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WO2018189143A1 - Ensemble palier servant à supporter une pale de rotor d'une éolienne - Google Patents

Ensemble palier servant à supporter une pale de rotor d'une éolienne Download PDF

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Publication number
WO2018189143A1
WO2018189143A1 PCT/EP2018/059099 EP2018059099W WO2018189143A1 WO 2018189143 A1 WO2018189143 A1 WO 2018189143A1 EP 2018059099 W EP2018059099 W EP 2018059099W WO 2018189143 A1 WO2018189143 A1 WO 2018189143A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
hub
ring
rolling
bearing ring
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/EP2018/059099
Other languages
German (de)
English (en)
Inventor
Gunther Elfert
Bernd LÜNEBURG
Fabian Ackfeld
Jörg ROLLMANN
Thomas Wulf
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
Priority to CN201880024519.XA priority Critical patent/CN110914538B/zh
Publication of WO2018189143A1 publication Critical patent/WO2018189143A1/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
    • 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
    • F16C19/381—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
    • 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
    • F16C33/583—Details of specific parts of races
    • 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
    • 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
    • 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
    • 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 relates to a bearing assembly for supporting a rotor blade of a wind turbine, comprising a rolling bearing for rotatably supporting the rotor blade about its longitudinal axis and a hub for transmitting a rotational movement of the rotor blade to a rotor shaft of the wind turbine, wherein the rolling bearing a first bearing ring, a second bearing ring and between the bearing rings arranged rolling elements, wherein the bearing rings are rotatable relative to each other, wherein the first bearing ring has a radially extending to the center of the first bearing ring down pin having two raceways for first rolling elements and a raceway for second rolling elements, wherein the second bearing ring Having raceways for the first rolling elements and a raceway for the second rolling elements, wherein one of the bearing rings with the hub and the other of the bearing rings is connected to the rotor blade, and wherein the hub has an annular connection area to the A having connection of the rolling bearing.
  • the blade bearings of wind turbines must transmit high forces and moments.
  • a high number of pitch cycles must be realized, which means high demands on the service life of the obsolete contact points of the row of rolling elements with the raceways.
  • the blade bearing must withstand large deformations and deformation change cycles, even when the bearing is at a standstill (with the turbine rotating).
  • the rollers have line contact with the raceways. Even slight relative deformations of the raceways perpendicular to the rolling direction of the rolling element row, in particular when the bearing is stationary, lead to damage (so-called false brinelling) in such roller bearings, which can unduly reduce the service life.
  • a bearing arrangement of the type mentioned is known for example from the document EP 1 891 327 Bl.
  • the blade bearing is designed as a 3-row roller slewing connection.
  • EP 1 891 327 Bl it is described that various stresses act on the blade bearing rotor blade of a wind energy plant. The greatest stress is the tilting moment, which acts on the blade bearings due to the self-weighting force of the rotor blades and the hub as well as the concentrated wind load in the center of the wind pressure (approximately in the middle of the rotor blade length). Due to the considerable lever arms result in very high bending stress of the blade root of the rotor blade and the blade bearings.
  • the outer ring of the blade bearing is flanged on the face side from the outside to an annular connecting region of the hub.
  • the outer ring has an annular connection surface 10 which rests on an end face 16 of the rotor hub 3.
  • the outer ring of the blade bearing is bolted to the rotor hub 3 via stud bolts 20, while the inner ring of the blade bearing is bolted to the rotor blade 2 via stud bolts 19 and anchoring body 8.
  • EP 1 891 327 B1 recommends, as a measure for increasing the service life of the proposed 3-row roller slewing connection, that the rolling elements receiving the axial forces should have at least one cambered transitional area between the lateral surface and at least one adjacent end face, ie. a flattening or rounding off.
  • an edge pressure against the track is tolerated during elastic deformation of the bearing unit during operation, as is ensured for this case in the region of the rounded transition sufficient contact surface with the treads.
  • a disadvantage of this proposed solution measure is that it does not address the above-mentioned problem of leakage caused by the elastic deformations of the bearing and inadequate lubrication which shorten the life of the bearing The deformations can become so great that the rounding of the rolling elements is not sufficient to safely avoid an inadmissibly large edge pressure.
  • the patent application EP 2 933 476 A1 pursues the approach of increasing the stiffness of the blade bearing by means of two reinforcement plates (first reinforcement plate 31, second reinforcement plate 32).
  • the two reinforcing discs are attached to the inner ring of the blade bearing.
  • further reinforcing means are provided for increasing the rigidity of the blade bearing secured to the reinforcing discs (paragraph 0070: "The pitch bearing is further reinforced by a stiffening block which as a further means 40 for reinforcing the bearing. 41. ").
