WO2015150159A1 - Ensemble palier à roulement et éolienne - Google Patents

Ensemble palier à roulement et éolienne Download PDF

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Publication number
WO2015150159A1
WO2015150159A1 PCT/EP2015/056218 EP2015056218W WO2015150159A1 WO 2015150159 A1 WO2015150159 A1 WO 2015150159A1 EP 2015056218 W EP2015056218 W EP 2015056218W WO 2015150159 A1 WO2015150159 A1 WO 2015150159A1
Authority
WO
WIPO (PCT)
Prior art keywords
rolling
rolling elements
rotation
axis
inner ring
Prior art date
Application number
PCT/EP2015/056218
Other languages
German (de)
English (en)
Inventor
Stefan Löffler
Jan-Peter BOCHERT
Thomas HANDRECK
Bernd LÜNEBURG
Original Assignee
Thyssenkrupp Rothe Erde Gmbh
Thyssenkrupp Ag
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Thyssenkrupp Rothe Erde Gmbh, Thyssenkrupp Ag filed Critical Thyssenkrupp Rothe Erde Gmbh
Priority to CN201590000687.7U priority Critical patent/CN207621175U/zh
Publication of WO2015150159A1 publication Critical patent/WO2015150159A1/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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/50—Other types of ball or roller bearings
    • F16C19/505—Other types of ball or roller bearings with the diameter of the rolling elements of one row differing from the diameter of those of another row
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65D—CONTAINERS FOR STORAGE OR TRANSPORT OF ARTICLES OR MATERIALS, e.g. BAGS, BARRELS, BOTTLES, BOXES, CANS, CARTONS, CRATES, DRUMS, JARS, TANKS, HOPPERS, FORWARDING CONTAINERS; ACCESSORIES, CLOSURES, OR FITTINGS THEREFOR; PACKAGING ELEMENTS; PACKAGES
    • B65D88/00—Large containers
    • B65D88/02—Large containers rigid
    • B65D88/12—Large containers rigid specially adapted for transport
    • B65D88/128—Large containers rigid specially adapted for transport tank containers, i.e. containers provided with supporting devices for handling
    • 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
    • F16C19/383—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 tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—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 tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—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 tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • 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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • F16C33/366—Tapered rollers, i.e. rollers generally shaped as truncated cones
    • 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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/30—Angles, e.g. inclinations
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/30—Angles, e.g. inclinations
    • F16C2240/34—Contact angles
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii
    • 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
    • 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 is based on a roller bearing assembly according to the preamble of claim 1.
  • Such rolling bearing arrangements are well known from the prior art and are used for example in the form of so-called large rolling bearings for supporting the rotor shaft of a wind turbine.
  • Wind turbines usually have a tower and a rotatably mounted on the tower and acting as a machine carrier nacelle.
  • the arranged in the nacelle rotor shaft is at one end with a
  • Rotor hub connected, which carries the wind-driven rotor blades, while the other end is coupled via a possible transmission directly or indirectly with a generator for generating electricity.
  • tapeered roller bearings disadvantageously unevenly loaded and therefore use unevenly. Furthermore, the dimensioning of the tapered roller bearings is always based on the highest expected forces, so that one of the two bearings is unnecessarily oversized. Disclosure of the invention
  • a needs-based dimensioning of the bearings should be made possible in order to optimize the overall costs for the rolling bearing assembly.
  • a rolling bearing assembly for a wind turbine having an outer ring and a relative to the outer ring rotatable about an axis inner ring, wherein between the outer ring and the inner ring, a first tapered roller bearing with first rolling elements and a second tapered roller bearing are formed with second rolling elements, wherein the Rotary axes of the first and second rolling elements relative to the axis of rotation are each aligned inclined and wherein the first and second tapered roller bearings are formed asymmetrically.
  • the rolling bearing assembly according to the invention has the advantage over the prior art that the two tapered roller bearings are designed differently and thus can be adapted to the wind turbines occurring in uneven loads.
  • tapered roller bearing which is arranged closer to the rotor blades provided with rotor, dimensioned larger and thus more loadable, as the other tapered roller bearing, which is located closer to the generator.
  • this other tapered roller bearing can be made smaller, which advantageously reduce the total cost of the rolling bearing assembly.
  • both the inner ring and the outer ring can be rotatable, i. the outer ring may also be rotatable relative to the inner ring about the axis of rotation.
  • the first rolling elements respectively rotate about a first axis of rotation and have a first tread concentrically arranged about the first axis of rotation and wherein the second rolling elements respectively rotate about a second axis of rotation and concentrically arranged about the second axis of rotation
  • the extension of the first tread parallel to the first axis of rotation is greater than the extension of the second tread parallel to the second axis of rotation.
  • the load capacity of the first tapered roller bearing compared to the second tapered roller bearing increased by the first treads are widened. In this way, the tilting forces typically occurring in a wind turbine can better from the first tapered roller bearing
