EP2926030A1 - Unité de transmission dotée d'un train planétaire positif - Google Patents

Unité de transmission dotée d'un train planétaire positif

Info

Publication number
EP2926030A1
EP2926030A1 EP13774434.8A EP13774434A EP2926030A1 EP 2926030 A1 EP2926030 A1 EP 2926030A1 EP 13774434 A EP13774434 A EP 13774434A EP 2926030 A1 EP2926030 A1 EP 2926030A1
Authority
EP
European Patent Office
Prior art keywords
gear
planetary
planetary stage
stage
carrier
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Withdrawn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
EP13774434.8A
Other languages
German (de)
English (en)
Inventor
Stefan Beck
Uemit KUTLUAY
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.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
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 ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of EP2926030A1 publication Critical patent/EP2926030A1/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Withdrawn legal-status Critical Current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
    • F16H1/46—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
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D15/00—Transmission of mechanical power
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D15/00—Transmission of mechanical power
    • F03D15/10—Transmission of mechanical power using gearing not limited to rotary motion, e.g. with oscillating or reciprocating members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/40—Transmission of power
    • F05B2260/403—Transmission of power through the shape of the drive components
    • F05B2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
    • F05B2260/40311—Transmission of power through the shape of the drive components as in toothed gearing of the epicyclic, planetary or differential type
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • the present invention relates to a transmission unit according to the closer defined in the preamble of claim 1. Art.
  • gearbox for the conversion of torque and speed between transmission input and output shaft application.
  • an applied at the transmission input shaft high torque is converted at low speed in a voltage applied to the transmission output shaft reduced torque at a higher speed.
  • these transmissions can be divided into types of transmissions which have either planetary stages connected in series or planetary stages connected in parallel.
  • differential gear which usually consists of three planetary stages.
  • Such a transmission for wind turbines consists of a drive-side symmetrically constructed planetary stage, which is followed by at least one gear stage, wherein the planetary stage consists of at least two equal-sized parallel-connected power-splitter planetary gears.
  • the power-splitting planetary gears are followed by a load-compensating differential gear stage.
  • the differential gear stage is designed as a passive differential in the form of a compensating planetary gear. It performs a uniform power split on the two connected sun shafts of the planetary gears existing planetary stages.
  • the differential gear stage is designed as an active differential in the form of an axially soft mounted and opposite helical Ausretesstirnradcruung. This leads on the one hand a uniform power split at the two connected sun waves the planetary gears existing planetary stages and on the other hand involved as a gear on the overall ratio of the transmission.
  • the one sun shaft here is in operative connection with one balancing spur wheel of the balancing spur wheel pairing and the other sun shaft with its other balancing spur gear.
  • the first planetary stage is arranged on the drive side.
  • the third planetary stage is arranged on the output side.
  • the second planetary stage is formed in the longitudinal direction of the gear unit between the first and the third planetary stage.
  • the three planetary stages are coupled to one another in such a way that a drive-side torque can be split to the first and second planetary stage and can be brought together in the third planetary stage.
  • the gear unit can thus be made compact even for very high torques, since the drive-side torque is divided by the preferably parallel connection of the first and second planetary stage, so that the first and second planetary stage can be designed for lower loads, thereby reducing the dimensions of these can be. As a result, the transmission unit can be made very compact and space-saving.
  • a higher torque can be implemented on the output side compared to the drive side, whereby the efficiency of the designated wind turbine can be improved.
  • the first or the second planetary stage is coupled to a ring gear of the third planetary stage.
  • the other planetary stage is coupled to at least one planetary gear or planet carrier third planetary stage.
  • the planetary gears are rotatably mounted in a carrier, with which in turn one of the two first planetary stages is coupled such that the planetary stage, the carrier and the planetary gears are able to rotate as a unit in the circumferential direction of the transmission unit.
  • the ring gear of the third planetary stage and the planet carrier of the third planetary stage of each one the two first planetary stages are driven so that they are movable in the circumferential direction of the gear unit.