  • the further means are provided for increasing the rigidity of the blade bearing secured to the reinforcing discs.
  • WO 2013/107452 A1 proposes a support structure (support structure 30) for increasing the stiffness of the blade bearing in the radial, circumferential and axial directions. This is formed by support ribs (support ribs 40). The support structure may have different stiffnesses in the circumferential direction.
  • the document EP 2 546 512 A1 proposes a reinforcing ring (reinforcing ring 23) connected to the inner ring of the journal bearing for increasing the rigidity.
  • Document EP 2 623 772 A1 also teaches the use of a reinforcing ring (reinforcing 24) connected to the inner ring of the blade bearing.
  • the patent application WO 2013/076754 AI teaches the use of a reinforcing element in the form of a ring plate ("reinforcement element 23 in the form of a ring plate"), which is attached to the inner ring of the blade bearing.
  • a bearing assembly for supporting a rotor blade of a wind turbine which has a high rigidity against elastic deformations of the rotor bearing, with a low weight of the blade bearing, a low assembly cost and low material costs are achieved.
  • a further object of the present invention is to propose a wind power plant in which, even with large rotor blades having a large diameter in the region of the rotor blade root, an elastic deformation of the blade bearing due to the high loads occurring during operation is prevented or limited to an acceptable level ,
  • the bearing arrangement is integrated into the hub in such a way that the hub optimally supports the raceways of the bearing and thus the deformations, in particular the radial deformations of the raceways, are minimized.
  • the integration of the rolling bearing in the hub has the consequence that the bearing-hub system is stiffer than in the known from the prior art end-side flanges of the bearing to the hub. This reduces in particular the radial deformations of the bearing and the raceways and thus leads to lower relative movements of the raceways perpendicular to the rolling direction of the rollers. This minimizes the risk of false bridging effects.
  • the bearing assembly according to the invention achieves an increase in the stiffness of the blade bearing and thus a greater resistance to elastic deformation of the blade bearing at high loads occurring during operation without the use of additional reinforcing components.
  • the bearing arrangement according to the invention requires no additional reinforcing elements. As a result, the weight of the blade bearing is kept as low as possible.
  • the bearing assembly according to the invention can be mounted without increased assembly costs, because no separate reinforcing elements must be handled and mounted. By dispensing with separate reinforcing elements and the material used for the blade bearing is reduced to a minimum.
  • stiffening additional elements can also be used in the context of the present invention. By using stiffening additional elements in a bearing assembly with integrated into the hub bearing ring particularly high stiffness can be achieved.
  • the present invention relates to a bearing assembly for supporting a rotor blade of a wind turbine, comprising a rolling bearing for rotatably supporting the rotor blade about its longitudinal axis and a hub for transmitting a rotational movement of the rotor blade to a rotor shaft of the wind turbine, the rolling bearing a first bearing ring, a second Bearing ring and between the bearing rings arranged rolling elements, wherein the bearing rings are rotatable relative to each other, wherein the first bearing ring has a radially extending towards the center of the first bearing ring down pin having two raceways for first rolling elements and a raceway for second rolling elements, wherein the second bearing ring raceways for the first rolling elements and a raceway for the second rolling elements, wherein one of the bearing rings with the hub and the other of the bearing rings is connected to the rotor blade, and wherein the hub has an annular connection area For connection of the rolling bearing.
  • the invention proposes that one of the bearing rings is integrated in the connection area in such a way in the hub in that the material of the hub contributes to the stiffening of the integrated bearing ring in the radial direction.
  • the material of the hub serving for stiffening the integrated bearing ring is arranged distributed in the connection region such that relative deformations in the radial direction between the raceways of the first and the second bearing ring are minimized.
  • the distribution of the hub material in the connection area of the hub takes place taking into account the rigidity ratios of the bearing ring connected to the rotor blade and the associated rotor blade in its operating position.
  • the changing loads are taken into account, which result from the tilting moment occurring due to the weight of the rotor blade. Due to the distribution of the hub material according to the invention in the connection region, there is no or only minimal / minimized relative deformations in the radial direction between the raceways of the first and the second bearing ring.
  • the concrete distribution of the hub material in the connection area and thus the structural design of the connection area of the hub takes place on the basis of finite element analyzes by determining the force flow and the deformations.
  • the existing material of the hub according to the invention is optimized in terms of its distribution in the connection area of the hub and used to increase the flexural rigidity of the blade bearing and thereby the resistance to elastic deformation of the blade bearing, especially in the radial direction, occurring during operation high loads increase.
  • the blade bearing can be integrated in different ways in the hub.
