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WO2017025343A1 - Ensemble de paliers à roulement et palier de pale pour éolienne - Google Patents

Ensemble de paliers à roulement et palier de pale pour éolienne Download PDF

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Publication number
WO2017025343A1
WO2017025343A1 PCT/EP2016/068032 EP2016068032W WO2017025343A1 WO 2017025343 A1 WO2017025343 A1 WO 2017025343A1 EP 2016068032 W EP2016068032 W EP 2016068032W WO 2017025343 A1 WO2017025343 A1 WO 2017025343A1
Authority
WO
WIPO (PCT)
Prior art keywords
cross
cross roller
roller bearing
rollers
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.)
Ceased
Application number
PCT/EP2016/068032
Other languages
German (de)
English (en)
Inventor
Gunther Elfert
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.)
ThyssenKrupp AG
ThyssenKrupp Rothe Erde Germany GmbH
Original Assignee
ThyssenKrupp AG
ThyssenKrupp Rothe Erde 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 ThyssenKrupp AG, ThyssenKrupp Rothe Erde GmbH filed Critical ThyssenKrupp AG
Publication of WO2017025343A1 publication Critical patent/WO2017025343A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F03D1/00—Wind motors with rotation axis substantially parallel to the air flow entering the rotor 
    • F03D1/06—Rotors
    • F03D1/065—Rotors characterised by their construction elements
    • F03D1/0658—Arrangements for fixing wind-engaging parts to a hub
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • 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
    • F05B2240/00—Components
    • F05B2240/50—Bearings
    • F05B2240/52—Axial thrust bearings
    • 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
    • F05B2240/00—Components
    • F05B2240/50—Bearings
    • F05B2240/54—Radial bearings
    • 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
    • F05B2260/70—Adjusting of angle of incidence or attack of rotating blades
    • F05B2260/79—Bearing, support or actuation arrangements therefor
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/381—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with at least one row for radial load in combination with at least one row for 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
    • F16C2360/00—Engines or pumps
    • F16C2360/31—Wind motors
    • 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 invention relates to a rolling bearing assembly and a blade bearing for a wind turbine.
  • Doppelvierddlinglager are usually used as standard blade bearings to meet the occurring relatively high radial and axial forces.
  • Roll-up connections are also known from the prior art, the use of which proves to be problematic in that a relative movement of the rings due to an elastic deformation, especially at a standstill, leads to a standstill wear ("false brinelling").
  • It is an object of the present invention to provide a rolling bearing assembly provide that has a relatively high load capacity against axial and radial forces and also in a simple and flexible manner to different requirements, in particular with regard to the proportions of axial and radial forces adaptable. In this way, the requirement profile applicable to a particular wind turbine should always be met.
  • the present invention solves the problem by a rolling bearing assembly for a wind turbine, in particular for a blade bearing of the wind turbine, comprising an inner ring and a relative to the inner ring about an axis rotatable outer ring, wherein the rolling bearing assembly comprises a first cross roller bearing and a second cross roller bearing, wherein both the first Cross roller bearing and the second cross roller bearing between the inner ring and the outer ring arranged cross rollers such that in each case the axis of rotation of at least one axially aligned cross roller parallel to the axis of rotation and the axis of rotation of at least one radially oriented cross roller perpendicular to the axis of rotation.
  • the present invention by the implementation of the first and second cross roller bearing has the advantage that their cross rollers lie flat against the inner ring or outer ring and the plant is not concentrated on a point contact, as occurs for example in four-point bearings, but extends over a line contact. Accordingly, a contact pressure between a tread associated with the raceway and the cross roller is reduced, whereupon the load for the rolling bearing assembly decreases over the operating time and correspondingly advantageously increases the service life.
  • the cross roller bearings while both axially and radially extending loads are absorbed.
  • a third radial track can be saved so that the bearing arrangement according to the invention can be realized more cost-effectively and / or more compactly than the prior art.
  • a greater compactness advantageously also allows the use of larger cross rollers and thus an increase in the load capacity.
  • Another advantage is that by the appropriate arrangement of the cross rollers in a simple manner, a load adjustment can be done by depending on the expected radial and axial forces more or less cross rollers are aligned in the axial or radial direction.
  • the raceways comprise running surfaces, which are arranged on an outer side of the inner ring and / or on an inner side of the outer ring and roll on which cross rollers of the first and / or second cross roller bearing.
  • the treads are hardened and adapted to the lateral surfaces of the cross rollers.
  • separating elements between individual cross rollers are arranged in the rolling bearing.
  • the rolling bearing comprises as separating elements, for example intermediate pieces.
  • the cross rollers have a rotational symmetry axis, wherein the cross rollers, in particular completely, are rotationally symmetrical to the rotational symmetry axis. The rotational symmetry axis determines the orientation of the respective cross roller.