  • the ring gear and the planet carrier of the third planetary stage is coupled with the two other planetary stages such that the ring gear and the planet carrier move in opposite directions in the circumferential direction of the planetary stage.
  • One of the three planetary stages is designed as plus planetary gear.
  • a planetary stage is understood, which has a central sun gear, a first set planetary gears, which comprises at least one planetary gear, said planetary gear meshes with the sun gear and meshes with at least one further second planetary gear from a second set of planetary gears.
  • the second planet gear meshes in a ring gear, wherein the ring gear at least partially surrounds the planetary stage.
  • the planet gears are rotatably mounted on a planet carrier, so that the axes of rotation of the planet gears can be moved around the sun gear.
  • a Plusplanetendevelopment moves in a fixed planet carrier the ring gear and the sun gear in different directions.
  • a very simple and space-saving coupling of the three planetary stages can be implemented.
  • identical components of two adjacent planetary stages, in particular the ring gears can be operated in the same way, i. fixed or rotating about the longitudinal axis of the gear unit, be formed. This therefore allows a constructive simplification of the transmission unit and a reduction of the technical failure risk combined with the advantages of compact design and high translation options.
  • the plus planetary stage has a radially inner first planet wheel meshing with the sun gear of the planetary stage and a radially outer planet wheel meshing with the ring gear of the planetary stage. These are coupled together so that they are able to rotate about their respective axis of rotation to each other in opposite directions.
  • the direction of rotation of the ring gear or the sun gear can thus be reversed compared to an ordinary planetary gear.
  • This can be implemented in the present case with structurally simple means.
  • the three planetary stages of the be coupled with each other, that the gear unit can be very space-saving and structurally simple design. As a result, the manufacturing cost of the gear unit and their risk of failure are significantly reduced.
  • the two gears can be structurally easily coupled to each other, if they are aligned with each other in the radial direction of the gear unit and / or intermeshed.
  • the two gears are held together by means of a gear carrier in the radial direction of the gear unit.
  • the gear carrier therefore takes the planetary gears rotatably mounted on such that the planet gears in the circumferential direction of the gear unit guided by the planet carrier are able to move as a unit.
  • the radially inner first planetary gear and the sun gear meshing therewith rotate about its respective axis of rotation in opposite directions. In this way, a very compact and structurally simple implementation of the torque-dividing gear unit can be realized.
  • a very compact and space-saving coupling of the three planetary stages can be ensured if the planet carrier is designed to be rotatable about the sun gear.
  • the planet carrier can also be designed to be stationary.
  • the above-mentioned advantages come in particular when the plus planetary set is formed with the fixed planet carrier in the first planetary stage.
  • the gear unit can be produced very inexpensively if at least two adjacent planetary stages have a common overall carrier.
  • the total carrier here includes the planet carrier of two adjacent planetary stages.
  • the total carrier couples these rotatably together.
  • the transmission unit can be formed by means of the overall carrier in particular when the positive gear set is formed with the planet carrier in the first or second planetary stage.
  • the overall carrier is preferably in one piece in frame produced by a casting process. As a result, the manufacturing cost of the transmission unit can be reduced.
  • the total carrier may also be designed in several parts, with the individual planet carriers preferably each forming part of the overall carrier.
  • the planet carrier can be non-positively, material and / or positively connected to each other.
  • these are preferably connected to each other by means of fastening means, in particular screws, bolts and / or rivets.
  • fastening means in particular screws, bolts and / or rivets.
  • the risk of failure of the gear unit can be reduced if the total carrier is rotatably coupled to a drive shaft or the drive side is at least partially designed as such. Due to the thus rotatable design of the overall carrier, the ring gears of the planetary stages can be designed to be fixed, whereby expensive, structurally complex and error-prone bearings of the ring gears can be avoided.
  • the two ring gears of the first and second planetary stage, in particular formed at a trained as a positive gear set second planetary gear stage are fixed.
  • the stationary ring gears preferably form at least part of a housing of the gear unit.
  • the ring gears of the first, second and third planetary stage in particular in a designed as a positive gear set, first planetary stage, wherein the ring gears of the first and second planetary stage form a unit.
  • the design complexity of the transmission unit can be reduced.
  • the gear unit can be made very compact, if the sun gear of the second planetary stage is formed as a hollow shaft, in which extends the sunwheel of the first planetary gear designed as a solid shaft at least partially. Trained as a solid shaft sun gear of the first planetary stage can alternatively also as Hollow shaft be formed. Such a hollow shaft can also be used to pass electrical lines through.