  • the different possibilities are described below in exemplary embodiments.
  • the rolling bearing is arranged on the inner circumference of the connection region.
  • the first bearing ring preferably forms the outer ring of the rolling bearing.
  • This embodiment offers several advantages: a) it is possible to realize an overall comparatively small blade bearing with a relatively small outside diameter, which leads to comparatively low production costs; b) the outer ring has high resistance to deformation, in particular radial deformations, due to the integration in the hub c) The rigidity of the inner ring against deformation, in particular radial deformations as a result of the loads occurring during operation (in particular by tilting moments) can be increased by additional stiffening additional elements.
  • connection area in the hub outer ring can be created with a small amount of material used in the radial direction very stiff trained leaf bearing, in which the radial deformation of the bearing rings and thus the undesirable relative movements of the raceways of the two bearing rings to each other in operation are minimized.
  • the first bearing ring may be formed integrally with the hub, d .h. Hub and first bearing ring are part of one and the same component.
  • the first bearing ring may be formed by machining such as turning or milling the hub from the material of the hub.
  • This embodiment may also be referred to by the term "fully integrated bearing ring" in order to make it clear that this type of integration of the bearing ring leads to the bearing ring not being a separate component but rather a component of the hub
  • the number of components is , which form the rolling bearing, particularly low, because the outer ring as a separate Component disappears.
  • no fastening means such as screws are required to connect the first bearing ring with the hub.
  • the first bearing ring can be designed as a separate bearing ring formed separately from the hub
  • the first bearing ring is connected to the hub by means of connecting elements such as, for example, threaded fasteners
  • An embodiment of the invention with a separate bearing ring formed separately from the hub may be termed “semi-integrated bearing ring” to better distinguish it linguistically from the "fully integrated bearing ring” solution described above
  • the superordinate term "integrated bearing ring” designates both the solution with a fully integrated bearing ring and the solution with a partially integrated bearing ring.
  • the material of the hub contributes to the stiffening of the integrated bearing ring in the radial direction.
  • the hub material contributes to a flexural rigidity of the rolling bearing against moments acting on the rotor blade on the rolling bearing.
  • the cross-sectional area of the integrated bearing ring and the cross-sectional area of the hub material in the connection region of the bearing ring both contribute to the area moment of inertia of the relevant component cross-section.
  • the rolling bearing is arranged on the outer circumference of the connection region.
  • the first bearing ring preferably forms the inner ring of the rolling bearing.
  • the first bearing ring may be formed integrally with the hub. Similar to the arrangement of the first bearing ring on the inner circumference of the connection region can be formed out of the material of the hub by a machining operation such as turning or milling in its arrangement on the outer circumference of this bearing ring.
  • the second bearing ring which forms the outer ring to form divided in the axial direction, ie. it consists of two partial rings.
  • the dividing rings forming the divided outer ring can also be segmented in the circumferential direction in order to further simplify assembly and disassembly.
  • the first bearing ring may be segmented in this embodiment in the circumferential direction and / or seen in the axial direction.
  • connection region of the hub has a first cylindrical abutment surface on which a circumferential surface of the first bearing ring rests.
  • This first cylindrical contact surface extends parallel to the axis of rotation of the rolling bearing. Since the lateral surface of the first bearing ring bears against this first cylindrical bearing surface of the hub, the cross section of the first bearing ring and the cross section of the connecting region of the hub add up to a common cross section, which then forms the relevant cross section for determining the area moment of inertia, which is responsible for the resistance of the bearing Association of the first bearing ring and connection area of the hub against deformation, in particular deformations due to bending stress, is authoritative.
  • the first bearing ring stiffening material of the hub causes in particular an increased resistance of the rolling bearing against deformation in the radial direction.
  • relative deformations of the first and second bearing ring are avoided or at least limited to a small extent to each other, which lead to a movement apart of the raceways of the two bearing rings in the radial direction. Just these relative movements of the raceways, which are caused by deformation of the bearing rings, lead to increased wear of the leaf bearing of wind turbines.
  • the hub in addition to the first cylindrical contact surface, has a second cylindrical contact surface.
  • This second cylindrical contact surface extends substantially perpendicular to the first cylindrical contact surface in the radial direction towards the center of the rolling bearing.
  • At this second cylindrical contact surface is an end face of the first bearing ring.
  • the first bearing ring is supported with its face remote from the rotor blade face in the longitudinal direction of the rotor blade form-fitting manner on the hub.
  • the material of the hub contributes in the axial direction to an increase in the relevant for the deformation stiffness cross-section.
  • the two above-described first and second cylindrical contact surfaces of the hub form a cross-sectionally L-shaped circumferential receiving pocket for the first bearing ring.
