WO2015176769A1 - Partie d'éolienne - Google Patents

Partie d'éolienne Download PDF

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Publication number
WO2015176769A1
WO2015176769A1 PCT/EP2014/060641 EP2014060641W WO2015176769A1 WO 2015176769 A1 WO2015176769 A1 WO 2015176769A1 EP 2014060641 W EP2014060641 W EP 2014060641W WO 2015176769 A1 WO2015176769 A1 WO 2015176769A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
ring
rotor
bearing ring
wind turbine
Prior art date
Application number
PCT/EP2014/060641
Other languages
German (de)
English (en)
Inventor
Thomas Krause
Junbiao Lai
Otto Menig
Armin Olschewski
Arno Stubenrauch
Alexander De Vries
Gunnar DE WIT
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
Priority to PCT/EP2014/060641 priority Critical patent/WO2015176769A1/fr
Publication of WO2015176769A1 publication Critical patent/WO2015176769A1/fr

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
    • 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
    • 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
    • F16C33/64—Special methods of manufacture
    • 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft
    • 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
    • F16C19/36—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 a single row of rollers
    • F16C19/364—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 a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • 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
    • 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
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P70/00—Climate change mitigation technologies in the production process for final industrial or consumer products
    • Y02P70/50—Manufacturing or production processes characterised by the final manufactured product

Definitions

  • the invention relates to a part of a wind energy plant, comprising at least one bearing arrangement, with which a rotor is rotatably mounted relative to a housing, wherein the bearing arrangement comprises at least one roller bearing, wherein the roller bearing at least one first bearing ring connected to the rotor and at least one With the housing connected to the second bearing ring, wherein between the bearing rings rolling elements are arranged, wherein the first bearing ring connected to the rotor has a cylindrical seat surface with which it sits on a cylindrical portion of the rotor, preferably with a press fit.
  • the storage of the rotor of a wind turbine is a demanding warehouse task.
  • the bearing inner ring of the often designed as a tapered roller bearing bearing is often arranged with a press fit on a cylindrical portion of the rotor to permanently fix the bearing ring during its service life on the rotor.
  • the effects mentioned limit the service life of the rolling bearing and sometimes lead to premature failure of storage.
  • the invention has for its object to provide a generic wind turbine or a part thereof, in which the tendency to cracking on the bearing rings of the storage is at least greatly reduced. Also, the occurrence of fretting corrosion in the region of the cylindrical seat of the bearing is to be reduced by shaft deflection under load.
  • the solution to this problem by the invention is characterized in that the cylindrical seat surface of the bearing ring connected to the rotor is produced by a concluding honing process as a final machining process, wherein between an end face of the first bearing ring and an end face formed for axial abutment a shoulder of the rotor, a ring element is arranged, which consists of a material which has a lower rigidity than the material of the first bearing ring and the rotor.
  • the bearing rings and the rotor preferably consist of steel, while the ring element consists of plastic.
  • the plastic is preferably fiber-reinforced; Polyamide is particularly preferred as the plastic, in particular polyamide 6.6.
  • the ring element preferably has a rectangular shape in radial section.
  • the cylindrical seat is subjected to a grinding operation according to a development before the honing process. It has surprisingly been found that a particularly good result is achieved when said honing process - optionally with upstream grinding process - preferred for later installation of the bearing ring, but not necessarily carried out by press fit to such a degree until a defined maximum radial difference between maximum and minimum value over the circumference of the cylindrical seat is present.
  • the cylindrical seating surface is designed after honing and, if appropriate, the preceding grinding in such a way that the radial difference between the maximum and minimum values above the circumference of the cylindrical seating surface is at most equal to the following value: ⁇ D 4,200
  • the critical hoop stress (o c ) in the bearing ring before the application of an external load is preferably a value between 180 MPa and 220 MPa, preferably 200 MPa.
  • the raceway of the bearing ring is preferably hard-turned; it can also be hard-rolled.
  • the first bearing ring is preferably the bearing inner ring; just as the first bearing ring but also be the bearing outer ring, which is designed accordingly.
  • the rolling bearing is preferably designed as a tapered roller bearing or as a cylindrical roller bearing.
  • the cylindrical seat surface of the bearing ring is produced by a honing process, wherein the honing process is the last machining step of the seat; However, this can be preceded by a grinding process.
  • the track and / or the cylindrical seat are preferably burnished. It has been found that the tendency to crack on the raceway of the bearing ring and the tendency to fretting corrosion can be significantly reduced when the proposed design of the bearing assembly is used.
  • an embodiment of the invention is shown. Show it:
  • FIG 3 shows the maximum allowable radial difference between the maximum and minimum values of the radius over the circumference of the cylindrical seating surface according to the invention as a function of the diameter of the cylindrical seating surface for various nominal circumferential stresses in the bearing ring.
  • a bearing assembly 2 is to be seen in the form of a tapered roller bearing, with a rotor 3 - this may, but need not be, the main rotor of the wind turbine - in a housing 4th is stored;
  • a second, not shown (tapered rollers) bearing is necessary to support the rotor 3 in the housing 4;
  • the bearing assembly 2 in this case therefore comprises two rolling bearings 5 in the form of tapered roller bearings.
  • the tapered roller bearing 5 has a first bearing ring 6, namely the bearing inner ring, and a second bearing ring 7, namely the bearing outer ring. Between the bearing rings 6, 7 rolling elements 8 are arranged in the usual way in the form of tapered rollers.
  • the bearing inner ring 6 is seated with a cylindrical seat surface 7 in the embodiment with a press fit on a congruent cylindrical section of the rotor 3.
  • the bearing inner ring 6 has an end face 10 which faces an end face 11 of a flange-shaped shoulder 12. Between the two end faces 11 and 12, a plastic ring 13 is arranged, which consists of polyamide.
  • the plastic ring 13 has in radial section - as can be seen - a rectangular shape.
  • the nominal hoop stress ⁇ 5 nom is usually zero. However, it can also be greater than zero if, for example, in the case of a tapered-roller bearing outer ring, a circumferential stress in the ring is produced as a result of an axial load and an expansion of the ring caused thereby.
  • a critical hoop stress o c in MPa
  • This value is material-dependent and may be 200 MPa for steel, for example.
  • Fig. 2 it is shown how the cylindrical bore 9 with its nominal diameter D (in mm) changed in radius over the circumference of the bearing ring 6, wherein, of course, the course of the bore is shown greatly exaggerated. It turns out that due to the irregularity or waviness there is a radial difference between the maximum and the minimum value of the radius; this difference is denoted by h c .
  • the cylindrical bore 9 is presently brought by a grinding operation with a subsequent honing process in its final form; after honing, no further mechanical machining of the hole follows.
  • the raceway of the bearing ring 6 can be made classic, ie that the final contour is made by grinding. However, hard twisting and / or hard rolling is also possible here, possibly followed by honing. A very advantageous result and a substantial improvement against cracks in the raceway are achieved if the radial difference hc does not exceed the following value: ⁇ D 4,200
  • the procedure is such that, based on the intended construction and the planned use of the rolling bearing in the wind energy plant, it is first determined with which hoop stress ⁇ ⁇ , for example, the bearing inner ring will sit on the rotor 3.
  • the critical hoop stress o c is determined in the bearing ring, as it exists after the production of the press fit and before the application of an external load in the bearing ring. This value is material-dependent; an example of said voltage has been given above.

