US20040213671A1 - Drive assembly - Google Patents

Drive assembly Download PDF

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Publication number
US20040213671A1
US20040213671A1 US10/485,563 US48556304A US2004213671A1 US 20040213671 A1 US20040213671 A1 US 20040213671A1 US 48556304 A US48556304 A US 48556304A US 2004213671 A1 US2004213671 A1 US 2004213671A1
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US
United States
Prior art keywords
drive assembly
assembly according
ring
bearing
main bearing
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.)
Abandoned
Application number
US10/485,563
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English (en)
Inventor
Peter Flamang
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 Wind Power Antwerpen NV
Original Assignee
Hansen Transmissions International NV
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 Hansen Transmissions International NV filed Critical Hansen Transmissions International NV
Assigned to HANSEN TRANSMISSIONS INTERNATIONAL NV reassignment HANSEN TRANSMISSIONS INTERNATIONAL NV ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: FLAMANG, PETER
Publication of US20040213671A1 publication Critical patent/US20040213671A1/en
Abandoned legal-status Critical Current

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    • 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
    • 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
    • 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
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F03D80/70—Bearing or lubricating arrangements
    • 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
    • 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
    • F16H2001/289—Toothed gearings for conveying rotary motion with gears having orbital motion comprising two or more coaxial and identical sets of orbital gears, e.g. for distributing torque between the coaxial sets
    • 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