  • Cross rollers are preferably arranged in a cross roller bearing, whose orientations are perpendicular to each other and alternate, for example in the circumferential direction.
  • the arrangement at 90 ° angles compared to known cross roller bearings with 45 ° angles has the advantage that no additional radial forces are generated.
  • the cross roller are assigned to a parallel to the rotational axis of symmetry extending height and a perpendicular to the rotational axis of symmetry diameter, wherein the height and the diameter are substantially equal.
  • the height of the cross roller substantially corresponds to a maximum diameter when the diameter of the cross roller changes along the rotational symmetry axis.
  • the cross roller is a cylindrical cross roller whose height and diameter substantially correspond to each other.
  • first cross roller bearing and the second cross roller bearing are arranged offset from one another along the axis of rotation. Due to the distance between the first cross roller bearing and the second cross roller bearing, the rolling bearing assembly can be further adjusted in terms of expected loads.
  • first and the second crossed roller bearings are arranged congruently to one another.
  • first and the second cross roller bearings differ in their diameter and preferably in the axial direction, d. H. are arranged along a direction parallel to the axis of rotation extending direction, seen concentrically with each other.
  • the first cross roller bearing and / or the second cross roller bearing cross rollers which are profiled on its front side and / or its shell side comprises.
  • cross rollers without profiling and cross rollers with profiling are arranged in the same cross roller bearing is arranged in a cross roller bearing whose running surface is provided for cross rollers without profiling, ie running surfaces without curvature.
  • the profiling advantageously decreases the edge tension, since the ends are rounded s cylindrical roller formed with a rolling element diameter D w , wherein the depth of the profiling is preferably at least 5%, more preferably at least 10% and most preferably at least 15% of the rolling element diameter D w .
  • the first cross roller bearing and / or the second cross roller bearing comprises a radially oriented cross roller and an axially oriented cross roller. It is provided that the axis of rotation of the axially oriented cross roller extends substantially parallel to the axis of rotation of the rolling bearing assembly and that the axis of rotation of the radially oriented cross roller extends substantially perpendicular to the axis of rotation of the rolling bearing assembly. In particular, it is provided that a numerical ratio of axially aligned cross rollers and radially oriented cross rollers is matched with a requirement profile for the rolling bearing assembly.
  • the first cross roller bearing comprises n times as many, in particular twice as many, radially oriented cross rollers as axially oriented cross rollers.
  • the load capacity can be controlled depending on the expected load. It is conceivable that in the first cross roller bearing more vertically oriented cross rollers are arranged as in the second cross roller bearing.
  • the cross rollers have a front side cover, in particular in the form of a wear protection element, for example a sliding cap.
  • the cover is disposed on a side surface through which the rotational symmetry axis passes. It is conceivable that the cover is arranged in a recess of a base body of the cross roller and is positively connected to the base body, frictionally engaged and / or cohesively.
  • the cover comprises a plastic, such as peak or POM, or is made entirely of plastic.
  • the cover made of polyamide and in particular of polyamide 12 PA 12: laurolactam or ⁇ -aminododecanoic acid), PTFE and / or Teflon is made. It has surprisingly been found that the longevity and resilience of the respective cross roller bearing can be increased due to the high strength and toughness of polyamide advantageously by the use of polyamide, PTFE or Teflon.
  • the cover is made of a metal which is softer than a metal of the main body of the cross roller, wherein the cover preferably comprises bronze. It would also be conceivable that the cover is made of brass or a ceramic. It is also conceivable that the cover also has a profiling or a structure. Through the use of the cover can be advantageously avoided by a frontal steel-steel contact between cross roller and inner ring or outer ring wear.
  • the main body of the cross roller has a recess on its end face.
  • This recess which is formed, for example, in the form of a flat blind bore extending parallel to the rotational symmetry axis of the cross roller, serves to fasten the cover to the cross roller.
  • the cover element on its side facing the front side is positively and / or non-positively disposed within the recess or the cover has on its side facing the front side a bulge, which is positively and / or non-positively disposed within the recess.
  • the cover is inserted over its entire cross-roll width facing within the recess, while in the second case, only the bulge is inserted within the recess.
  • the main body of the cross roller on its front side has a central bulge, which is arranged positively and / or non-positively in an opening of the cover.
  • the opening comprises either a blind hole or a through hole.
  • the main body of the cross roller on its front side comprises a protruding, circumferential ring which extends along the circumference of the tread. Between the circumferential ring and the central bulge thus a circumferential groove is formed, in which the annular cover is arranged. In this way, preferably a stable and resilient positive connection of the cover is achieved on the main body of the cross roller.