  • the extension of the first tread is by 1, 1 to 2.0 times, preferably by 1, 1 to 1, 5 times, and more preferably by 1, 1 to 1, 3 times greater than that Extension of the second tread is.
  • the nominal diameter of the first rolling elements is greater than the nominal diameter of the second rolling elements.
  • the load capacity of the first tapered roller bearing can also be achieved by increasing the nominal diameter of the first rolling elements in comparison with the second rolling elements.
  • the nominal diameter of a rolling element is, in particular, that diameter which the rolling element has in its geometric center, i. in particular the center of the tread along its axis of rotation.
  • the nominal diameter of the first rolling elements between 36 and 180 millimeters, preferably between 80 and 160 millimeters and more preferably between 120 and 140 millimeters, while the nominal diameter of the second rolling elements between 36 and 180 millimeters, preferably between 80 and 160 millimeters and more preferably between 120 and 140 millimeters.
  • first angle between the rotation axis and the first rolling elements always a first angle is formed and wherein between the rotation axis and the second rolling elements always a second angle is formed, wherein the first angle is smaller than the second angle .
  • the flatter first angle provides greater radial load bearing capacity on the first tapered roller bearing, while the steeper second angle provides better axial force absorption on the second tapered roller bearing.
  • the first angle is between 30 and 60 degrees, preferably between 30 and 50 degrees and particularly preferably between 30 and 40 degrees, while the second angle is between 40 and 90 degrees, preferably between 50 and 85 degrees and particularly preferably between 60 and 85 degrees.
  • the outer ring has a first outer race, on which run the first rolling elements, and a second outer race, on which the second rolling elements run, wherein the outer ring has a wedge-shaped projecting in the direction of the axis of rotation
  • first and second outer raceway are formed on a single one-piece ring segment.
  • the formation of the first and second outer race on a single one-piece ring segment makes it possible for the rolling element arrangement to be realized in a particularly space-saving and cost-effective manner.
  • the axial and radial forces are introduced directly into the bilaterally supported ring segment, resulting in a particularly tamper-proof, torsionally rigid and stable storage.
  • the outer ring is for this purpose in particular integrally formed.
  • the inner ring is formed in several parts from a first inner part and a second inner ring part.
  • the inner ring has a first inner race, on which run the first rolling elements, and a second inner race, on which the second
  • Run off rolling elements on, wherein on the first inner ring part, the first inner raceway and on the second inner ring part, the second inner raceway is formed.
  • the two-part design of the inner ring allows advantageously a simple and quick installation of the rolling element, whereby the manufacturing costs can be further reduced.
  • a shoulder is made for a shoulder to be formed on the inner ring between the first inner raceway and the second inner raceway. It has surprisingly been found that the distribution of lubricant between the first and the second inner raceway can be optimized by the heel and thus always a reliable lubrication of the first and second rolling elements is ensured.
  • the first and second rolling elements are each received in cages and at least one recess on a surface of the inner ring facing the cages
  • the recess offers the advantage that lubricant collects within the recess and thus always a reliable lubrication between the cage and inner ring is guaranteed. Basically also conceivable that in the field of cages on the outer ring a corresponding
  • Another object of the present invention is a wind turbine comprising a rotor hub with a plurality of rotor blades, wherein the rotor hub rotatably with a
  • Rotor shaft is connected and wherein the rotor shaft is coupled directly or indirectly with a generator, wherein the wind turbine has a bearing assembly for supporting the rotor shaft and wherein the bearing assembly comprises the rolling bearing assembly according to the invention.
  • the wind turbine can be realized relatively inexpensively due to the use of the rolling bearing assembly according to the invention.
  • Figure 1 shows a schematic sectional view of a rolling bearing assembly according to an exemplary first embodiment of the present invention.
  • FIG. 2 is a schematic sectional view of a rolling bearing assembly according to an exemplary second embodiment of the present invention.
  • FIG. 3 is a schematic sectional view of a rolling bearing assembly according to an exemplary third embodiment of the present invention.
  • FIG. 1 is a schematic sectional view of a rolling bearing assembly 1 according to an exemplary embodiment of the present invention.
  • the rolling bearing assembly 1 has an outer ring 2 and an inner ring 3.
  • the inner ring 3 is rotatably mounted about an axis of rotation 24 relative to the outer ring 2.
  • Rolling bearing assembly 1 is for this purpose formed in two rows and has two tapered roller bearings, a first tapered roller bearing 4 and a second tapered roller bearing 6.
  • the first tapered roller bearing 4 comprises a plurality of first rolling elements 5, each of which rotates about its longitudinal axis, referred to herein as the first axes of rotation 12.
  • Each first rolling body 5 has a circumferential first tread 14, which as
  • the first rolling element 5 is in each case formed in the shape of a truncated cone so that its diameter changes along the first axis of rotation 12.