  • This invention relates to a drive assembly and to a gear transmission unit for a wind turbine.
  • the present invention seeks to provide an improved drive assembly and an improved gear transmission unit for a wind turbine and which permits an advantageous integration of components.
  • a drive assembly for a wind turbine comprises a rotor hub, supporting structure such as a turbine nacelle, a planetary type gear transmission unit comprising sun, planet and ring gears and a planet carrier, said ring gear being non-rotatably secured to said supporting structure, a main bearing which is a double taper bearing and rotatably supports the rotor hub relative to said ring gear and supporting structure, and said drive assembly comprising two substantially independent force transmission paths for transmission of forces reacting with forces exerted by the wind turbine rotor hub, a first of said force transmission paths acting from the rotor hub via said main bearing to the supporting structure primarily for transmission of overhang load forces and bending moment forces and a second of said force transmission paths acting from the rotor hub via said planet carrier primarily for transmission of rotational forces.
  • Said main bearing may also rotatably support the planet carrier relative to said ring gear and supporting structure.
  • Said double taper bearing may comprise a single outer bearing ring.
  • the rotor hub may be rigidly secured relative to said single outer bearing ring.
  • the double taper bearing may comprise rollers arranged in an ⁇ configuration in which the rollers of one series increase in diameter in a direction away from the rollers of the other series of the pair.
  • a gear transmission unit for use in a wind turbine to transmit forces from a rotor hub to a generator comprises a planetary type gear transmission unit comprising sun, planet and ring gears and a planet carrier, said ring gear being adapted for non-rotatably securing to supporting structure such as a turbine nacelle, and a main bearing of a double taper type as described herein.
  • the invention teaches that the overhung load forces and bending moments from the rotor are taken by a double taper bearing which is directly connected to stationary parts instead of to the torque transmitting low speed part of the gear unit.
  • said main bearing lies at a position substantially aligned axially with the axial position of at least the ring gear of the gear transmission unit.
  • the sun, planet and ring gears lie in a transverse plane (perpendicular to the rotation axis of said rotational forces) which also contains said main bearing.
  • the main bearing comprises an inner ring bearing surface of a diameter greater than that of the toothed surface of the ring gear, and that at all radial positions inwards of the toothed surface of the ring gear the second force transmission path is substantially independent of the first force transmission path.
  • the second of said force transmission paths comprises a radially extending torque transmission member which is torsionally stiff but relatively compliant in an axial direction parallel with the axis about which the rotational forces act whereby movement of the hub in consequence of bending forces is accommodated at least in part by deflection of the torque transmission member.
  • the torque transmission member thereby isolates the gear transmission unit from the potentially damaging effects of bending deflections experienced by the rotor hub relative to the main rotational axis of the gear transmission unit.
  • the present invention accordingly provides, in a further of its aspects, a drive assembly in which the main rotor bearing and gear transmission unit for a wind turbine are of an integrated construction.
  • the wind turbine rotor hub preferably is connected to the outer ring of the main bearing.
  • the bearing inner ring preferably is supported by, and may be directly mounted on, the ring gear of the planetary gear stage, or on a flange which connects the ring gear to the supporting structure.
  • the ring gear may provide a bearing surface for rotatable bearing components of the main bearing.
  • the ring gear may provide axial and radial locations for the main bearing.
  • the ring gear may have a radially outer surface of a stepped profile to define a shoulder for axial location of an inner bearing ring of the main bearing.
  • the inner bearing ring may be secured axially between said shoulder and said supporting structure.
  • the ring gear may be provided with a reinforcing ring, and said reinforcing ring may extend axially and or radially beyond the toothed surface of the ring gear. Said reinforcing ring may provide an axial location of the main bearing.
  • the present invention provides a wind turbine comprising rotors, a generator and a drive assembly of a type in accordance with the present invention.
  • the gear transmission unit e.g. a housing thereof, may be arranged to support an electrical generator.
  • FIG. 1 is an elevation view of a wind turbine having a drive assembly of the present invention
  • FIG. 2 is a sectional view of part of a gear transmission unit
  • FIG. 3 shows part of FIG. 2 in more detail
  • FIGS. 4, 5 and 6 each show variations of the construction of FIGS. 2 and 3;
  • FIG. 7 shows part of FIG. 6 in more detail
  • FIGS. 8 and 9 each show further variations of the construction of FIGS. 2 and 3.
  • a wind turbine 10 (see FIG. 1) comprises a gear transmission unit 11 which acts to transmit torque from rotor blades 12 and rotor hub 14 to an electrical generator 13 , the gear transmission unit comprising an epicyclic gear unit.
  • the gear transmission unit and generator are housed in and supported by a nacelle 15 .
  • the gear transmission unit 11 comprises an epicyclic gear unit having four planet gears 25 , a sun gear 27 a planet carrier 28 , and a ring gear 24 which is non-rotatably mounted relative to the nacelle structure 15 .
  • the sun gear is connected to an output shaft (not shown) which connects either to a further gear unit or direct to the rotor of the generator 13 .
  • the radially outer surface 29 of the ring gear 24 provides location and support for the inner ring 30 of a main bearing 23 .
  • the outer ring 31 of the main bearing has secured thereto the rotor hub 14 and, interposed between the rotor hub and ring 31 , the outer region 22 of the planet carrier 28 .
  • the planet carrier 28 comprises four bearing support studs 26 uniformly circumferentially spaced to locate bearings 32 which rotatably support the four planet gears 25 .
  • the planet carrier 28 has an annular region 33 which extends radially between the radial position of the bearing studs 26 and the outer region 22 and is designed to be relatively stiff, in a circumferential direction about the Y axis, for transmission of torque between the region 22 and the bearing studs 26 , but to be relatively flexible about the X and Z axis.
  • FIG. 4 shows a variation 40 in which the planet carrier 41 is provided with three integral and uniformly circumferentially spaced studs 42 which support a planet bogie plate 43 .
  • the planet bogie plate 43 provides support for three circumferentially uniformly spaced shafts 44 arranged each to self adjust in angular position on the plate 43 .
  • Each shaft 44 provides support, at opposite sides if the plate 43 , for a pair of bearings 45 , 46 about which each of a pair of planet gears 47 , 48 are rotatably mounted for engagement with the ring gear 49 .
  • the planet carrier 56 is of a cage type design.
  • each of three planet bearing support shafts 51 is supported at one axial end 52 by the part 53 of the planet carrier that extends radially outwards to be supported by the outer ring of the main bearing 54 whilst the other end 55 is supported by an auxiliary driving plate 57 carried by three circumferentially uniformly spaced supports 58 provided at positions interposed circumferentially between the shafts 51 .
  • the plate 57 is provided with a central aperture 59 to which an output shaft 60 extends from the sun gear 61 .
  • FIG. 6 shows an embodiment of the present invention and which is a further variation of the construction of FIGS. 2 and 3.
  • the planet carrier is constructed substantially similar to that described with reference to FIG. 5.
  • the ring gear 63 differs in so far as part of the outer periphery of the gear is surrounded by a reinforcing support ring 64 .
  • the reinforcing ring is either formed integrally, e.g. forge rolled, with the outer ring 63 or permanently secured thereto, for example by being a shrink fit thereon.
  • the presence of the support ring, provided axially at a position spaced from the nacelle structure 15 provides an abutment surface 65 for axial location of the inner ring of the main bearing 66 .
  • the main bearing 66 is a double taper type bearing, shown in more detail in FIG. 7.
  • the main bearing comprises an inner ring of a split construction comprising two taper rings 67 .
  • the bearing additionally comprises a single outer ring 68 of double taper
  • FIG. 8 A further variation of the construction of FIGS. 2 and 3 is shown in FIG. 8.
  • this construction 80 the inner ring of the main rotor bearing 81 contrasts with aforedescribed constructions in so far as it is not directly mounted on or supported by the ring gear 82 . Instead, the inner ring of the bearing 81 is supported by a flange assembly 83 secured to the nacelle structure 15 .
  • the bearing inner ring is connected substantially directly to the nacelle structure 15 at position 91 .
  • FIGS. 8 and 9 show that the inner ring of the main bearing is non-rotatably secured relative to the nacelle structure 15 , it is to be understood that the outer ring of the main bearing may be secured to the nacelle structure and that the rotor hub and planet carrier may be rotatably supported by the inner ring of the bearing.
  • the sun, planet and ring gears are all substantially aligned with one another as considered in an axial direction parallel with the axis of rotation of the planet carrier.
  • the main bearing comprises an inner ring bearing surface the diameter of which is greater than that of the toothed surface of the ring gear.
  • a benefit arising from the drive assembly, and the gear transmission unit of the present invention as used in a wind turbine is that the overhung loads generated by the wind turbine rotor blades have only a minimal effect on the planet driving components and on the gear meshing contact of the planetary gear stage. This allows for an increased power rating of the gear transmission unit or a reduction of dimension for a given power rating as compared with hitherto known constructions. It is also to be appreciated that the forces generated in gear meshing of the planets have only a minimal effect on the load distribution over the bearing rollers in the main bearing, thus increasing the load capacity of the main bearing or allowing for reduction of dimensions of that bearing for a given load capability.

