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EP2488767A1 - Ensemble palier pour éolienne - Google Patents

Ensemble palier pour éolienne

Info

Publication number
EP2488767A1
EP2488767A1 EP10768479A EP10768479A EP2488767A1 EP 2488767 A1 EP2488767 A1 EP 2488767A1 EP 10768479 A EP10768479 A EP 10768479A EP 10768479 A EP10768479 A EP 10768479A EP 2488767 A1 EP2488767 A1 EP 2488767A1
Authority
EP
European Patent Office
Prior art keywords
bearing
pocket
partner
sliding
storage device
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Withdrawn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
EP10768479A
Other languages
German (de)
English (en)
Inventor
Juergen Wagner
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.)
Suzlon Energy GmbH
Original Assignee
Suzlon Energy 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 Suzlon Energy GmbH filed Critical Suzlon Energy GmbH
Publication of EP2488767A1 publication Critical patent/EP2488767A1/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Withdrawn legal-status Critical Current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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/26—Systems consisting of a plurality of sliding-contact bearings
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/26—Brasses; Bushes; Linings made from wire coils; made from a number of discs, rings, rods, or other members
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C43/00—Assembling bearings
    • F16C43/02—Assembling sliding-contact bearings
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/10—Application independent of particular apparatuses related to size
    • F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/31—Wind motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/02—Fluid pressure
    • 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 bearing device for a wind turbine, wherein the bearing assembly has two bearing partners, which are arranged rotatably about a common axis to each other. Between the bearing partners an effective in an axial direction sliding coating is provided.
  • bearing assemblies between the tower of the plant and the nacelle are arranged and serve, among other things, the absorption and discharge of shear, gyro and yaw forces from the machine carrier of the nacelle in the tower. It is possible by means of the bearing assembly, the so-called azimuth bearing and the azimuth drive wind tracking of the nacelle.
  • the nacelle is rotated in the horizontal plane about a substantially vertical axis of rotation, so that the wind flows perpendicular to a rotational plane of the rotor and thus the energy yield is maximized.
  • a bearing arrangement is known from EP 124702181.
  • a plain bearing is given, with an embodiment indicating the features listed in the preamble of the main claim.
  • An arranged on a bearing partner annular rib engages in a provided on another bearing partner annular groove which is provided with peripheral surfaces with sliding linings.
  • the sliding linings are subdivided like a segment and firmly but detachably connected to the rib. This allows the inspection of the sliding linings and, if necessary, their replacement during operation.
  • the outer ring is divided into segments, which are fastened by screws to the scaffold.
  • This is to be regarded as disadvantageous, since the number of arranged in the circle coverings is very high. This requires a high number of pieces, so higher Cost, due to increased wear and thus an increased need to replace the pads. Furthermore, the replacement of the coverings is difficult by their fastening by means of screws.
  • a maintenance-friendly and power flow-optimized arrangement of the sliding linings is to be made possible.
  • the interchangeability of the sliding linings should be improved in a simple and cost-effective manner.
  • the bearing assembly can simultaneously serve as an active brake.
  • the object is achieved with the features of the main claim 1 by the individual sliding linings are arranged in pockets between the two bearing partners, wherein the pockets are provided in the material of the machine frame.
  • the axial sliding linings are designed plate-shaped, so that they can be sawn from plate material, whereby complex milling or shooting are not required.
  • At the pocket at least one stop is provided such that the sliding coating can be applied, and so between the sliding lining and the bearing partner a positive connection for power transmission is provided, which is effective in the circumferential direction. This results in the advantage that fewer deposits are provided, which are arranged in the pockets.
  • An advantageous embodiment of the invention is that the construction is designed so that the necessary machining can be done on one side of the underside of the machine frame.
  • the chip volume is small, with no special requirements for form and position tolerances and surface quality.
  • the bag is intended as a recess directly in one of the bearing partners (), recommended directly on the machine carrier.
  • the pocket extends to a radial edge of the machine frame, thus simplifying the interchangeability of the sliding liners and making it cheaper.
  • the pocket is designed such that the sliding lining can be mounted in the radial direction. The fact that the sliding linings are divided into segments, they can be replaced individually.
  • the bag includes a first radially effective stop, which limits the possibility of movement of the sliding lining in the assembled state. This prevents the sliding linings from working radially out of the pocket.
  • a second radially effective stop which is designed as a stopper, determines the radial position of the assembled sliding lining.
  • the axial sliding linings are spring loaded. Due to the resilience of the disc spring construction, the system is relatively insensitive to unevenness of the bearing ring. Furthermore, the system offers the possibility to be able to adjust the inhibition in a wide range by changing the axial and radial bias.
  • adjusting screws are provided both in the machine frame and in the locking plate, through which the radial lining along the wedge can be moved.
  • lifting means are provided. The lower sliding linings are relieved of the spring tension, so that the sliding linings are unencumbered in the pockets.
  • the two bearing partners are lifted by hydraulic rams, which are temporarily installed and operated by means of a manually operated hydraulic pump, from each other and the sliding linings can be replaced.
  • One bearing partner engages around the other bearing partner in the axial direction, whereby a further sliding layer is provided between the bearing partners.
  • a bearing partner which is designed as a machine carrier
  • another bearing partner which is designed as a bearing ring, rotatably arranged about a common axis to each other.
  • On the bearing ring an external toothing is provided.
  • the storage can be performed both inside and outside. Accordingly, the teeth attached to the bearing ring are mounted outside or inside, however, internal gears are usually associated with higher manufacturing costs.
  • the lubricant supply is ensured by a lubrication unit in the machine carrier. After a certain period of use of the bearing assembly can be relubricated from the outside to compensate for any loss of lubricant.
  • a simple felt coating with lubricant supply ensures the lubrication of the pads.
  • Another advantage of the invention is that at least one actively controllable braking device is provided in a bearing partner. Hydraulic cylinders can be used instead of the disc spring units in the corresponding holes in the locking plates.
  • Fig. 2 is a perspective view of an underside of a first
  • FIG. 1 Embodiment of a bearing assembly of a wind turbine gem. 1
  • Fig. 3 is another view of the bearing assembly of FIG. 2
  • 4 is a plan view of the bearing assembly of FIG. 2
  • Fig. 5 shows a section through the bearing assembly along the line B-B according to
  • Fig. 6 shows a section through the bearing assembly along the line C-C according to
  • Fig. 7 shows a section through the bearing assembly along the line A-A according to
  • the nacelle is due to the necessary wind tracking via a bearing assembly 1, the so-called azimuth bearing, rotatably supported about a vertical axis 5 on the tower 3.
  • the wind direction tracking is performed by the azimuth bearing 1 and the azimuth drives.
  • the drive train which includes a rotor shaft and a transmission, and a generator connected to the fast shaft of the transmission.
  • the drive train is mounted on the machine frame 10 via a rotor bearing and via the gearbox.
  • On the rotor shaft is a rotor flange, on which the hub 38 is arranged.
  • the hub 38 receives the rotor blades 4 and transmits the forces acting on the rotor blade 4 forces on the rotor shaft.
  • the bearing assembly 1 according to the invention is also applicable to other types of wind turbines.
  • FIG. 2 shows the above-mentioned bearing assembly 1, with respect to the mounting position, from the lower side.
  • a first bearing partner 9 is formed as a machine carrier 10 with closure plates 1 1.
  • the closure plates 1 1 are so connected to the machine frame 10, so that they surround a second, designed as a bearing ring 12 bearing partner in the axial direction 8 from the inside (Fig. 5).
  • the bearing ring 12 is with provided with a ring gear 13, can be connected via holes 14 with the tower flange tower 3.
  • On the bearing ring 12 an external toothing is provided, can engage in the azimuth drives, not shown.
  • receiving recesses 21 are embedded for the drives.
  • 1 1 sliding devices 16 are provided in the closure plates, which are each equipped with an integrated, biased sliding coating 19.
  • About adjustment screws 29 for the axial and radial preload the bearing friction can be adjusted in a wide range.
  • Fig. 3 discloses the bearing assembly 1 of FIG. 2, wherein the bearing ring 12 is not shown.
  • the machine frame 10 is shown with axial 17 and radial slide bearing pads 18.
  • the axial sliding linings 17 are arranged in pockets 20, the pockets 20 being provided in the material of the machine carrier 10.
  • the pockets 20 extend up to the radial edge 6 of the machine carrier 10.
  • the sliding lining 17 can be mounted particularly easily in the radial direction 8.
  • stopper 22 can be arranged as a locking stop, which ensure that the axial sliding linings 17 can not work radially out of the pocket 20.
  • 10 receiving bores 33 are provided for hydraulic ram 30 in the machine frame.
  • a lubricating device 33 for lubricating the axial, the machine frame 10 facing bearing surface of the bearing ring 12 and the pads 17 of the machine frame 10 is arranged. It is conceivable to arrange several lubricating devices distributed over the circumference. A simple felt covering with lubricant supply ensures the lubrication of the radial 18 and axial linings 17,19.
  • 4 shows a plan view of the machine carrier 10 with the mounted bearing 1. Shown therein are the sections AA, BB and CC, which are shown in Figures 5, 6 and 7, and will be explained in the following.
  • the lower slide device 16 which can be prestressed in the closure plate 11, comprises a cylindrical housing 24, which is closed in a form-fitting manner with a stopper 25.
  • an adjusting screw 28 is screwed axially with lock nut 26, which acts on the disc springs 27.
  • the plate springs 27 generate a biasing force acting on the sliding coating 19.
  • the sliding device 16 may lead a bore which is connectable to a lubricant supply, not shown
  • the biasing means 16 are screwed on, so that the lower sliding linings 19 are relieved of the bias voltage.
  • the hydraulic rams 30, which can be temporarily installed, and can be operated by means of a hydraulic pump activated.
  • the machine frame 10 is lifted from the bearing ring 12, so that the sliding linings 17 are unencumbered on the bearing ring 12 in the pockets 20 and on the bearing ring 12.
  • the lock 22 is opened and the sliding linings 19 can be removed in the radial direction 8 from the pockets 20 and replaced.
  • the lock 22 is applied again and the machine frame 10 is lowered.
  • an active brake can be used instead of the disc spring units 27 controllable actuating means, such as hydraulic cylinder 30 in the corresponding holes.
  • the radial sliding linings 18 bear against the machine carrier 10 and are formed in this embodiment in a wedge shape.
  • the setting of the radial prestressing takes place via the axial displacement of the wedge-shaped sliding lining 18.
  • adjusting screws 23 are provided in the machine carrier 10, via which the radial lining 18 can be displaced axially.
  • other radial bearings may alternatively be provided, for example, this may also be formed in a socket shape.
  • FIG. 6 shows a section along the line A-A.
  • the structure of the lower lubricating device 32 of the bearing assembly 1 is illustrated.
  • the upper 17 of the radial sliding coating 18 between the machine frame 10 and bearing ring 12 are shown.
  • a felt covering 36 is supplied with grease, which lubricates the sliding linings 18.
  • FIG. 7 shows a section through the pocket 20 and the sliding lining 17 of the machine carrier 10. This clearly shows that the upper sliding lining 17 is provided in the pocket 20 in a rotationally fixed manner to the machine carrier 10.
  • the force acting on the sliding coating 17 circumferential force caused by the friction of the bearing assembly 1 is derived via stops 29 in the circumferential direction 15 from the sliding coating 17 in the machine frame 10. These stops 29 are formed by the tangential surfaces of the pocket 20.

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)
  • Sliding-Contact Bearings (AREA)
  • Support Of The Bearing (AREA)
  • Wind Motors (AREA)

Abstract

La présente invention concerne un système de palier pour une éolienne (2), l'ensemble palier présentant deux éléments de palier associés (9, 12) agencés de manière à pouvoir tourner autour d'un axe commun (5) l'un par rapport à l'autre. Une garniture de glissement (17) active dans une direction axiale (7) est agencée entre les éléments de palier associés. L'invention vise à mettre au point un ensemble palier pour une éolienne qui, entre autres, ne présente pas les inconvénients de l'état de la technique. L'invention vise en particulier à permettre d'agencer les garnitures de glissement de façon à faciliter leur entretien et à optimiser le flux de force. L'invention a également pour objet d'améliorer l'interchangeabilité des garnitures de glissement de manière simple et peu coûteuse, par l'agencement des différentes garnitures de glissement dans des évidements (20) entre les deux éléments de palier associés, les évidements étant ménagés dans le matériau du support de machine. De plus, l'ensemble palier peut en même temps servir de frein actif.
EP10768479A 2009-10-16 2010-10-17 Ensemble palier pour éolienne Withdrawn EP2488767A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009049769A DE102009049769A1 (de) 2009-10-16 2009-10-16 Lageranordnung für eine Windturbine
PCT/EP2010/065578 WO2011045435A1 (fr) 2009-10-16 2010-10-17 Ensemble palier pour éolienne