  • the second cylindrical abutment surface can be introduced distributed over the circumference arranged blind holes with internal thread, which are each aligned with through holes of the first bearing ring.
  • the first bearing ring is firmly connected to the hub.
  • the first bearing ring and the hub then form a stiff component composite.
  • the first bearing ring in particular a much higher rigidity against the tilting moments, which act on the connected to the rotor blade second bearing ring on the first bearing ring.
  • the dimensioning of the connection region is influenced by the thickness of the first bearing ring in the radial and axial direction.
  • the diameter of the first bearing ring must also be considered.
  • the flow of force also plays a role, ie. It must be taken into account in which directions the forces acting on the first bearing ring act on the hub and in particular on the connecting region of the hub.
  • the power flow can be different for different hub types.
  • the dimensioning of the connection area of the hub is also dependent on whether the first bearing ring is "fully integrated" (ie is part of the hub), or whether it is "partially integrated", ie.
  • the invention also relates to a wind energy plant with at least one rotor blade attached to a hub and with a rotor shaft which transmits the rotation of the hub to a rotor of a generator, wherein the rotor blade is connected to the hub via the bearing arrangement according to the invention.
  • a wind turbine is less frequent, because the blade bearings have an increased life due to the present invention and therefore less often need to be replaced or repaired.
  • the availability of wind turbines, which are equipped with the layer arrangement according to the invention is greater than the availability of wind turbines, in which the rotor blades with bearing arrangements according to the prior art attached to the hub. The invention thus makes a significant contribution to the profitability of wind turbines.
  • Fig. 1 shows a perspective view of a rotor hub of a wind turbine with integrated bearings.
  • FIG. 2 shows a radial half section through a connection region of the hub.
  • FIG. 3 shows an enlarged illustration of the detail B from FIG. 2 according to a first embodiment of the invention.
  • FIG. 4 shows an enlarged view of the detail B from FIG. 2 according to a second embodiment of the invention.
  • Fig. 5 shows a third embodiment of the invention.
  • Fig. 6 shows a fourth embodiment of the invention.
  • Fig. 1 shows a perspective view of a rotor hub 10 (hereinafter referred to simply as "hub") for a wind energy plant 10.
  • the hub 10 has connection areas 11, to which rotor blades of the wind energy plant with its rotor blade root, not shown in FIG A total of three connection regions 11 are provided on the hub 10.
  • a rolling bearing 1 is accommodated in the connection region 11 shown at the top in Fig. 1.
  • This rolling bearing 1 forms a blade bearing, through which the rotor blade moves relative to the hub 10 can be rotated about its longitudinal axis in order to adjust the angle of attack of the rotor blade to the wind during operation of the wind turbine.
  • FIG. 2 shows a radial half section through the connection area 11 of the hub 10 according to FIG. 1 accommodating the roller bearing 1. It can be clearly seen that the roller bearing 1 is completely enclosed by the connection area 11 of the hub 10.
  • the rolling bearing 1 comprises a first bearing ring 2 and a second bearing ring 3.
  • the rolling bearing 1 enclosing hub material contributes to the stiffening of the integrated bearing ring 2 in the radial direction.
  • the illustrated in Fig. 2 first embodiment of the bearing assembly according to the invention is shown in Fig. 3 again in an enlarged view. The exact structure of the bearing assembly according to the first embodiment of the invention will be described in more detail with reference to FIG. 3.
  • the in Fig. 3 illustrated first embodiment of a bearing assembly according to the invention has a first bearing ring 2.
  • the first bearing ring 2 has a pin 6 extending radially towards the center of the first bearing ring 2.
  • the pin 6 has two raceways 7, 8 for first rolling elements 4a, 4b and a raceway 9 for second rolling elements 5.
  • the second bearing ring 3 has two raceways 7 ', 8' for the first rolling elements 4a, 4b and a raceway 9 'for the second rolling elements 5.
  • the first bearing ring 2 is in the embodiment shown in FIG. 3 part of the hub 10, i. he is fully integrated into the hub 10.
  • the raceways 7, 8, 9 are part of the hub 10.
  • the "connection" of the first bearing ring 2 with the hub 10 is thereby very strong and stiff Hub 10.
  • the first bearing ring 2 may be formed for example by a machining process such as turning or milling of the material of the hub 10.
  • the first bearing ring 2 has a pin 6.
  • the pin 6 has two horizontally aligned raceways 7, 8.
  • the raceways 7, 8 are formed by raceway plates 20 or wires 21, which are applied to the pin 6.
  • the pin 6 at its radially inwardly facing end face a track 9 for the second rolling elements 5.