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  • 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)
  • Wind Motors (AREA)
US10/485,563 2001-08-03 2002-08-01 Drive assembly Abandoned US20040213671A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB0118996.8 2001-08-03
GBGB0118996.8A GB0118996D0 (en) 2001-08-03 2001-08-03 Drive Assembly
PCT/IB2002/003672 WO2003014567A1 (fr) 2001-08-03 2002-08-01 Ensemble d'entrainement

Publications (1)

Publication Number Publication Date
US20040213671A1 true US20040213671A1 (en) 2004-10-28

Family

ID=9919776

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/485,563 Abandoned US20040213671A1 (en) 2001-08-03 2002-08-01 Drive assembly

Country Status (4)

Country Link
US (1) US20040213671A1 (fr)
EP (1) EP1423608A1 (fr)
GB (1) GB0118996D0 (fr)
WO (1) WO2003014567A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070142156A1 (en) * 2005-11-21 2007-06-21 Hansen Transmissions International, Naamloze Vennootschap Gearbox for a wind turbine
US20100244454A1 (en) * 2007-08-31 2010-09-30 Schaeffler Technologies Gmbh & Co., Kg Rotor bearing for a wind turbine
US20120032448A1 (en) * 2010-06-30 2012-02-09 Mitsubishi Heavy Industries, Ltd. Wind turbine generator
US20130052013A1 (en) * 2011-08-23 2013-02-28 Charles Franklin ECKART Wide Blade Multiple Generator Wind Turbine
US10352419B2 (en) * 2016-06-30 2019-07-16 Borgwarner Inc. Carrier stop for split ring planetary drive