  • a running surface associated with the running surface is designed corresponding to the shell side and / or the end face of one of the cross rollers.
  • the tread is designed to match the curvature of the shell side or front side of the cross roller.
  • the tread varies along an axially extending direction.
  • the tread is concavely curved, wherein a radius of curvature of the concave curvature of the tread corresponds approximately to the radius of curvature of the curvature on the front or shell side of the cross roller.
  • a first or second cross roller bearing with a curved tread comprises a cross roller without profiling. It is also conceivable that the tread is designed such that it forms a point contact together with one of the cross rollers, in particular one of the Toroidal- roles, whereby a targeted higher resistance to a stall wear can be achieved.
  • the inner ring and / or the outer ring are formed in several parts.
  • the assembly of the first and the second cross roller bearing can be simplified.
  • the individual parts of the multi-part inner ring or outer ring can each be assigned to a cross roller bearing. This makes it possible in an advantageous manner, in each case - for example, by removing the corresponding part - to obtain access to the individual cross roller bearing, there z.
  • the inner ring has a projection on one side of a raceway for cross rollers of the first cross roller bearing is formed and on the other side of a raceway for cross rollers of the second cross roller bearing is formed.
  • the extension of the projection parallel to the axis of rotation from the track on one side to the track on the other side, is preferably between 0.8 and 1.4 times and more preferably between the 1, 0 and 1, 2 times the WälzSystem devismessers D w . It has been found that a particularly stable and at the same time compact rolling element arrangement can be realized with this geometric relationship.
  • the first and / or second cross roller bearing comprises a track in which a group of cross rollers is arranged, wherein the group comprises at least two juxtaposed radially oriented cross rollers and at least one axially oriented cross roller along the career at least two such groups are arranged one behind the other.
  • the first and / or second bearing can be adapted to larger radial loads by simply always providing at least two successive radially oriented cross rollers.
  • a deviation from the group arrangement can only take place at an "interface" if an integral multiple of the groups does not fit into the bearing due to the tree.
  • the first and / or second cross roller bearing has a raceway in which a group of cross rollers is arranged, the group comprising at least two juxtaposed axially oriented cross rollers and at least one radially oriented cross roller (2). comprises, along the track at least two such groups are arranged one behind the other.
  • the first and / or second bearing can be adapted to larger axial loads by simply always at least two successive radially oriented cross rollers are provided. Only at an "interface" can a deviation from the group arrangement take place, if an integral multiple of the groups does not fit into the warehouse due to space constraints.
  • the first cross roller bearing optionally has a group arrangement with in each case at least two successive axial cross rollers, while the second cross roller bearing has a group arrangement with at least two successive radial cross rollers.
  • the first and the second cross roller bearings are symmetrical to each other.
  • the rolling bearing arrangement according to the invention gives the person skilled in particular the possibility of adapting the first and second cross roller bearings individually and flexibly to the expected forces. If higher axial forces are to be expected, more axially oriented cross rollers are used, while more radially oriented cross rollers are used when higher radial forces are to be expected. It is also conceivable that the rolling bearing assembly is formed such that exactly one integer multiple of a group is arranged in the raceway of the first and / or second cross roller bearing. Basically, can be carried out by the appropriate arrangement of the cross rollers in a simple manner, a load adjustment by depending on the expected radial and axial forces more or less cross rollers are aligned in the axial or radial direction.
  • the cross rollers have a diameter between 30 mm and 90 mm, preferably between 50 mm and 70 mm and particularly preferably about 60 mm.
  • Another object of the present invention is a blade bearing for a wind turbine having a rolling bearing assembly according to the invention.
  • the blade bearing according to the invention has the advantage of a rolling bearing assembly, with which instead of a point contact between cross roller and inner ring or outer ring adjusts a line contact.
  • the contact pressure is lowered, without the capacity or the space taken is impaired.
  • the multi-row configuration of the rolling bearing assembly and on the geometric configuration of the cross rollers it is possible in an advantageous manner to adjust the load capacity of the rolling bearing assembly to the requirements profile of the blade bearing of the wind turbine.
  • FIG. 1 shows a rolling bearing assembly according to a first exemplary embodiment of the present invention.
  • FIG. 2 shows a rolling bearing arrangement according to a second exemplary embodiment of the present invention.
  • 3 shows an exemplary cross roller for a rolling bearing assembly according to the present invention.
  • FIG. 4 shows a rolling bearing arrangement according to a third exemplary embodiment of the present invention.
  • the rolling bearing assembly 1 shows a rolling bearing assembly 1 according to a first exemplary embodiment of the present invention.
  • the rolling bearing assembly 1 comprises an inner ring 1 1 and a relative to the inner ring 1 1 about an axis of rotation D rotatable outer ring 12.
  • the rolling bearing assembly 1 comprises a first cross roller bearing and a second cross roller bearing. Both cross rollers 2 of the first cross roller bearing 10 'and cross rollers 2 of the second cross roller bearing 10 "are arranged between the inner ring 11 and the outer ring 12.
  • the first cross roller bearing 10' and the second cross roller bearing 10" respectively face the inner ring 11 and the outer ring 12 trained raceways, wherein the cross rollers 2 of the first and second cross roller bearing 10 'and 10 "roll on raceways 3 of the raceways on the outer ring 12 and inner ring 1. 1. Furthermore, the first and the second cross roller bearings 10' and 10" next the cross rollers 2 preferably separating elements, such as spacers, with the cross rollers 2 are held at a distance from each other. In the arrows drawn in the figures are effective directions of the cross rollers 2 at loads of the rolling bearing assembly 1.
  • the rolling bearing assembly 1 is a rolling bearing assembly 1 for a sheet storage, which is provided for example in a wind turbine with rotor blades as a rotor blade bearing.
  • the rolling bearing assemblies 1 must withstand high loads and be used as long as possible maintenance-free.
  • the first cross roller bearing 10 'and the second cross roller bearing 10 "are offset from each other in the axial direction and in the axial direction arranged congruent to each other.
  • cross rollers 2 'without profiling are cross rollers 2 'without profiling.
  • cross rollers Compared with the four-point bearings used in the prior art with their spherical rolling elements, the use of cross rollers has the advantage that a Point contact and a concomitant relatively high contact pressure of the cross roll on the track can be avoided. Instead, arises in an advantageous manner in a cross roller 2 line contact.
  • the cross rollers 2 can also absorb axially and radially directed loads.
  • the cross rollers 2 are designed as a cylinder, on the front side covers 4, for example, sliding elements in the form of sliding caps, are provided to reduce by means of the sliding elements an undesired friction of the respective end face with the inner ring 1 1 and the outer ring 12 and a To avoid frontal wear by a steel-steel contact between the tread 3 and cross roller 2.
  • each cross rollers 2 each comprise an axis of rotation about which the cross roller 2 is rotationally symmetrical.
  • the orientation of the respective cross roller 2 can be defined or defined.
  • the cross roller 2 is aligned axially or radially.
  • the cross roller 2 in the first cross roller bearing 10 ' is radial, since the axis of rotation of the cross roller 2 is aligned perpendicular to the axis of rotation D, and the cross roller 2 in the second cross roller bearing 10 "axially aligned, since the axis of rotation of the cross roller 2 parallel to
  • the cross rollers 2 of the first and second cross roller bearings 10 'and 10 are preferably located on one, in particular the same, projection 8 of the inner ring 11.
  • the outer ring 12 is designed in two parts in order to simplify the assembly of the outer ring 12 and the rolling bearing assembly 1.
  • a height of the cross roller 2 substantially corresponds to a diameter of the cross roller 2.
  • the cross rollers have a diameter between 30 mm and 90 mm, preferably between 50 mm and 70 mm and particularly preferably about 60 mm.
  • the rolling bearing assembly of the second exemplary embodiment comprises cross rollers 2 with profiling, preferably with profiled lateral surfaces.
  • the cross roller 2 here is a Toroidalrolle.
  • the running surfaces 3 of the raceways on the inner ring 1 1 and outer ring 12, particularly preferably concave, are curved, in particular corresponding to a curvature of a shell side of the Toroidalrolle are curved.
  • the contact surface between the running surfaces 3 and the cross rollers 2 or the line contact in an advantageous manner can be further increased.
  • the rolling bearing assembly 1 seals 6, which preferably seal a gap between the inner ring 1 1 and the outer ring 12.
  • via holes 5 lubricant for the first and / or the second cross roller bearing 10 'and / or 10 "in the rolling bearing assembly 1 can be introduced.
  • FIG. 3 shows an exemplary cross roller 2 for a roller bearing assembly 1 according to the present invention.
  • a cross roller 2 in the first embodiment is part of the cross roller bearing.
  • the cross roller 2 shown here comprises, in addition to the cylindrical base body 7, a cover 4 at the front side.
  • These covers 4 are embedded in recesses provided on the end faces of the main body and screwed, riveted, welded or clipped to the base body 7, for example.
  • the cover 4 forms an edge of the cross roller 2 and / or that the cover is made of a plastic.
  • the first or second cross roller bearing 10 ', 10 "of a rolling bearing assembly 1 according to a third exemplary embodiment of the present invention is shown in a perspective view, provided that the cross rollers 2 in the respective cross roller bearing 10', 10" both axially and are arranged radially.
  • cross roller bearing 10 ', 10 has a raceway in which a plurality of successively arranged groups 9 is arranged with three cross rollers 2.
  • Each group 9 has two juxtaposed radially oriented cross rollers 2 and next to an axially oriented cross roller 2. It is provided that a separating element 13 is arranged between each two crossed rollers 2.
  • the separating element 13 is adapted to the cross rollers 2 to be separated or axially aligned cross rollers 2, a different separating element 13 is arranged than between an axially and a radially oriented cross roller 2 and 2 which are adjacently
  • the separating elements 13 are designed such that they at least partially surround the lateral surfaces of the adjacent cross roller 2 or along the lateral surface n partially extend. LIST OF REFERENCE NUMBERS

