CN110914538B - Bearing arrangement for mounting a rotor blade of a wind turbine - Google Patents
Bearing arrangement for mounting a rotor blade of a wind turbine Download PDFInfo
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- CN110914538B CN110914538B CN201880024519.XA CN201880024519A CN110914538B CN 110914538 B CN110914538 B CN 110914538B CN 201880024519 A CN201880024519 A CN 201880024519A CN 110914538 B CN110914538 B CN 110914538B
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- bearing
- hub
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- bearing ring
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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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
The invention relates to a bearing arrangement for mounting a rotor blade of a wind power plant, comprising a rolling bearing (1) for rotatably mounting the rotor blade about a longitudinal axis of the rotor blade, and a hub (10) for transmitting the rotation of the rotor blade to a rotor shaft of the wind power plant, wherein the rolling bearing (1) has a first bearing ring (2), a second bearing ring (3) and rolling bodies (4a,4b,5) arranged between the bearing rings (2,3), wherein the bearing rings (2,3) are rotatable relative to one another, wherein the first bearing ring (2) has a pin (6) extending radially toward the center of the first bearing ring (2) and having two guide rails (7,8) for the first rolling bodies (4a,4b) and a guide rail (9) for the second rolling bodies (5), wherein the second bearing ring (3) has a guide rail for the first rolling bodies (4a,4b) and a guide rail (9') for the second rolling body (5), wherein one of the bearing rings (2,3) is connected to a hub (10) and the other of the bearing rings (3,2) is connected to a rotor blade, and wherein the hub (10) has an annular interface region (11) for connecting the rolling bearing (1). In order to provide a bearing arrangement for supporting a rotor blade of a wind energy plant, which has a high rigidity against elastic deformation of the rotor bearing, wherein a low weight, a low assembly effort and a low material expenditure of the blade bearing are achieved and the risk of a false brinell mark effect is minimized, it is proposed that one of the bearing rings (2,3) is integrated in the hub (10) in the interface region (11) such that the material of the hub (10) contributes to a reinforcement of the integrated bearing ring (2,3) in the radial direction.
Description
Technical Field
The invention relates to a bearing arrangement for mounting a rotor blade of a wind power plant, comprising a roller bearing for rotatably mounting the rotor blade about a longitudinal axis of the rotor blade, and a hub for transmitting the rotation of the rotor blade to a rotor shaft of the wind power plant, wherein the roller bearing has a first bearing ring, a second bearing ring and rolling bodies arranged between the bearing rings, wherein the bearing rings are rotatable relative to one another, wherein the first bearing ring has a pin which extends radially toward the center of the first bearing ring and has two guide rails for the first rolling bodies and a guide rail for the second rolling bodies, wherein the second bearing ring has a guide rail for the first rolling bodies and a guide rail for the second rolling bodies, wherein one of the bearing rings is connected to the hub and the other bearing ring is connected to the rotor blade, and wherein, the hub has an annular interface region for connecting a rolling bearing.
Background
The blade bearings of wind power plants must transmit high forces and moments. Here, a large number of pitch cycles must be carried out, which means a high requirement for the lifetime of the repeated contact points of the rolling element rows with the guide rail. Furthermore, the blade bearing must undergo large deformations and deformation change cycles even in the stationary state of the bearing (when the worm wheel rotates). In the 3-row roller swivel connection used in the bearing arrangement according to the invention, the rollers are in linear contact with the guide rail. In such roller bearings, small relative deformations of the guide rail perpendicular to the rolling direction of the rows of rolling elements already lead to damage (so-called "False Brinelling"), which can lead to an impermissible reduction in the service life, in particular in the stationary state of the bearing. This damage mechanism limits the range of use of 3-row roller swivel connections.