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4031747B2 (ja) 2003-09-30 2008-01-09 三菱重工業株式会社 風力発電用風車
DE10360693A1 (de) * 2003-12-19 2005-07-14 Winergy Ag Planetengetriebe, insbesondere für Windkraftanlagen
ES2274696B1 (es) 2005-06-13 2008-05-01 GAMESA INNOVATION & TECHNOLOGY, S.L. Turbina eolica.
MX2008014894A (es) 2006-05-22 2009-02-10 Vestas Wind Sys As Sistema de engranes para turbina eolica.
CN101595299B (zh) 2007-01-31 2012-06-27 维斯塔斯风力系统有限公司 风轮机，用于维修风轮机的主轴承单元的方法及其使用
DE102007042770A1 (de) 2007-09-07 2009-03-12 Schaeffler Kg Rotorlagerung für eine Windenergieanlage
DE102009016329A1 (de) * 2009-04-06 2010-10-14 Innovative Windpower Ag Getriebe, insbesondere für eine Windenergieanlage, Antriebsstrang, welcher das Getriebe aufweist, sowie Kraftwerk und Kraftwerkspark
DE102010008198A1 (de) 2010-02-17 2011-08-18 Schaeffler Technologies GmbH & Co. KG, 91074 Großlager für ein Planetengetriebe sowie Planetengetriebe mit dem Großlager
CN115896475B (zh) * 2022-11-07 2024-05-31 宁波锦越新材料有限公司 一种超高纯铝细晶制备设备

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6872049B2 (en) * 2001-04-02 2005-03-29 Vestas Wind Systems A/S Wind turbine comprising a planetary gear

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29609794U1 (de) * 1996-06-03 1996-08-22 aerodyn GmbH, 24768 Rendsburg Getriebe-Generator-Kombination
DE29612720U1 (de) * 1996-07-23 1996-10-02 aerodyn GmbH, 24768 Rendsburg Windkraftanlage
DE10032626A1 (de) * 2000-07-07 2003-04-03 Flender A F & Co Planetengetriebe mit Vorgelege
DE01954251T1 (de) * 2000-08-15 2005-05-04 Hansen Transmissions Int Antriebsaufbau für eine Windturbine

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6872049B2 (en) * 2001-04-02 2005-03-29 Vestas Wind Systems A/S Wind turbine comprising a planetary gear

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070142156A1 (en) * 2005-11-21 2007-06-21 Hansen Transmissions International, Naamloze Vennootschap Gearbox for a wind turbine
US7614976B2 (en) * 2005-11-21 2009-11-10 Hansen Transmissions International, Naamloze Vennootschap Gearbox for a wind turbine
US20100244454A1 (en) * 2007-08-31 2010-09-30 Schaeffler Technologies Gmbh & Co., Kg Rotor bearing for a wind turbine
US8222759B2 (en) 2007-08-31 2012-07-17 Schaeffler Technologies AG & Co. KG Rotor bearing for a wind turbine
US20120032448A1 (en) * 2010-06-30 2012-02-09 Mitsubishi Heavy Industries, Ltd. Wind turbine generator
US8672628B2 (en) 2010-06-30 2014-03-18 Mitsubishi Heavy Industries, Ltd. Wind turbine generator
US20130052013A1 (en) * 2011-08-23 2013-02-28 Charles Franklin ECKART Wide Blade Multiple Generator Wind Turbine
US8851839B2 (en) * 2011-08-23 2014-10-07 Charles Franklin ECKART Wide blade multiple generator wind turbine
US10352419B2 (en) * 2016-06-30 2019-07-16 Borgwarner Inc. Carrier stop for split ring planetary drive

Also Published As

Publication number Publication date
GB0118996D0 (en) 2001-09-26
WO2003014567A1 (fr) 2003-02-20
EP1423608A1 (fr) 2004-06-02

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Legal Events

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AS Assignment

Owner name: HANSEN TRANSMISSIONS INTERNATIONAL NV, BELGIUM

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:FLAMANG, PETER;REEL/FRAME:014731/0369

Effective date: 20040213

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION