WO2015144460A1 - Système de palier lisse - Google Patents

Système de palier lisse Download PDF

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Publication number
WO2015144460A1
WO2015144460A1 PCT/EP2015/055304 EP2015055304W WO2015144460A1 WO 2015144460 A1 WO2015144460 A1 WO 2015144460A1 EP 2015055304 W EP2015055304 W EP 2015055304W WO 2015144460 A1 WO2015144460 A1 WO 2015144460A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
inner ring
ring
bearing system
sliding
Prior art date
Application number
PCT/EP2015/055304
Other languages
German (de)
English (en)
Inventor
Martin Buettner
Original Assignee
Aktiebolaget Skf
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 Aktiebolaget Skf filed Critical Aktiebolaget Skf
Publication of WO2015144460A1 publication Critical patent/WO2015144460A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/02—Sliding-contact bearings
    • F16C25/04—Sliding-contact bearings self-adjusting
    • 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
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • 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
    • 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
    • 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
    • F16C33/72—Sealings
    • F16C33/74—Sealings of sliding-contact bearings

Definitions

  • the present invention relates to a slide bearing system for receiving radial and / or axial bearing forces and / or tilting moments with a bearing inner ring and a bearing outer ring cooperating with the bearing inner ring, wherein at least one sliding surface is formed between the bearing inner ring and bearing outer ring, and further provided at least one movable carrier is, which is received by the bearing inner ring and / or the bearing outer ring.
  • a sliding bearing system is known with a first and a second between an inner ring and an outer ring arranged sliding surface, wherein further on the outer ring, a brake member is arranged, which acts on the inner ring, and its relative mobility Restricts to the outer ring.
  • a piston is arranged on the brake element, which presses the piston with more or less large force to the corresponding inner ring by means of a lever or other elements acting mechanically on the piston elements.
  • a motor is provided, which acts on the piston with the appropriate force.
  • a disadvantage of this known plain bearing system is that the mechanical actuation svorraumen for the piston are very maintenance-intensive and difficult to assemble.
  • Object of the present invention is therefore to provide a possible maintenance-free and easier to install sliding bearing with bias.
  • a sliding bearing system for receiving radial and / or axial bearing forces and / or tilting moments with a bearing inner ring and a bearing outer ring cooperating with the bearing inner ring.
  • at least one sliding surface is formed between the bearing inner ring and bearing outer ring.
  • the sliding bearing system has at least one movable support, which is received by the bearing inner ring and / or the bearing outer ring or is arranged thereon.
  • This movable support of the bearing inner ring can be biased relative to the bearing outer ring by the carrier is more or less heavily loaded in contact with the corresponding bearing ring is brought.
  • the bearing ring can be prestressed or a relative movement of the bearing rings can be braked or blocked relative to one another.
  • the invention is based on the idea of forming a fluid-loadable intermediate space between the at least one movable carrier and the bearing ring receiving the carrier, by means of which the movable carrier can be acted upon by a fluid pressure. By means of this fluid pressure, the carrier can be moved and the contact strength between carrier and the corresponding bearing ring can be adjusted.
  • a simple to install and substantially maintenance-free possibility is created by the provision of fluidbeaufschlagbaren gap to move the carrier and thus provide a bias.
  • the number of elements to be installed compared to the known from the prior art plain bearing is significantly reduced, so that the entire system is less susceptible to interference.
  • a backlash between the bearing rings can be determined via the movable carrier so that micro-movements in the bearing are reduced or avoided.
  • the storage system advantageously has a reduced susceptibility to material fatigue.
  • it may also be provided to release the bearing only for a movement, ie not to contact the movable support or weakly loaded contact with the corresponding bearing ring when the bearing is actuated.
  • pressurized fluid may be applied to the movable support so that the bearing is locked in position. Since the pressurization via fluid and not via mechanical elements, such a determination can also be maintained maintenance-free and material fatigue over a long period.
  • the at least one sliding surface for the bearing inner ring and / or the bearing outer ring is accommodated on the at least one movable carrier.
  • a lining with a high coefficient of friction can also be arranged on at least one of the movable carriers.
  • the movable support can also be designed as a braking device, which can dampen a movement of the bearing rings to each other.
  • Such a configuration is particularly useful in bearings that are to be kept in position at standstill, which tilt by external high loads on the bearing clearance and / or require, for example, a precise adjustment of bearing outer ring to bearing inner ring, for example, for positioning a turbine in a fluid stream , If, for example, the turbine connected to the bearing inner ring is rotated with respect to the bearing outer ring, the brake lining according to the invention on the movable carrier can ensure that the turbine is oriented with precise position, and is securely fixed at standstill and is not tilted in the standstill position by external forces, is rotated or otherwise moved.
  • At least one further second sliding surface is provided between the bearing inner ring and the bearing outer ring.
  • This second sliding surface preferably serves as a main sliding surface between the bearing inner ring and the bearing outer ring, while, for example, the sliding surface arranged on the movable support constitutes a shiftable sliding surface.
  • the movable support is designed as a movable annular piston or as a ring segment.
  • the training as an annular piston allows the carrier to move over the entire circumference of the bearing ring against the corresponding other bearing ring, so that the most even possible pressure on the other bearing ring.
  • the intermediate space can be formed in a fluid-tight manner, for example by means of seals arranged on the carrier, it is simpler to introduce a fluid-loadable element into the intermediate space, which expands or deforms elastically during fluid loading, for example, and thus exerts a pressure on the movable carrier can.
  • the elastic element may be formed as a membrane which expands in Fluidbeauf only in the direction of movable support and which seals the gap relative to the movable support.
  • the elastic fluidbeaufschlagbare element has a sealed relative to the outer space interior, which is acted upon by pressurized fluid. It is preferred if the elastic fluidbeaufschlagbare element is formed for example as a bellows or hose. Such bellows or hoses are easy to insert into the intermediate space and connectable to a pressure fluid access, with which the bellows or hose can be acted upon with pressurized fluid.
  • the carrier may also be adapted to the shape of the elastic element.
  • the elastic element is designed, for example, as a bellows or hose
  • the carrier and / or the bearing ring having the carrier has a surface facing the hose or bellows which is of concave design. This can also be counteracted damage to the elastic element.
  • the concave surface also has advantages when the intermediate space itself is subjected to the pressure fluid, since, for example, a larger guide surface is provided.
  • the movable support is dimensioned such that without Fluidbeauf regurgitation of the carrier or attached thereto sliding surface or attached brake pad has no contact or hardly pressure-loaded contact with the adjacent bearing ring.
  • the sliding surface may be spherical and / or conical and / or cylindrical. As a result, axial and / or radial forces and / or tilting moments can be absorbed.
  • the inner ring has at least a first and a second inner ring part.
  • first inner ring part as Axiallagerinnenring or angular contact bearing inner ring or radial bearing inner ring
  • the second inner ring part as Axialla- gerinnenring or angular contact bearing inner ring or radial bearing inner ring may be formed.
  • the two-part design may of course be formed as two individual elements, wherein the first inner ring part with the second inner ring part is releasably and permanently connected, but it is also possible to manufacture the inner ring as a one-piece component whose dimensions are adapted only to the corresponding dimensions of the first and second inner ring part.
  • FIG. 1 shows a schematic perspective view of a plain bearing system according to the invention in a plan view
  • FIG. 2 is a schematic sectional view through the sliding bearing system shown in FIG. 1;
  • FIG. 3 is a schematic representation of an alternative embodiment of the sliding bearing system according to the invention from FIG. 2;
  • FIG. 4 shows a schematic illustration of a further alternative embodiment of the slide bearing system according to the invention from FIG. 2;
  • FIGS. 1 to 4 is a schematic detail of the plain bearing systems of FIGS. 1 to 4;
  • FIGS. 1 to 5 shows a schematic representation of a plan view of the outer ring of the slide bearing systems according to the invention shown in FIGS. 1 to 5;
  • FIG. 7 shows a schematic representation of a detail of the sliding bearing systems according to the invention from FIGS. 1 to 6;
  • FIG. 7 shows a schematic representation of a detail of the sliding bearing systems according to the invention from FIGS. 1 to 6;
  • FIG. 8 shows a schematic representation of a further preferred embodiment of the sliding bearing system according to the invention.
  • FIG. 11 is a schematic representation of a further preferred embodiment of the sliding bearing system according to the invention.
  • FIG. 12 shows a schematic illustration of a further preferred embodiment of the sliding bearing system according to the invention.
  • Fig. 1 shows a schematic perspective view of a sliding bearing system 1 with an outer ring 2 and an inner ring 4, which are formed rotatable against each other.
  • the outer ring 2 and the inner ring 4 each have through holes 6, 8, by means of which the plain bearing system 1 is rotatably connected to the components to be stored.
  • Such plain bearing systems 1 are used in particular for the rotatable mounting of turbines, wherein the turbines can be rotated by means of the plain bearing system 1 about its axis, for example in a fluid stream.
  • Such turbines are installed, for example, in a tidal power station or a wind power plant.
  • FIG. 2 shows a schematic sectional view through the sliding bearing system 1 according to the invention shown in Figure 1, again the outer ring 2 and the inner ring 4 and the fastening holes 6; 8 are shown.
  • the sliding bearing system 1 has two sliding surfaces 10, 12 between the outer ring 2 and the inner ring 4, which ensure rotatability of the inner ring 4 to the outer ring 2.
  • Fig. 2 shows that the inner ring 4 and the outer ring 2 are made in two parts, the bipartite of the outer ring 2 is necessary to mount the inner ring 4 can.
  • the inner ring 4 may optionally also be formed in two parts, for example, as shown in Fig. 2, as two angular bearing inner rings, which are detachably or permanently connected to one another.
  • the sliding bearing surfaces 10, 12 may be conical, for example. However, as explained more fully below, it is also possible to form other slide bearing surface shapes. In addition, it may be useful and is also preferable not to form the inner ring 4, as shown in Fig. 2, in two parts, but, as shown in FIG. 3, to manufacture in one piece, whereby greater stability can be achieved.
  • the sliding bearing system 1 further comprises a movable support 14 which is received in the outer ring 2 in the embodiments shown in FIGS. 2, 3 and 4.
  • a gap 16 is provided between the movable carrier 14 and outer ring 2, which is acted upon by a pressure p.
  • FIGS. 3 and 4 show enlarged in FIGS. 3 and 4, wherein FIG. 3 shows a back-to-back arrangement and FIG. 4 shows a face-to-face arrangement.
  • the movable carrier 14 and the intermediate space 16 formed between the outer ring 2 and the movable carrier 14 are clearly illustrated.
  • this intermediate space 16 is acted upon by fluid pressure p, which makes it possible to bring the movable carrier 14 into contact with the inner ring 4.
  • a bellows 18 or generally an elastic element may be arranged, the interior 20 of which is acted upon by the fluid pressure p.
  • the intermediate space 16 may also be provided by means of sealing elements 22, which may be mounted, for example, on the movable support 14 or in the outside.
  • ring 2 are arranged to be sealed against a bearing clearance 24 between the inner ring 4 and outer ring 2.
  • the bearing clearance 24 may be open to an environment, but it is also possible, as shown in Fig. 4, to provide the bearing clearance 24 sealing lips 26, which also allows ingress of dirt, moisture or Prevent foreign objects from entering the plain bearing.
  • Fig. 4 also shows an embodiment in which the inner ring 4 in two parts and the outer ring 2 are made in one piece.
  • the bearing clearance 24 can be limited by means of the movable carrier 14 which can be subjected to pressure p, since the movable carrier 14 can contact the inner ring 4 more or less firmly.
  • FIGS. 5a to 5c show schematically in FIGS. 5a to 5c, wherein, without pressurization (see FIG. 5a), the intermediate space 16 is in a ground state, wherein the movable support 14 is more or less pressure-free and optionally contact-free to the contact surface (not shown) of the opposite bearing. is guided around.
  • the movable support 14 brings no or only a small force on the opposite bearing ring, so that it is more or less freely movable.
  • FIG. 6 shows schematically a plan view from inside on a bearing ring 2; 4, which shows a gap 16 for receiving the movable support 14.
  • the gap 16 is formed as an annular groove in which a designed as an annular piston carrier 14 can be accommodated.
  • individual carrier elements may also be provided.
  • circumferentially along the bearing ring 2; 4 are arranged, which are each acted upon individually with pressurized fluid. This can be advantageous, in particular, when different pressures distributed over the circumference are to be applied to the movable carriers 14.
  • the annular piston 14 itself can also, for example, as shown in FIG. 6, with a feather key 34 against rotation in the bearing ring 2; 4 are secured. Alternatively, it is also conceivable, the rotation by off-center insertion of the annular piston 14 in the bearing ring 2; 4 to provide. It would also be possible to prevent rotation by an oval-shaped annular piston 14 or by another non-rotatable contour of the annular piston 14. Of course, it is also possible to dispense entirely with an anti-twist device. If the annular piston 14 is formed from at least one ring segment, it can also be used to prevent rotation in the bearing ring 2; 4 be executed. As can further be seen from the exemplary embodiment of FIG.
  • a bellows or hose 18 is accommodated in the annular groove 16, which can be acted upon by pressurized fluid and can exert a pressure on the movable carrier 14.
  • a Fluidbeaufschlagungssystem 28 may be provided which can pressurize the bellows 18 with pressurized fluid.
  • a valve system can be connected in the usual way, which controls the fluid admission and the pressure in the bellows 18.
  • the movable support 14 may be concave on a side 30 facing the bellows 18, so that the bellows 18 at all Pages on the movable support 14 can press.
  • a concave configuration can also be formed in the outer ring 2 or analogously in the inner ring 4, so that the intermediate space 16 is, for example, at least partially substantially elliptical in cross section.
  • FIGS. 8 to 13 show further aspects and different embodiments of the slide bearing system 1 according to the invention, with only the differences being discussed in each case.
  • Fig. 8 shows that on the one hand, the inner ring 4 does not have to form a symmetrical configuration of two inclined sliding surfaces 10, 12, but that it is also possible to form the sliding bearing system as a combination of an angular contact and a thrust bearing.
  • FIG. 8 shows that in turn the movable carrier 14 is arranged on the outer ring 2 and can influence the bearing clearance 24 between inner ring 4 and outer ring 2.
  • a gap 16 is formed in the inner ring 4, which is acted upon by a pressurized fluid.
  • Fig. 10 shows a further preferred embodiment of the present invention, wherein the movable support 14 and the gap 16 are not the same size.
  • the movable support 14 simultaneously carries the sliding surface 10.
  • the movable support 14 is equipped with a sliding surface 10
  • the movable support 14 shown in the previous figures can also be equipped with a sliding layer.
  • the movable support 14 may also be provided with a friction lining, so that the movable support 14 can serve as a braking element.
  • a friction lining in bearings that carry heavy loads or that are to be secured at a standstill against rotation by external forces or external moments, such
  • Braking function may be necessary to counteract the inertial forces during movement.
  • the movable carrier 14 is not designed as a one-piece annular piston, as shown in FIG. 6, but rather as individual elements, it is likewise conceivable for a carrier element to be a carrier element.
  • NEN friction lining and another support member carries a sliding surface, so that they can be used differently and depending on the application, a sliding surface or a brake pad is brought into contact with the corresponding bearing ring.
  • FIG. 11 shows, that the sliding surface 10 is completely dispensed with.
  • the carrier 14 only has a braking function and is mainly used to set the bearing rings 2, 4 to each other at a standstill. 12 and 13 show further bearing shapes, wherein the inner ring of Fig.
  • Fig. 13 shows a combination of axial and radial sliding surfaces.
  • FIG. 13 shows that further sliding surfaces 34 may be provided.
  • all slide bearing designs can have the individual discussed elements in any combination.
  • the plain bearing system according to the invention enables a sanitaryweise play-free storage system, with a variable bias voltage is adjustable. This can be counteracted in particular wear and fatigue due to micro-movements of the bearing.
  • the storage system according to the invention enables a complete fixing of the bearing rings to one another at standstill.
  • the bearing can also be equipped with special functionalities, such as a corrosion protection coating or wear sensors.
  • the sliding bearing can be designed as a maintenance-free sliding bearing. However, it is also possible to initially pre-lubricate the slide bearing, wherein preferably care can be taken to a low-maintenance design as possible.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)

Abstract

L'invention concerne un système de palier lisse (1), destiné à supporter des forces de palier axiales et/ou radiales et/ou des couples de renversement, qui comprend une bague intérieure de palier (4) et une bague extérieure de palier (2) coopérant avec la bague intérieure de palier (4), une ou plusieurs surfaces de glissement (10 ; 12 ; 34) étant formées entre la bague intérieure de palier (4) et la bague extérieure de palier (2), et en outre un ou plusieurs supports mobiles (14) étant disposés au niveau de la bague intérieure de palier (4) et/ou de la bague extérieure de palier (2), un espace intermédiaire (16), pouvant être alimenté en fluide, étant ménagé entre le ou les supports mobiles (14) et la bague de palier (2 ; 4) recevant le ou les supports (14) de telle sorte que le support mobile (14) peut être soumis à une pression de fluide.
PCT/EP2015/055304 2014-03-26 2015-03-13 Système de palier lisse WO2015144460A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014205637.3 2014-03-26
DE102014205637.3A DE102014205637A1 (de) 2014-03-26 2014-03-26 Gleitlagersystem

Publications (1)

Publication Number Publication Date
WO2015144460A1 true WO2015144460A1 (fr) 2015-10-01

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2015/055304 WO2015144460A1 (fr) 2014-03-26 2015-03-13 Système de palier lisse

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Country Link
DE (1) DE102014205637A1 (fr)
WO (1) WO2015144460A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9856910B2 (en) * 2015-11-30 2018-01-02 Roller Bearing Company Of America, Inc. Self-lubricated thrust bearing for a hinged aircraft wing
CN110799763A (zh) * 2017-06-29 2020-02-14 乌本产权有限公司 风能设备转动连接件和具有其的风能设备
US11644013B2 (en) 2019-05-21 2023-05-09 Miba Gleitlager Austria Gmbh Nacelle for a wind turbine

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016209206A1 (de) 2016-05-27 2017-12-14 Wobben Properties Gmbh Windenergieanlage
DE102016210039A1 (de) 2016-06-07 2017-12-07 Wobben Properties Gmbh Windenergieanlagen-Drehverbindung, Rotorblatt und Windenergieanlage mit selbiger
AT519288B1 (de) 2016-10-21 2018-07-15 Miba Gleitlager Austria Gmbh Lagerelement
DE102018201885A1 (de) * 2018-02-07 2019-08-08 Aktiebolaget Skf Abgedichtetes Lagermodul
AT521885B1 (de) 2018-12-13 2020-09-15 Miba Gleitlager Austria Gmbh Gondel für eine Windkraftanlage
AT521884B1 (de) 2018-12-13 2020-10-15 Miba Gleitlager Austria Gmbh Verfahren zum Wechseln eines Gleitlagerelementes einer Rotorlagerung einer Windkraftanlage, sowie Gondel für eine Windkraftanlage
AT521775B1 (de) 2018-12-13 2020-06-15 Miba Gleitlager Austria Gmbh Planetengetriebe für eine Windkraftanlage
AT521882B1 (de) 2018-12-13 2021-05-15 Miba Gleitlager Austria Gmbh Gleitlager, insbesondere für ein Getriebe einer Windkraftanlage

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1894952U (de) * 1961-08-08 1964-06-18 Eisenwerk Rothe Erde G M B H Waelzlager, insbesondere drahtkugellager mit leichtmetallringen.
DE2915088A1 (de) * 1979-04-12 1980-10-16 Industrieanlagen Betriebsges Lagerelement
EP1467111A2 (fr) * 2003-04-07 2004-10-13 Ab Skf Methode pour ajuster la prétension ou le jeu d'un palier
EP2306008A2 (fr) * 2009-09-30 2011-04-06 General Electric Company Palier pour le mouvement de lacet d'une éolienne et procédé pour le freinage du même mouvement
DE102011008958A1 (de) * 2011-01-19 2012-07-19 Imo Holding Gmbh Rotorlager für eine Windkraftanlage

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1894952U (de) * 1961-08-08 1964-06-18 Eisenwerk Rothe Erde G M B H Waelzlager, insbesondere drahtkugellager mit leichtmetallringen.
DE2915088A1 (de) * 1979-04-12 1980-10-16 Industrieanlagen Betriebsges Lagerelement
EP1467111A2 (fr) * 2003-04-07 2004-10-13 Ab Skf Methode pour ajuster la prétension ou le jeu d'un palier
EP2306008A2 (fr) * 2009-09-30 2011-04-06 General Electric Company Palier pour le mouvement de lacet d'une éolienne et procédé pour le freinage du même mouvement
DE102011008958A1 (de) * 2011-01-19 2012-07-19 Imo Holding Gmbh Rotorlager für eine Windkraftanlage

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9856910B2 (en) * 2015-11-30 2018-01-02 Roller Bearing Company Of America, Inc. Self-lubricated thrust bearing for a hinged aircraft wing
CN110799763A (zh) * 2017-06-29 2020-02-14 乌本产权有限公司 风能设备转动连接件和具有其的风能设备
US11698057B2 (en) 2017-06-29 2023-07-11 Wobben Properties Gmbh Wind turbine rotary connection, and wind turbine comprising same
US11644013B2 (en) 2019-05-21 2023-05-09 Miba Gleitlager Austria Gmbh Nacelle for a wind turbine

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