  • the third planetary stage is coupled to the sun gears of the two other planetary stages, since this can reduce the geometric dimensions of the transmission unit.
  • the sun gear of the first planetary stage is preferably coupled to the planet carrier of the third planetary stage.
  • the sun gear of the second planetary stage with the ring gear of the third planetary stage is rotatably coupled.
  • the third planetary stage is designed as a positive gear set, preferably the sun gear of the first planetary gear is rotatably coupled to the ring gear of the third planetary gear and the sun gear of the second planetary gear to the planet carrier of the third planetary gear.
  • Fig. 1 a schematic half-view of a transmission unit with a designed as a positive gear set second planetary stage
  • Fig. 2 is a schematic half-view of a transmission unit with a trained as a positive gear set first planetary stage and
  • Fig. 3 is a schematic half-view of a transmission unit with a trained as a positive gear set third planetary stage.
  • FIG. 1 shows a gear unit 1 in a schematic half-view.
  • the transmission unit 1 comprises a first planetary stage 2, which is arranged on the drive side in the transmission unit 1.
  • the transmission unit 1 On the output side, the transmission unit 1 has a third planetary stage 4.
  • a second planetary stage 3 is arranged between the first planetary stage 2 and the third planetary stage 4.
  • the three planetary stages 2, 3, 4 are coupled to each other such that a drive-side Torque on the first and second planetary stage 2, 3 is divided.
  • the transmission unit 1 advantageously be made very compact, since the first and second planetary stage 2, 3 each have to withstand a lower torque.
  • the divided on the first and second planetary stage 2, 3 torque is again combined in the output-side region of the transmission unit 1 in the third planetary stage 4.
  • All planetary stages 2, 3, 4, each have a central sun gear 5, 6, 7, a surrounding this ring gear 8, 9, 10 and arranged radially between them planetary gears 1 1 on.
  • the planet gears 1 1 of the first and third planetary stage 2, 4 are each rotatably supported in a planet carrier 12, 13. They rotate accordingly through the planet carrier 12, 13 guided in the circumferential direction of the gear unit 1 to the respective sun gear 5, 7th
  • the second planetary stage 3 is designed as a positive planetary stage.
  • the second planetary stage 3 has a radially inner first planetary gear 15 and a radially outer second planetary gear 16.
  • the radially inner first planetary gear 15 meshes with the sun gear 6 of the second planetary stage 3.
  • the radially outer second planet gear 1 6 is in contrast arranged in the region between the sun gear 6 and the ring gear 9 by means of a planet carrier 18 so that it combs in a radially outer region with the ring gear 9 of the second planetary stage 3.
  • the two planetary gears 15, 16 are coupled with each other in such a way that they always rotate in opposite directions about their respective axis of rotation. For this purpose, they are interlinked in a region 17.
  • the two planetary gears 15, 16 are rotatably supported relative to each other and in the region between the sun gear 6 and the ring gear 9 by means of a planet carrier 18 and guided in the circumferential direction of the gear unit 1.
  • the two planet gears 15, 16 are therefore rotatably formed by the planetary carrier 18 as a unit around the sun gear 6.
  • the first planet carrier 12 of the first planetary stage 2 and the planet carrier 18 of the second planetary stage 3 are formed as a total carrier 19.
  • the transmission unit 1 on the drive side a drive shaft 20, by means of which a high torque at a relatively low speed is introduced into the transmission unit 1.
  • the drive shaft 20 is coupled to the first planet carrier 12 of the first planetary stage 2.
  • the high torque of the drive shaft 20 is thus divided into substantially equal parts, in particular in a division 60:40 on the first and second planetary stage 2, 3 of the transmission unit 1.
  • the two ring gears 8, 9 of the first and second planetary stage 2, 3 are each formed stationary. For this purpose, they are coupled to a housing, not shown in Figure 1, of the transmission unit 1 or at least form part of this housing.
  • the transmission unit 1 can be implemented in a space-saving, structurally simple and cost-effective manner, since expensive and expensive bearings of the ring gears 8, 9 are omitted.
  • the planetary gears 1 1 of the first planetary stage 2 rotated by the first planetary carrier 12 roll in the first ring gear 8 such that the first sun gear 5 of the first planetary stage 2 is set in rotation.
  • the direction of rotation of the first sun gear 5 corresponds to the direction of rotation of the drive shaft 20 and the first planet carrier 12.
  • the radially outer second planetary 1 6 of the second planetary stage 3 rolls in the stationary second ring gear 9 such that the radially inner first planetary 15 is offset due to the coupling in the region 17 in a comparison with the radially outer second planet gear 1 6 in an opposite rotation.