Bearing arrangements of the type mentioned at the outset are known, for example, from document EP 1891327B 1. In the embodiment according to fig. 1 of this document, the blade bearing is embodied as a 3-row rotor-rotating connection. EP 1891327B 1 describes that different stresses act on the blade bearings of the rotor blades of the wind power installation. The largest load is caused by the overturning moment, which acts on the blade bearings by the own weight of the rotor blades and hub and the wind load concentrated in the wind pressure centre (approximately in the middle of the rotor blade length). The blade root of the rotor blade and the blade bearing are subjected to high bending stresses due to the significant lever arms. The wind load-induced overturning moment is supported in the construction of the 3-row roller slewing connection proposed in EP 1891327B 1 as a blade bearing only by axial force couples. In order to absorb this force, which acts axially on the blade bearing and is caused by the aforementioned overturning moment caused by wind loads and the own weight, rolling bodies with axes of rotation transverse to the longitudinal axis of the rotor blade are used in a 3-row roller swivel connection. In the case of a 3-row roller rotary connection according to EP 1891327B 1, the rolling elements are designed such that they can only transmit axial forces. Radial forces cannot be received or transmitted by the rolling bodies.
In addition to the wind loads acting via the lever arms of the rotor blades and the bending stresses caused by the axial forces resulting therefrom, it is also necessary according to EP 1891327B 1 to take into account the loads caused by the wind force itself and acting on the blade bearings in the radial direction. This load, although significantly lower than the load caused by the overturning moment due to its own weight and wind load, is still not negligible, since in the case of the blade bearing design proposed in EP 1891327B 1 as a 3-row roller slewing connection, the approximately cylindrical rolling elements are not able to transmit radial forces. In a 3-row roller rotary joint used as a vane bearing, therefore, a third row of rolling elements is provided, via which radial forces can be transmitted. This third row of rolling elements can be arranged between the two rows of rolling elements for transmitting axial forces, viewed in the axial direction, in a space-saving manner.
In the prior art, the blade bearing is usually connected to the hub by an outer end flange. Thus, in the configuration proposed in EP 1891327B 1 for a blade bearing, the outer ring of the blade bearing is connected at the end by an external flange to the annular interface region of the hub. The outer ring has a circular ring-shaped connecting surface 10 which rests against an end face 16 of the rotor hub 3. The outer ring of the blade bearing is screwed to the rotor hub 3 by means of the pegs 20, while the inner ring of the blade bearing is screwed to the rotor blade 2by means of the pegs 19 and the anchor 8.
Mechanical simulation calculations and operating practices have shown that due to the partially very high loads acting on the blade bearings of the rotor blades of the wind energy installation, elastic deformations of the blade bearings occur. This elastic deformation leads to a reduction in the life of the blade bearing due to different influencing factors. On the one hand, in the case of bearing sealing, elastic deformation may lead to leaks, so that the design life of the bearing is practically not achieved due to insufficient lubrication of the bearing. On the other hand, elastic deformation of the blade bearing can also lead to the rolling bodies being subjected to loads which cause premature wear or even damage to the rolling bodies or the bearing ring guide rails which cooperate therewith. Thus, for example, an increase in the edge pressure of the rolling elements relative to the guide rail can be brought about by elastic deformation of the vane bearing, which leads to increased wear and a reduction in the life of the vane bearing.
The larger the blade bearing diameter, the more severe the aforementioned phenomenon. In the field of wind power installations, there is a trend to use larger and larger installations, with rotor blades of greater length and rotor roots which are to be connected to the hub having a greater diameter. Therefore, blade bearings of increasingly larger diameters are also required. The greater the ratio of the blade bearing diameter to the bearing ring thickness, the more "soft" the blade bearing behaves, i.e. the greater the elastic deformation which occurs as a result of the loads acting on the blade bearing during operation.
The problem of elastic deformation of the blade bearing and the resulting edge pressure of the rolling element against the guide rail when using essentially cylindrical rolling-element rollers is mentioned in EP 1891327B 1 (see paragraph 0023). As a measure for increasing the service life of the proposed 3-row roller swivel connection, EP 1891327B 1 proposes that the rolling elements "which are subjected to axial forces have at least one bulged transition region, i.e. flat or rounded, between the flank and at least one adjacent end face. In operation, this allows edge pressure to be absorbed in the bearing unit during elastic deformation relative to the guide rail, in that a sufficient contact area with the active surface is ensured also in the rounded transition region. The disadvantage of this proposed solution is that it does not address the aforementioned problems of poor sealing and insufficient lubrication which reduces the life through elastic deformation of the bearing. Furthermore, this solution is disadvantageous in the case of very large bearings, since the deformation may be so great that the rounding of the rolling bodies is not sufficient to reliably avoid unacceptably high edge pressures.
