétaire axialement décalée étant à chaque fois associées à chacun des deuxièmes arbres (18) planétaires, le premier arbre (11) côté entrée et le deuxième arbre (12) côté entrée s'étendant de manière coaxiale l'un par rapport à l'autre, les premières dentures (19) planétaires des premiers arbres (17) planétaires étant en contact avec la première denture (13) d'entraînement et les deuxièmes dentures (20) planétaires des deuxièmes arbres (18) planétaires étant en contact avec la deuxième denture (14) d'entraînement, les troisièmes dentures (21) planétaires des premiers arbres (17) planétaires et les quatrièmes dentures (22) planétaires des deuxièmes arbres (18) planétaires étant en contact avec la denture (16) de sortie.
EP16705031.9A 2015-02-17 2016-02-08 Dispositif de transmission Withdrawn EP3259492A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015002029.3A DE102015002029A1 (de) 2015-02-17 2015-02-17 Getriebeanordnung
PCT/EP2016/000202 WO2016131529A1 (fr) 2015-02-17 2016-02-08 Dispositif de transmission

Publications (1)

Publication Number Publication Date
EP3259492A1 true EP3259492A1 (fr) 2017-12-27

Family

ID=55398247

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16705031.9A Withdrawn EP3259492A1 (fr) 2015-02-17 2016-02-08 Dispositif de transmission

Country Status (7)

Country Link
US (1) US10400860B2 (fr)
EP (1) EP3259492A1 (fr)
JP (1) JP6507265B2 (fr)
KR (1) KR102040385B1 (fr)
CN (1) CN107223188B (fr)
DE (1) DE102015002029A1 (fr)
WO (1) WO2016131529A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE1550263A1 (en) * 2015-03-04 2016-09-05 Swepart Trans Ab Gear train
EP3431812B1 (fr) * 2017-07-21 2020-11-11 Ge Avio S.r.l. Transmission pour répartir un couple de rotation entre deux roues dentées coaxiales
EP3431811B1 (fr) * 2017-07-21 2021-12-22 Ge Avio S.r.l. Dispositif de transmission pour la division d'un couple entre deux roues coaxiales, en particulier pour un engrenage planétaire pour des applications aéronautiques et procédé de fabrication et d'assemblage de ce dispositif de transmission

Family Cites Families (18)

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US1459964A (en) * 1919-04-05 1923-06-26 Alquist Karl Gearing
US1740756A (en) * 1926-10-26 1929-12-24 Deutsche Schiff & Maschb Ag Power-transmission gear
US2423820A (en) * 1942-08-18 1947-07-15 Vickers Electrical Co Ltd Transmission gearing for power plants
DE1206254B (de) * 1963-10-23 1965-12-02 Demag Ag Planetengetriebe mit zwei parallelen Umlauf-raedersaetzen
DE2029371A1 (de) 1969-06-19 1971-01-07 S koda, narodni podnik, Pilsen (Tschechoslowakei) Plantengetnebe mit doppelten Um laufradern
DE3423983A1 (de) * 1984-06-29 1986-01-16 A. Friedr. Flender Gmbh & Co Kg, 4290 Bocholt Mehrweggetriebe
US6334368B1 (en) * 2000-05-17 2002-01-01 Harrier Technologies, Inc. Multi-path gear sets with load sharing between paths
DE10036937A1 (de) * 2000-07-28 2002-02-07 Zf Lenksysteme Gmbh Spielfreies Planetengetriebe, insbesondere für eine Betätigungseinrichtung einer Fahrzeug-Lenkvorrichtung
JP4501356B2 (ja) * 2003-05-07 2010-07-14 住友金属工業株式会社 鉄道車両用歯車装置及び鉄道車両用台車
DE102005012226B3 (de) * 2005-03-15 2006-06-08 Linsinger-Maschinenbau Ges.M.B.H. Zahnradgetriebe
US7803085B2 (en) * 2007-07-19 2010-09-28 Hamilton Sundstrand Corporation Electrically driven parallel shaft transmission that maintains delivered power while shifting
GB0819233D0 (en) * 2008-10-20 2008-11-26 Zhou Changxiu Load distribution system
US8096917B2 (en) 2008-11-13 2012-01-17 General Electric Company Planetary gearbox having multiple sun pinions
ITBO20090465A1 (it) * 2009-07-21 2011-01-22 Ferrari Spa Trasmissione per un veicolo stradale con propulsione ibrida
US8733194B2 (en) * 2011-04-27 2014-05-27 Gm Global Technology Operations, Llc Dual clutch multi-speed transmission
US8888649B2 (en) * 2011-05-26 2014-11-18 Miva Engineering Ltd. Dynamic reduction-ratio hoisting device
DE102012013834A1 (de) * 2012-07-13 2014-01-16 Renk Ag Leistungsverzweigungsgetriebe
FR3034158B1 (fr) * 2015-03-27 2018-06-15 Safran Transmission Systems Reducteur de vitesse a deux lignes intermediaires de transmission

Also Published As

Publication number Publication date
CN107223188A (zh) 2017-09-29
DE102015002029A1 (de) 2016-08-18
US10400860B2 (en) 2019-09-03
KR20170118808A (ko) 2017-10-25
US20180023667A1 (en) 2018-01-25
JP6507265B2 (ja) 2019-04-24
CN107223188B (zh) 2019-10-15
WO2016131529A1 (fr) 2016-08-25
KR102040385B1 (ko) 2019-11-04
JP2018505367A (ja) 2018-02-22

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