  • the first rolling elements 5 are arranged between the outer ring 2 and the inner ring 3 and run with their first running surfaces 14 in each case on a formed on the outer ring 2 circumferential first outer raceway 8 and a formed on the inner ring 3 circumferential first inner race 16.
  • the first axis of rotation 12 is in each case inclined relative to the axis of rotation 24 by a first angle 10, so both along the axis of rotation 24 acting axial forces, as well as perpendicular to
  • Rotation axis 24 acting radial forces can be absorbed by the first tapered roller bearing 4.
  • the second tapered roller bearing 6 comprises a plurality of second rolling elements 7, which likewise each rotate about their longitudinal axes, referred to as second axes of rotation 13.
  • the second rolling elements 7 each have circumferential second running surfaces 15, which extends around the second rotation axis 13 as a concentric lateral surface.
  • Analogous to the first rolling elements 5 and the second rolling elements 7 are frustoconical, so that their diameter changes along the second axis of rotation 13.
  • the outer ring 2 in addition to the first outer race 8 further comprises a circumferential second outer raceway 9 and the inner ring 3 in addition to the first inner race 16 further comprises a circumferential second inner raceway 17, between which the second rolling elements 7 are arranged and soft on the second rolling elements 7 with their second Running surfaces 15 each expire.
  • the second axis of rotation 13 is also in each case inclined with respect to the axis of rotation 24 by a second angle 1 1, so both along the axis of rotation 24 acting axial forces, as well as perpendicular to the axis of rotation 24 acting radial forces can also be absorbed by the second tapered roller bearing 6.
  • the first and second rolling elements 5, 7 are each received in cages 25.
  • the present rolling bearing assembly 1 is provided for supporting a rotor shaft of a wind turbine not shown.
  • the rotor shaft extends
  • first and second tapered roller bearings 4, 6 are thus unequally loaded. To accommodate this unequal load, the first and second tapered roller bearings 4, 6 are designed asymmetrically, ie, the first and second tapered roller bearings 4,
  • first tapered roller bearing 4 is the one bearing closer to the rotor hub, while the second tapered roller bearing 6 is the bearing closer to the generator, the tilting forces in the region of the first tapered roller bearing 4 cause a higher one
  • the first angle 10 is therefore smaller than the second angle 1 to 1 at the first tapered roller bearing 4 increasingly accumulating radial forces acting perpendicular to the axis of rotation 24 to record.
  • the first angle 10 is for example between 30 and 40 degrees, while the second angle 1 1 could for example be between 60 and 85 degrees.
  • the first rolling elements 5 are formed larger than the second rolling elements 7, i.
  • the first rolling elements 5 have in comparison to the second rolling elements 7 each have both a larger nominal diameter, and a wider tread. It is conceivable, for example, that the nominal diameter of the second rolling elements 7 is only between 50 and 90 millimeters, while the nominal diameter of the first rolling elements 5 is between 120 and 140 millimeters. It would also be conceivable that the extension of the first running surface 14 along the associated first rotation axis 12 is in each case 1, 1 to 1, 3 times the extent of the second running surface 15 along the associated second rotation axis 13.
  • the outer ring 2 is designed in one piece such that the outer ring 2 has a wedge-shaped in the direction of the rotation axis 24 projecting circumferential ring segment 23 with two wedge flanks 20, 21, wherein on the one wedge edge 20, the first outer race 8 and on the other Wedge edge 21, the second outer race 9 is formed.
  • the first and second outer race 8, 9 are thus arranged on the wedge flanks 20, 21 of the ring segment 23 extremely space-compact, between the first and second outer race 8, 9 only the tip of the wedge-shaped ring segment is arranged.
  • the inner ring 3 is preferably formed in two parts from a first inner ring part 18 and a second inner ring part 19.
  • the first inner race 16 is at the first
  • Inner ring member 18 is formed and the second inner race 17 is on the second
  • Inner ring part 19 is formed.
  • a shoulder 22 is formed between the first and second inner races 16, 17.
  • FIG. 2 is a schematic sectional view of a rolling bearing assembly 1 according to an exemplary second embodiment of the present invention, wherein the rolling bearing assembly 1 according to the second embodiment of the rolling bearing assembly 1 according to the illustrated in Figure 1 first embodiment is similar, in contrast, the rolling bearing assembly 1 according to the second Embodiment has no shoulder 22 and the inner ring 3 each recesses 26 are formed in which the contact surfaces of the cages 25 of the first and second rolling elements 5, 7 run.
  • the recesses 26 ensure that lubricant collects in the region of the cages 25 and always ensure adequate lubrication between the cages 25 and the inner ring 3.
  • FIG. 3 is a schematic sectional view of a rolling bearing assembly 1 according to an exemplary third embodiment of the present invention, wherein the rolling bearing assembly 1 according to the third embodiment is a hybrid of FIG
  • Rolling bearing assembly 1 according to the illustrated in Figure 1 first embodiment and the rolling bearing assembly according to the second embodiment illustrated in Figure 2.
  • the rolling bearing assembly 1 according to the third embodiment therefore has both the shoulder 22, and depressions 26 on the inner ring 3, in which the contact surfaces of the cages 25 of the first and second rolling elements 5, 7 run.