Various other solutions to the problem of being able to counteract the elastic deformation of the blade bearing during operation are known from the prior art. These solutions have the same basic idea of increasing the rigidity of the blade bearing by means of additional stiffening elements and thereby increasing the blade bearing resistance against elastic deformation during operation.
In patent application EP 2933476 a1, a solution is followed in which the rigidity of the blade bearing (pitch bearing) is increased by two stiffening plates (first resilience plate 31, second resilience plate 32). The two reinforcing plates are fixed on the inner ring of the blade bearing. In addition to The stiffening plates, further stiffening measures for increasing The stiffness of The blade bearing are provided, which are fastened to The stiffening plates (paragraph 0070: "The pitch bearing is used for stiffening by a stiffening block while servers as a heat means 40for re-entering The pitch bearing. The pitch bearing 40is used for attaching to The re-entering plates 31. The blade bearing is further stiffened by a stiffening block which serves as a further measure 40for stiffening The blade bearing. The further measure 40is fastened to The stiffening plates 31,32by a reinforcing block
WO 2013/107452 a1 proposes a support structure (support structure 30) for increasing the rigidity of the blade bearing in the radial, circumferential and axial directions. Which is formed by support ribs (support ribs 40). The support structure may have different rigidity along the circumferential direction.
Document US 2013/0052023 a1 teaches to resist elastic deformation of The outer ring (outer ring 15) of The blade bearing by adding material outside The outer ring that deviates from a generally cylindrical shape and is extra (see paragraph 0027: "In order to reduce such deformation of The bearing outer ring 15.The outer bearing is reinforced by adding material to The generally cylindrical shape of The bearing outer ring 15. this material adds … to The outer surface of The generally cylindrical bearing outer ring).
EP 2546512 a1 discloses a reinforcement ring (reinforcement ring 23) for increasing the rigidity, which is connected to the inner ring of the blade bearing. Document EP 2623772 a1 likewise teaches the use of a stiffening ring (reinforing 24) connected to the inner ring of the blade bearing. Patent application WO 2013/076754 a1 also teaches the use of a reinforcement in the form of an annular plate ("reinforcement element 23in form of a ring plate") fixed to the inner ring of the blade bearing.
All the aforementioned reinforcement solutions have the disadvantage that additional parts have to be used to achieve the reinforcement of the blade bearing. This additional part increases the weight of the blade bearing and leads to increased assembly costs and increased material expenditure.
Disclosure of Invention
Against this background, the object of the invention is to provide a bearing arrangement for mounting a rotor blade of a wind turbine, which has a high rigidity against elastic deformation of the rotor bearing, wherein a low weight, a low assembly effort and a low material expenditure of the blade bearing are achieved.
A further object of the invention is to provide a wind power installation in which, even in the case of large rotor blades having a large diameter in the region of the rotor blade root, elastic deformation of the blade bearing due to high loads occurring during operation can be avoided or limited to an acceptable range.
This object is achieved for a bearing arrangement by the bearing arrangement of the invention. Advantageous embodiments of the bearing arrangement according to the invention are given in the dependent claims. This object is achieved for a wind power installation by the wind power installation according to the invention.
According to the invention, the bearing structure is integrated in the hub in such a way and method that the hub optimally supports the guide rail of the bearing and thus minimizes the deformation, in particular the radial deformation, of the guide rail. The integration of the rolling bearing in the wheel hub makes the bearing-wheel hub system more rigid than the flange connection of the rolling bearing known from the prior art on the upper end face of the wheel hub. This reduces, in particular, the radial deformation of the bearing and the guide rail and thus contributes to a reduction in the relative movement of the guide rail perpendicular to the rolling direction of the rollers. In this way, the risk of the False brinell indentation (False Brinelling) effect is minimized.