  • the raceway 9 is also formed by raceway plates 20 or wires 21.
  • the raceway plates 20 or wires 21 are advantageously positively applied to the raceways 7, 8, 9 of the pin 6.
  • the hub 10 and the pin 6 thus serves as a support for the raceway plates 20 or wires 21.
  • the raceway plates 20 or wires 21 are hardened or made of a hard to very hard material.
  • the rolling elements 4a, 4b, 5 have no direct contact with the rolling elements facing surfaces of the pin 6, but the rolling elements 4a, 4b, 5 roll on the raceway plates 20 or wires 21 from.
  • the material of the hub 10 need not be a hardenable material, in particular a hardenable steel. The hardening of the surfaces of the pin 6 to produce raceways on which the rolling elements can roll immediately is not required.
  • An inexpensive material for the hub 10 may be used because the hardness required for the raceways 7, 8, 9 is provided over the separate raceway plates 20 or wires 21.
  • raceways 7, 8, 9 of the pin 6 may also be hardened or coated with a hard material. In these cases, no raceway plates 20 or wires 21 are then required.
  • the rolling elements 4a, 4b, 5 can then roll directly on the raceways 7, 8, 9.
  • the first bearing ring 2 formed integrally with the hub 10 forms the outer ring of the rolling bearing 1.
  • the inner ring of the rolling bearing 1 is formed by the second bearing ring 3.
  • the second bearing ring 3 is divided in the axial direction, ie. it is formed by two partial rings 3a, 3b.
  • the partial rings have the raceways 7, 8, 9 of the first bearing ring 2 associated raceways 7 ', 8', 9 ', which are formed by hardened, in particular inductively hardened surface regions of the partial rings 3a, 3b.
  • the rolling elements 4a, 4b, 5 roll directly on the hardened raceways 7 ', 8', 9 'of the partial rings 3a, 3b from.
  • the partial rings 3a, 3b have mutually aligned through holes.
  • FIG. 1 A second embodiment of the layer arrangement according to the invention is shown in FIG.
  • the first bearing ring 2 formed as a separate, separate from the hub 10 formed component.
  • the first bearing ring 2 forms the outer ring of the rolling bearing 1 and the second bearing ring 3 forms the inner ring of the rolling bearing 1.
  • the first bearing ring 2 has through holes, which are aligned with corresponding blind holes in the material of the hub 10.
  • the blind holes in the hub 10 have an internal thread.
  • the first bearing ring 2 is connected by screws 13 to the hub 10. The screws 13 are passed through the through holes in the first bearing ring 2 and screwed into the blind holes of the hub 10. In this way, the first bearing ring 2 is rotatably connected to the hub 10.
  • the first bearing ring 2 has a pin 6, the raceways 7, 8, 9 for the rolling elements 4a, 4b, 5 has.
  • the raceways 7, 8, 9 for the rolling elements 4a, 4b, 5 have.
  • the surfaces of the pin 6 are hardened, so that the surfaces themselves form the raceways 7, 8, 9 for the rolling elements.
  • the rolling elements 4a, 4b, 5 roll directly on the raceways 7, 8, 9 forming surfaces of the pin 6 from.
  • the raceways 7, 8, 9 of the pin 6 are inductively hardened.
  • the first bearing ring 2 may in particular consist of hardenable steel, so that the raceways 7, 8, 9 of the pin 6 are hardened by induction hardening to sufficiently hard and wear resistant raceways 7, 8, 9 for the rolling elements 4a, 4b, 5 are available put.
  • the second bearing ring 3 is in the embodiment of FIG. 4 formed by two partial rings 3a, 3b.
  • the first partial ring 3a has a raceway 7 'for the rolling elements 4a.
  • the raceway 7 ' is the complementary to the raceway 7 of the first bearing ring 2 career.
  • the second sub-ring 3b has a raceway 8 'for the rolling elements 4b, which is the complementary to the raceway 8 of the first bearing ring 2 career.
  • the second partial ring 3b on a track 9 'for the rolling elements 5, which is the complementary to the track 9 of the first bearing ring 2 career.
  • the raceways 7 ', 8', 9 'of the second bearing ring 3 are hardened, in particular inductively hardened.
  • the rolling elements 4a, 4b, 5 roll directly on the hardened raceways 7, 8, 9 and 7 ', 8' and 9 'from.
  • the inner rings forming partial rings 3a, 3b are in the embodiment of FIG. 4 as well connected to the rotor blade as described above to the embodiment of FIG. 3.