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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

L'invention concerne un ensemble palier à roulement (1) pour une éolienne, qui présente une bague extérieure (2) et une bague intérieure (3), celle-ci pouvant tourner autour d'un axe de rotation (24), relativement à la bague extérieure, un premier roulement à rouleaux coniques (4) doté de premiers corps roulants (5) et un second roulement à rouleaux coniques (6) doté de seconds corps roulants (7) étant agencés entre la bague extérieure et la bague intérieure, les axes de rotation (12, 13) des premier et second corps de roulement étant dans chaque cas orientés inclinés par rapport à l'axe de rotation et le premier et le second roulement à rouleaux coniques étant conçus de manière asymétrique.
PCT/EP2015/056218 2014-04-04 2015-03-24 Ensemble palier à roulement et éolienne WO2015150159A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201590000687.7U CN207621175U (zh) 2014-04-04 2015-03-24 滚动轴承装置和风力发电设备

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014104862.8A DE102014104862A1 (de) 2014-04-04 2014-04-04 Wälzlageranordnung und Windkraftanlage
DE102014104862.8 2014-04-04

Publications (1)

Publication Number Publication Date
WO2015150159A1 true WO2015150159A1 (fr) 2015-10-08

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Application Number Title Priority Date Filing Date
PCT/EP2015/056218 WO2015150159A1 (fr) 2014-04-04 2015-03-24 Ensemble palier à roulement et éolienne

Country Status (3)

Country Link
CN (1) CN207621175U (fr)
DE (2) DE102014104862A1 (fr)
WO (1) WO2015150159A1 (fr)

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DE102016201955A1 (de) * 2016-02-10 2017-08-10 Schaeffler Technologies AG & Co. KG Reibungsarmes Kegelrollenlager
DE102017106962A1 (de) 2017-03-31 2018-10-04 Thyssenkrupp Ag Wälzlageranordnung und Windkraftanlage
DE102017008877A1 (de) 2017-09-21 2019-03-21 Imo Holding Gmbh Schrägrollenlager
DE102017128951A1 (de) * 2017-12-06 2019-06-06 Thyssenkrupp Ag Wälzlageranordnung und Verfahren
DE202018100216U1 (de) * 2018-01-16 2019-04-17 Liebherr-Components Biberach Gmbh Mehrreihiges Wälzlager
DE102018213951A1 (de) * 2018-08-17 2020-02-20 Thyssenkrupp Ag Wälzkörper mit asymmetrischer Rollenprofilierung, Wälzlager, Windkraftanlage und Verfahren zur geometrischen Dimensionierung von Wälzkörpern
DE102019106276A1 (de) 2019-03-12 2020-09-17 Schaeffler Technologies AG & Co. KG Rotorlagerung einer Windkraftanlage Technisches Gebiet
DE102020131335A1 (de) 2020-11-26 2022-06-02 Thyssenkrupp Ag Wälzlager
DE102022200534A1 (de) 2022-01-18 2023-08-03 Thyssenkrupp Ag Belastungsoptimierte Großwälzlageranordnung

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