  • the second sun gear 6 Since the radially inner first planet gear 15 is meshed with the second sun gear 6 of the second planetary gear stage 3, the second sun gear 6 is set in rotation. Due to the positive gear set, however, as described above, a direction of rotation reversal, so that the second sun gear 6 in a compared to the first Son nenrad 5 opposite direction rotates. This is due in particular to the fact that the second sun gear 6 and the radially inner first planet gear 15 engaging therewith rotate in opposite directions with respect to their respective axis of rotation.
  • the second sun gear 6 of the second planetary stage 3 is formed as a hollow shaft 21.
  • the first sun gear 5 is formed in the present embodiment as a solid shaft 22 which extends through the hollow shaft 21 of the second planetary stage 3 therethrough.
  • the hollow shaft 21 is coupled on the output side with the third ring gear 10 of the third planetary stage 4 rotatably.
  • the third planet carrier 13 and the third ring gear 10 of the third planetary stage 4 rotate due to the reversal of direction by means of at least one plus gear set 14 in the second planetary stage 3 circumferentially in opposite directions.
  • the rotational speed of the planet gears 1 1 of the third planetary stage 4 is greatly increased compared to the rotational speed of the drive shaft 20.
  • the divided on the first and second planetary stage 2, 3 torque is thus brought together in the third sun gear 7 of the third planetary stage 4, that coupled to the third sun gear 7 output shaft 23 is operated with an increased compared to the drive shaft 20 speed.
  • the above-described first coupling variant of the three planetary stages 2, 3, 4 in conjunction with the direction of rotation reversal caused by the at least one positive gear set 14 has the significant advantages that the gear unit 1 can be made very compact and inexpensive. Furthermore, it is less susceptible to errors, as can be saved by the two fixed ring gears 8, 9 of the first and second planetary stage 2, 3 consuming and error-prone storage.
  • FIG. 2 shows an alternative embodiment of the transmission unit 1, in which the positive gear set 14 is formed in the first planetary stage 2.
  • the third planetary stage 4 is identical in construction to the first embodiment illustrated in FIG.
  • the overall carrier 19 formed between the first and second planetary stages 2, 3 is 19 fixed formed.
  • the planetary gears 1 1 and the radially inner first and radially outer second gears 15, 16 of the positive gear set 14 do not rotate about the longitudinal axis of the gear unit 1.
  • the two ring gears 8, 9 of the first and second planetary stage 2, 3 are rotatably formed.
  • first ring gear 8 is connected to the drive shaft 20, so that the two ring gears 8, 9 are offset by the drive-side torque in rotation.
  • the voltage applied to the drive shaft 20 torque is thus divided substantially equally to the two ring gears 8, 9 of the two first planetary stages 2, 3. Due to the fixed gear carrier 18 of the first planetary stage 2, the radially outer second gear 1 6 is rotated about its fixed by the rotatable mounting in the gear carrier 18 axis of rotation.
  • the positive gear set 14 may also be formed in the third planetary stage 4.
  • the first and second planetary stage 2, 3 is formed substantially as a conventional planetary gear.
  • the drive shaft 20 is coupled to the first planet carrier 12 of the first planetary stage 2.
  • the first ring gear 8 is fixed, so that the Planet wheels 1 1 of the first planetary stage 2 in the au llieri, fixed first ring gear 8 such that the stationary with the planet gears 1 1 in engagement first sun gear 5 is set in rotation, wherein the rotational direction of the first sun gear 5 of the rotational direction of the drive shaft 20 corresponds ,
  • the first planetary carrier 1 2 is rotatably coupled to the second ring gear 9 of the second planetary stage 3.
  • the second planet carrier 24 of the second planetary stage 3 is coupled to the housing, not shown here, such that the second planet carrier 24 is stationary.
  • the outer second ring gear 9 displaces the planet gears 11 of the second planetary stage 3 in such a manner that the inner second sun gear 6 of the second planetary stage 3 is rotated in a direction opposite to the first sun gear 5.
  • the first sun gear 5 of the first planetary stage 2 is rotatably coupled to the third ring gear 1 0 of the third planetary stage 4.
  • the second sun gear 6 of the second planetary stage 3 is rotatably coupled to the gear carrier 1 8 of the third planetary stage 4.
  • the third ring gear 1 0 and the gear carrier 1 8 of the third planetary stage 4 is rotated in the circumferential direction of the transmission unit 1 in opposite directions.
  • the toothed wheels 1 5, 1 6 meshed with one another in the region 1 7 are set in mutually opposite rotation.
  • the radially inner first gear 15 drives the third sun gear 7 in such a way that the output shaft 23 coupled therewith, the drive shaft 20 and the first sun gear 5 or the solid shaft 22 rotate in the same direction.
  • the total carrier 1 9 may be integrally formed in one piece or in a non-illustrated embodiment in the embodiment of several parts.
  • the gear carrier 1 8 and the first planetary carrier 1 2 of the first planetary stage 2 each form a part of the total carrier 1 9.
  • force and / or materially connected In a connection region of the gear carrier 1 8 with the first planet carrier 1 2 form, force and / or materially connected.
  • fastening means in particular screws, bolts and / or rivets