  • the raceway 9 'for the rolling elements 5 may also be provided on the first part ring 3a. In this case, then the dividing plane between the sub-rings 3a, 3b below the rolling elements 5 and not, as shown in FIG. 3 and 4, above the rolling elements. 5
  • the embodiment according to FIG. 4 has several further advantages.
  • One advantage is that the construction of the rolling bearing is very similar to the design of the 3-row roller slewing rings known from the prior art for the application "blade bearing.” The designer benefits from the fact that the behavior of the rolling bearing 1 itself and Another advantage is that the well-known and in practice proven screwing of the inner ring with the rotor blade can be maintained.
  • a third advantage is that all components of the bearing can be formed from the same materials already used for
  • a further advantage is that the customer with the embodiment of Fig. 4, a known and well-known 3-row roller slewing compounds known and tested ready to install solution can be offered, which the customer as it is delivered to integrate into the hub and connect to the rotor blade 10.
  • a third embodiment of the bearing assembly according to the invention is shown, in which the first bearing ring 2 forms the inner ring of the rolling bearing 1.
  • the rolling bearing 1 is arranged on the outer circumference of the connection region 11 of the hub 10.
  • the first bearing ring 2 is integrated into the hub 10 in that it is formed integrally with the hub 10.
  • the first bearing ring 2 is thus completely integrated into the hub 10.
  • the "connection" of the first bearing ring 2 with the hub 10 is thereby very strong and stiff.There are no separate fastening means such as screws required to connect the first bearing ring 2 with the hub 10.
  • Manufacturing technology the first bearing ring 2, for example by a machining process such as turning or milling from the material of the hub 10 may be formed.
  • the first bearing ring 2 has a pin 6 extending radially outwards.
  • the pin 6 has raceways 7, 8, 9 for the rolling elements 4a, 4b, 5.
  • the raceways 7, 8 are aligned horizontally.
  • the raceway 9 is arranged on the radially outwardly facing end face pin 6.
  • the raceways 7, 8, 9 are formed by raceway plates 20 or wires 21 which are hardened or consist of a hard to very hard material.
  • raceway plates 20 or wires 21 are advantageously positively applied to the raceways 7, 8, 9 of the pin 6.
  • the raceway plates 20 or wires 21 are hardened or made of a hard to very hard material.
  • the hub 10 and the pin 6 thus serves as a support for the raceway plates 20 or wires 21.
  • the raceways 7, 8, 9 together with the raceway plates 20 or wires 21 so to speak part of the hub 10.
  • the material of the hub 10 does not have to be a hardenable material, in particular no hardenable steel.
  • raceways 7, 8, 9 The hardening of the surfaces of the pin 6 to produce raceways on which the rolling elements can roll immediately is not required.
  • An inexpensive material for the hub 10 may be used because the hardness required for the raceways 7, 8, 9 is provided over the separate raceway plates 20 or wires 21.
  • the raceways 7, 8, 9 of the pin 6 may also be hardened or coated with a hard material. In these cases, no raceway plates 20 or wires 21 are then required.
  • the rolling elements 4a, 4b, 5 can then roll directly on the raceways 7, 8, 9.
  • the first bearing ring 2 formed integrally with the hub 10 forms the inner ring of the rolling bearing 1.
  • the outer ring of the rolling bearing 1 is formed by the second bearing ring 3.
  • the second bearing ring 3 is divided in the axial direction, ie. it is formed by two partial rings 3a, 3b.
  • the partial rings have the raceways 7, 8, 9 of the first bearing ring 2 associated raceways 7 ', 8', 9 ', which are formed by hardened, in particular inductively hardened surface regions of the partial rings 3a, 3b.
  • the rolling elements 4a, 4b, 5 roll directly on the hardened raceways 7 ', 8', 9 'of the partial rings 3a, 3b from.
  • the partial rings 3a, 3b have mutually aligned through holes.
  • Fig. Fig. 6 shows a fourth embodiment of the invention.
  • the rolling bearing 1 is disposed on the outer periphery of the terminal portion 11 of the hub 10.
  • the first bearing ring 2 is designed as a separate component formed separately from the hub 10.
  • the first bearing ring 2 forms the inner ring of the rolling bearing 1 and the second bearing ring 3 forms the outer ring of the rolling bearing 1.
  • the first bearing ring 2 has through holes, which are aligned with corresponding blind holes in the material of the hub 10.
  • the blind holes in the hub 10 have an internal thread.
  • the first bearing ring 2 is connected by screws 13 to the hub 10. The screws 13 are passed through the through holes in the first bearing ring 2 and screwed into the blind holes of the hub 10. In this way, the first bearing ring 2 is rotatably connected to the hub 10.
  • the first bearing ring 2 has a pin 6, the raceways 7, 8, 9 for the rolling elements 4a, 4b, 5 has.