Publications (1)

Publication Number Publication Date
EP2488767A1 true EP2488767A1 (fr) 2012-08-22

Family

ID=43470223

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10768479A Withdrawn EP2488767A1 (fr) 2009-10-16 2010-10-17 Ensemble palier pour éolienne

Country Status (6)

Country Link
US (1) US20120224799A1 (fr)
EP (1) EP2488767A1 (fr)
CN (1) CN102639884A (fr)
AU (1) AU2010306501A1 (fr)
DE (1) DE102009049769A1 (fr)
WO (1) WO2011045435A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11603882B2 (en) 2018-09-26 2023-03-14 Vestas Wind Systems A/S Bearing unit for a yawing system of a wind turbine

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EP2781740B1 (fr) * 2011-03-08 2018-05-09 Vestas Wind Systems A/S Structure de support de l'arbre de rotor d'une éolienne
EP2706254B8 (fr) * 2012-09-05 2015-06-10 S.B. Patent Holding ApS Système de freinage
AT513743B1 (de) 2013-01-30 2014-07-15 Miba Gleitlager Gmbh Windkraftanlagengetriebe
AT513507B1 (de) * 2013-01-30 2014-05-15 Miba Gleitlager Gmbh Gleitlagerpaket
AT513516B1 (de) 2013-01-30 2014-05-15 Miba Gleitlager Gmbh Windkraftanlagengetriebe
US9951818B2 (en) 2015-05-13 2018-04-24 Wind Solutions, LLC. Wind turbine yaw bearing pre-load
DE102015216763B4 (de) * 2015-09-02 2017-09-07 Siemens Aktiengesellschaft Entfernen eines vorderen oberen Gleitelements eines Gierlagers einer Windkraftanlage
PL3139058T3 (pl) 2015-09-04 2018-06-29 S.B. Patent Holding Aps System do serwisowania i sposób serwisowania urządzenia hamulcowego układu hamulcowego z tarczą hamulcową umieszczoną poziomo
US11286914B2 (en) 2016-06-30 2022-03-29 Vestas Wind Systems A/S Nacelle base frame assembly for a wind turbine
DE102018107172A1 (de) * 2018-03-26 2019-09-26 Liebherr-Components Biberach Gmbh Stellantrieb zum Verstellen des Pitchwinkels eines Rotorblatts einer Windkraftanlage sowie Windkraftanlage mit einem solchen Stellantrieb
DE102018110925A1 (de) * 2018-05-07 2019-11-07 Liebherr-Components Biberach Gmbh Stellantrieb zum Verstellen eines Großwälzlagers
EP3594490B1 (fr) * 2018-07-09 2021-04-07 Siemens Gamesa Renewable Energy A/S Agencement de palier de lacet
PL3597903T3 (pl) * 2018-07-20 2021-12-27 General Electric Renovables España S.L. System odchylania do turbiny wiatrowej
WO2020057701A1 (fr) 2018-09-17 2020-03-26 Vestas Wind Systems A/S Ensemble de griffes de lacet pour roulement d'orientation d'éolienne
ES2951920T3 (es) * 2019-05-16 2023-10-25 Siemens Gamesa Renewable Energy As Disposición de rodamientos para una turbina eólica y turbina eólica
EP3904711A1 (fr) * 2020-04-28 2021-11-03 Siemens Gamesa Renewable Energy A/S Procédé de remplacement d'un patin coulissant d'un palier coulissant rotatif, palier lisse et éolienne
CN116529497A (zh) * 2020-11-30 2023-08-01 米巴滑动轴承奥地利有限公司 用于装配风力机的转子轴承的方法
DE102020133940A1 (de) * 2020-12-17 2022-06-23 Renk Gmbh Gleitlager mit Gleitsegmenten

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Cited By (1)

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Publication number Priority date Publication date Assignee Title
US11603882B2 (en) 2018-09-26 2023-03-14 Vestas Wind Systems A/S Bearing unit for a yawing system of a wind turbine

Also Published As

Publication number Publication date
CN102639884A (zh) 2012-08-15
US20120224799A1 (en) 2012-09-06
DE102009049769A1 (de) 2011-04-21
AU2010306501A1 (en) 2012-06-07
WO2011045435A1 (fr) 2011-04-21

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