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Retarders (AREA)

Abstract

La présente invention concerne une unité de transmission (1), notamment pour éolienne, comprenant un premier étage planétaire (2) côté entrée, une deuxième étage planétaire (3) et un troisième étage planétaire (4) côté sortie, qui sont accouplés de telle façon qu'un couple de rotation côté entrée puisse se répartir entre le premier et le deuxième étage planétaire (2; 3) et puisse être réuni dans le troisième étage planétaire (4), le premier ou le deuxième étage planétaire (2 ; 3) étant accouplé à une couronne (10) du troisième étage planétaire (4) et l'autre étage planétaire (2; 3) étant accouplé à au moins un satellite (11) du troisième étage planétaire (4). Selon l'invention, l'un des étages planétaires (2; 3; 4) présente, dans la zone comprise entre leur pignon planétaire (5; 6; 7) central et la couronne (8; 9; 10) située radialement à l'extérieur, un train planétaire positif (14) qui permet d'inverser le sens de rotation du pignon planétaire (5; 6; 7) ou de la couronne (8; 9; 10).
EP13774434.8A 2012-11-29 2013-10-11 Unité de transmission dotée d'un train planétaire positif Withdrawn EP2926030A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012221825.4A DE102012221825A1 (de) 2012-11-29 2012-11-29 Getriebeeinheit mit Plusgetriebesatz
PCT/EP2013/071228 WO2014082782A1 (fr) 2012-11-29 2013-10-11 Unité de transmission dotée d'un train planétaire positif

Publications (1)

Publication Number Publication Date
EP2926030A1 true EP2926030A1 (fr) 2015-10-07

Family

ID=49326681

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13774434.8A Withdrawn EP2926030A1 (fr) 2012-11-29 2013-10-11 Unité de transmission dotée d'un train planétaire positif

Country Status (5)

Country Link
EP (1) EP2926030A1 (fr)
JP (1) JP2015535581A (fr)
CN (1) CN104755803B (fr)
DE (1) DE102012221825A1 (fr)
WO (1) WO2014082782A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104791432A (zh) * 2014-09-15 2015-07-22 周献生 直线可无级换挡的变速器
EP3587863A1 (fr) * 2018-06-25 2020-01-01 Flender GmbH Engrenage planétaire, chaîne cinématique, éolienne et application industrielle
EP3599394A1 (fr) * 2018-07-23 2020-01-29 Flender GmbH Engrenage couplé pour éoliennes et applications industrielles
EP3599391A1 (fr) * 2018-07-23 2020-01-29 Flender GmbH Engrenage couplé pour éoliennes et applications industrielles
EP3599393A1 (fr) * 2018-07-23 2020-01-29 Flender GmbH Engrenage couplé pour éoliennes et applications industrielles

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DE7805045U1 (de) * 1978-02-20 1978-06-22 A. Friedr. Flender Gmbh & Co Kg, 4290 Bocholt Zweistufiges Differentialdoppelplanetengetriebe
DE19963597A1 (de) 1999-12-23 2001-07-26 Mannesmann Ag Getriebe, insbesondere für Windkraftanlagen
KR100476223B1 (ko) * 2002-12-03 2005-03-10 현대자동차주식회사 차량용 자동변속기의 6속 파워 트레인
JP2009113519A (ja) * 2007-11-01 2009-05-28 Toyota Motor Corp 車両の動力伝達装置
FR2927394B1 (fr) * 2008-02-11 2010-06-04 Roucar Gear Technologies Bv Dispositif de transmission pour machine de production d'electricite a partir d'une source motrice a vitesse variable, unite de production electrique et eolienne ainsi equipees, et procede de reglage d'un rapport de transmission
DK2331813T3 (da) * 2008-09-10 2012-09-03 Timken Co Transmission til vindmølle
DE102008056622A1 (de) * 2008-11-10 2010-05-12 Volkswagen Ag Aktive Differentialanordnung für ein Kraftfahrzeug
JP5123904B2 (ja) * 2009-07-08 2013-01-23 本田技研工業株式会社 自動変速機

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Also Published As

Publication number Publication date
CN104755803A (zh) 2015-07-01
JP2015535581A (ja) 2015-12-14
CN104755803B (zh) 2017-08-04
WO2014082782A1 (fr) 2014-06-05
DE102012221825A1 (de) 2014-06-05

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