  • no race plates 20 or wires 21 are required to provide sufficiently hard raceways for the rolling elements 4a, 4b, 5 are available.
  • the surfaces of the pin 6 are hardened, so that the surfaces themselves form the raceways 7, 8, 9 for the rolling elements.
  • the rolling elements 4a, 4b, 5 roll directly on the raceways 7, 8, 9 forming surfaces of the pin 6 from.
  • the raceways 7, 8, 9 of the pin 6 are inductively hardened.
  • the first bearing ring 2 may in particular of hardenable steel so that the raceways 7, 8, 9 of the pin 6 are hardened by induction hardening to provide sufficiently hard and wear resistant raceways 7, 8, 9 for the rolling elements 4a, 4b, 5 are available.
  • the second bearing ring 3 is in the embodiment of FIG. 6 formed by two partial rings 3a, 3b.
  • the first partial ring 3a has a raceway 7 'for the rolling elements 4a.
  • the raceway 7 ' is the complementary to the raceway 7 of the first bearing ring 2 career.
  • the second sub-ring 3b has a raceway 8 'for the rolling elements 4b, which is the complementary to the raceway 8 of the first bearing ring 2 career.
  • the raceways 7 ', 8', 9 'of the second bearing ring 3 are hardened, in particular inductively hardened.
  • the rolling elements 4a, 4b, 5 roll directly on the hardened raceways 7, 8, 9 and 7 ', 8' and 9 'from.
  • the outer ring forming part rings 3a, 3b are in the embodiment of FIG. 6 as well connected to the rotor blade as described above to the embodiment of FIG. 5.
  • the raceway 9 'for the rolling elements 5 may also be provided on the second part ring 3b. In this case, then the dividing plane between the sub-rings 3a, 3b above the rolling elements 5 and not, as shown in FIG. 5 and 6, below the rolling elements. 5
  • the embodiment according to FIG. 6 has several further advantages.
  • One advantage is that the construction of the roller bearing 1 is very similar to the design of the 3-row roller slewing rings known from the prior art for the application "blade bearing.” The designer benefits from the fact that the behavior of the rolling bearing 1 itself
  • a further advantage is that the well-known and practically proven screwing of the outer ring with the rotor blade can be maintained
  • a third advantage is that all the components of the bearing can be formed from the same materials that already exist
  • a further advantage is that the customer can be offered with the embodiment of Fig. 6, a ready-to-install solution that the customer as it is delivered to him in the Hub 10 can integrate and connect to the rotor blade.
  • fastening means in the form of screws 13 are provided by way of example in order to firmly connect the first bearing ring 2 with the hub 10. Instead of such screw the first bearing ring 2 can also over others Fastening means are connected to the hub 10.
  • Suitable fasteners are, for example, a) conical clamping or clamping elements screwed from above or below, which clamp or clamp the first bearing ring 2 against the hub 10, b) screwing a clamping element or several clamping elements which clamp the first bearing ring against the hub 10 , in particular form-fitting clamp against the hub 10, c) screwing of clamping nuts which are screwed into a thread that is arranged on the connection portion 11 of the hub 10 and the first bearing ring 2 against the hub 10 brace or jam, d) screwing from the outside the hub 10 respectively on the outside of the connection area 11 ago by means of screws, which pass through the connection portion 11 of the hub 10 and are screwed into threaded holes which are arranged in the first bearing ring 2.
  • the bearing rings 2, 3 can be segmented,
  • the rolling elements 4a, 4b, 5 may be held in cages or cage segments or the rolling elements may be spaced from each other by interposed between the rolling elements of each other
  • the rolling elements 4a, 4b, 5 may be the rolling elements 4a, 4b, 5 holding cages / cage segments or arranged between the rolling elements intermediate pieces of metallic or non-metallic material.
  • Metallic cages / cage segments or metallic spacers may be coated with plastic.
  • the cages / cage segments may be provided with sliders. In this case, the material of the sliders may be different than that of the cages / cage segments.
  • the rolling elements 4a, 4b are provided to receive the axial forces acting on the bearing rings 2, 3, while the rolling elements 5 absorb the radial forces acting on the bearing rings 2, 3.