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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)
  • Rolling Contact Bearings (AREA)

Abstract

La présente invention propose un ensemble de palier à roulement (1), destiné à une éolienne, en particulier à un palier de pale, qui comprend une bague intérieure (11) et une bague extérieure (12) rotative sur un axe de rotation (D) par rapport à la bague intérieure (11). L'ensemble de palier à roulement (1) comprend un premier palier à rouleaux croisés (10') et un second palier à rouleaux croisés (1''). Le premier palier à rouleaux croisés (10') et le second palier à rouleaux croisés (10'') comportent des rouleaux croisés (2) disposés entre la bague intérieure (11) et la bague extérieure (12) de telle sorte que l'axe de rotation d'au moins un rouleau croisé (2) orienté axialement s'étend parallèlement à l'axe de rotation (D) et l'axe de rotation d'au moins un rouleau croisé (2) orienté radialement s'étend perpendiculairement à l'axe de rotation (D).
PCT/EP2016/068032 2015-08-07 2016-07-28 Ensemble de paliers à roulement et palier de pale pour éolienne Ceased WO2017025343A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015113100.5A DE102015113100A1 (de) 2015-08-07 2015-08-07 Wälzlageranordnung und Blattlager für eine Windkraftanlage
DE102015113100.5 2015-08-07

Publications (1)

Publication Number Publication Date
WO2017025343A1 true WO2017025343A1 (fr) 2017-02-16

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2016/068032 Ceased WO2017025343A1 (fr) 2015-08-07 2016-07-28 Ensemble de paliers à roulement et palier de pale pour éolienne

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DE (1) DE102015113100A1 (fr)
WO (1) WO2017025343A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
ES2761321A1 (es) * 2018-11-15 2020-05-19 Laulagun Bearings Sl Rodamiento de rodillos
CN114810950A (zh) * 2021-01-27 2022-07-29 宁波瀚晟传动技术有限公司 内啮合传动机构

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202017000692U1 (de) * 2017-02-08 2018-05-09 Liebherr-Components Biberach Gmbh Mehrreihiges Großwälzlager
DE102018216252A1 (de) * 2018-09-24 2020-03-26 RS Schwarze Elektrotechnik Moderne Industrieelektronik GmbH Wälzkörper mit integrierter Elektronik zur Verwendung in einem Wälzlager
DE202019101697U1 (de) * 2019-03-26 2020-07-02 Liebherr-Components Biberach Gmbh Großwälzlager

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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