Abstract

L'invention concerne une partie d'éolienne (1), comprenant au moins un ensemble palier (2) avec lequel un rotor (3) est monté rotatif par rapport à un boîtier (4). L'ensemble palier comprend au moins un palier à roulement (5) et le palier à roulement (5) possède au moins une première bague de palier (6) reliée au rotor (3) et au moins une deuxième bague de palier (7) reliée au boîtier. Des éléments roulants (8) sont disposés entre les bagues de palier (6, 7) et la première bague de palier (6), reliée au rotor (3), possède une portée cylindrique (9) avec laquelle elle repose sur une portion cylindrique du rotor (3). Selon l'invention, en vue de prévenir la prédisposition de la bague de palier à la fissuration, la portée cylindrique (9) de la bague de palier (6) en liaison avec le rotor (3) est produite par une opération de tournage dur qui est une opération de fabrication par enlèvement de copeaux finale. Un élément annulaire (13), qui est constitué d'un matériau ayant une rigidité plus faible que le matériau de la première bague de palier (6) et du rotor (3), est disposé entre une face frontale (10) de la première bague de palier (6) et une face frontale (11) d'un gradin (12) du rotor (3), configurée pour l'appui axial.
PCT/EP2014/060641 2014-05-23 2014-05-23 Partie d'éolienne WO2015176769A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/EP2014/060641 WO2015176769A1 (fr) 2014-05-23 2014-05-23 Partie d'éolienne

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2014/060641 WO2015176769A1 (fr) 2014-05-23 2014-05-23 Partie d'éolienne

Publications (1)

Publication Number Publication Date
WO2015176769A1 true WO2015176769A1 (fr) 2015-11-26

Family

ID=50771506

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2014/060641 WO2015176769A1 (fr) 2014-05-23 2014-05-23 Partie d'éolienne

Country Status (1)

Country Link
WO (1) WO2015176769A1 (fr)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1157776A2 (fr) * 2000-05-23 2001-11-28 Delphi Technologies, Inc. Pièces de paliers en acier pour charges elevées et leur procédé de fabrication
DE102009040062A1 (de) * 2009-09-07 2011-03-10 Thielenhaus Technologies Gmbh Vorrichtung zur Endbearbeitung ringförmiger Werkstücke, insbesondere von Lagerringen

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1157776A2 (fr) * 2000-05-23 2001-11-28 Delphi Technologies, Inc. Pièces de paliers en acier pour charges elevées et leur procédé de fabrication
DE102009040062A1 (de) * 2009-09-07 2011-03-10 Thielenhaus Technologies Gmbh Vorrichtung zur Endbearbeitung ringförmiger Werkstücke, insbesondere von Lagerringen

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