  • the rolling elements 4a, 4b, 5 may preferably be formed as cylindrical rollers or as Toroidalrollen. If the rolling elements are designed as cylindrical rollers, the raceways have a planar shape. If the rolling elements are designed as Toroidalrollen, so adapted to the shape of the roles career forms are provided. List of Reference Signs

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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)
  • Wind Motors (AREA)

Abstract

L'invention concerne un ensemble palier servant à supporter une pale de rotor d'une éolienne. L'ensemble palier comprend un palier à roulement (1) servant à supporter la pale de rotor de manière à pouvoir tourner autour de son axe longitudinal et un moyeu (10) servant à transférer un mouvement de rotation de la pale de rotor sur un arbre de rotor de l'éolienne. Le palier à roulement (1) comporte une première bague (2) de palier, une deuxième bague (3) de palier et des corps de roulement (4a, 4b, 5) disposés entre les bagues (2, 3) de palier. Les bagues (2, 3) de palier peuvent être tournées l'une par rapport à l'autre. La première bague (2) de palier comporte un tourillon (6) s'étendant de manière radiale en direction du centre de la première bague (2) de palier, lequel tourillon comporte deux voies de roulement (7, 8) pour des premiers corps de roulement (4a, 4b) et une voie de roulement (9) pour des deuxièmes corps de roulement (5). La deuxième bague (3) de palier comporte des voies de roulement (7', 8') pour les premiers corps de roulement (4a, 4b) et une voie de roulement (9') pour les deuxièmes corps de roulement (5). Une des bagues (2, 3) de palier est reliée au moyeu (10), tandis que l'autre des bagues (3, 2) de palier est reliée à la pale de rotor. Le moyeu (10) comporte une zone de raccordement (11) en forme de bague circulaire servant à attacher le palier à roulement (1). L'invention vise à proposer un ensemble palier servant à supporter une pale de rotor d'une éolienne qui présente une rigidité élevée contre des déformations élastiques du palier de rotor, permettant de réduire le poids du palier de pale, le renfort de moyens pour le montage et des coûts de matériau et de minimiser le risque d'effets Brinell. L'invention propose à cet effet d'intégrer une des bagues (2, 3) de palier dans la zone de connexion (11) de telle manière dans le moyeu (10) que le matériau du moyeu (10) contribue au renforcement de la bague (2, 3) de palier intégrée dans une direction radiale.
PCT/EP2018/059099 2017-04-11 2018-04-10 Ensemble palier servant à supporter une pale de rotor d'une éolienne Ceased WO2018189143A1 (fr)

Priority Applications (1)

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CN201880024519.XA CN110914538B (zh) 2017-04-11 2018-04-10 用于支承风能设备的转子叶片的轴承结构

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DE102017206246.0 2017-04-11
DE102017206246.0A DE102017206246A1 (de) 2017-04-11 2017-04-11 Lageranordnung zur Lagerung eines Rotorblatts einer Windenergieanlage

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CN111692053A (zh) * 2020-07-08 2020-09-22 湘电风能有限公司 一种风力发电机组主轴系传动系统
CN112955671A (zh) * 2018-10-25 2021-06-11 蒂森克虏伯罗特艾德德国有限公司 滚动轴承装置和风力设备
WO2023059282A1 (fr) * 2021-10-06 2023-04-13 Tekno Kauçuk Sanayi̇ Anoni̇m Şi̇rketi̇ Mécanisme de palier permettant d'empêcher un endommagement par faux effet brinell dans des paliers fixes ou oscillants à de faibles amplitudes

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DE102018217899A1 (de) * 2018-10-18 2019-12-24 Thyssenkrupp Ag Wälzlager, insbesondere Großwälzlager, vorzugsweise für Windkraftanlagen mit optimierter Lagerung
DE202019101697U1 (de) * 2019-03-26 2020-07-02 Liebherr-Components Biberach Gmbh Großwälzlager
DE102020001930A1 (de) 2020-03-25 2021-09-30 Imo Holding Gmbh Großlager
DE102020205669A1 (de) 2020-05-05 2021-11-11 Thyssenkrupp Ag Verfahren zum Herstellen von Ringsegmenten und Ringsegment für einen segmentierten Wälzlagerring mit einer gehärteten Wälzlagerlaufbahn
CN114542406B (zh) * 2022-03-01 2023-03-24 哈电风能有限公司 一种直驱风力发电机轴承系统

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Publication number Priority date Publication date Assignee Title
CN112955671A (zh) * 2018-10-25 2021-06-11 蒂森克虏伯罗特艾德德国有限公司 滚动轴承装置和风力设备
CN111692053A (zh) * 2020-07-08 2020-09-22 湘电风能有限公司 一种风力发电机组主轴系传动系统
WO2023059282A1 (fr) * 2021-10-06 2023-04-13 Tekno Kauçuk Sanayi̇ Anoni̇m Şi̇rketi̇ Mécanisme de palier permettant d'empêcher un endommagement par faux effet brinell dans des paliers fixes ou oscillants à de faibles amplitudes

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