The bearing structure according to the invention achieves an increase in the rigidity of the blade bearing and thus a greater resistance against elastic deformation of the blade bearing in the event of high loads during operation, without the use of additional reinforcing parts. The bearing structure according to the invention is completed without using additional reinforcing elements. Thereby, the weight of the blade bearing is kept as low as possible. The bearing structure according to the invention can be assembled without increasing the assembly effort, since no separate reinforcing elements have to be handled and assembled. By eliminating a separate reinforcement element, the use of material for the blade bearing is also minimized.
However, for further optimization, it is also possible within the scope of the invention to use reinforcing additional elements. A particularly high rigidity can be achieved by using a reinforcing additional element in the bearing structure in which the bearing ring is integrated in the hub.
The invention is based on a bearing arrangement for supporting a rotor blade of a wind power plant, having a rolling bearing for rotatably supporting the rotor blade about a longitudinal axis of the rotor blade, and having a hub for transmitting a rotation of the rotor blade to a rotor shaft of the wind power plant, wherein the rolling bearing has a first bearing ring, a second bearing ring and rolling bodies arranged between the bearing rings, wherein the bearing rings are rotatable relative to one another, wherein the first bearing ring has a pin extending radially towards the center of the first bearing ring, the pin having a guide track for the first rolling body and a guide track for the second rolling body, wherein the second bearing ring has a plurality of guide rails for the first rolling elements and a guide rail for the second rolling elements, wherein one of the bearing rings is connected to the hub and the other bearing ring is connected to the rotor blade, and wherein the hub has an annular interface region for connecting a rolling bearing. In order to achieve a high rigidity against elastic deformation of the rotor bearing in such a bearing arrangement and to achieve a low weight, a low assembly effort and a low material expenditure for the blade bearing, the invention proposes that one of the bearing rings is integrated in the hub in the region of the interface, so that the material of the hub contributes to a radial reinforcement of the integrated bearing ring.
According to one embodiment of the invention, the hub material for reinforcing the integrated bearing ring is distributed in the region of the interface such that relative deformations between the guide rails of the first and second bearing rings in the radial direction are minimized. The distribution of the hub material in the interface region of the hub is achieved taking into account the rigid behavior of the bearing ring connected to the rotor blade and the rotor blade connected thereto in the operating state thereof. Furthermore, alternating loads due to overturning moments occurring due to the weight of the rotor blades are taken into account. By the distribution of the hub material in the interface region, which is selected according to the invention, no or only a small/minimal relative deformation in the radial direction occurs between the rails of the first and second bearing rings. The specific distribution of the hub material in the interface region and thus the structural design of the interface region of the hub is based on a defined finite element analysis by means of flow and deformation.
The existing material of the hub is thereby optimized according to the invention with regard to its distribution in the hub connection region and serves to increase the flexural rigidity of the blade bearing and thus the resistance to elastic deformation of the blade bearing, in particular in the radial direction, when high loads occur during operation. By increasing the rigidity of the bearing structure according to the invention by means of the hub, it can be said that the material of the hub acts as a reinforcing material for the blade bearing. Thereby eliminating the need for additional stiffening elements. The weight of the blade bearing is thus not increased by the additional, separate reinforcing element, but can be kept as low as possible. The amount of material and the number of parts required for the blade bearing is thereby kept to a minimum.
According to the invention, the blade bearing can be integrated in the hub in different ways. The different schemes are illustrated by the examples below.
According to one embodiment of the invention, the rolling bearing is arranged on the inner circumference of the interface region. In this embodiment, the first bearing ring preferably forms the outer ring of the rolling bearing. This embodiment offers a number of advantages: a) the relatively small overall blade bearing can be realized with a relatively small outer diameter, which results in a relatively low manufacturing outlay, b) the outer ring, because of its integration in the hub, has a large resistance to deformation, in particular radial deformation caused by loads occurring in operation (in particular caused by overturning moments), c) the rigidity of the inner ring against deformation, in particular radial deformation caused by loads occurring in operation (in particular caused by overturning moments), can also be increased by additional reinforcing additional elements. In this embodiment, in which the outer ring is integrated into the hub at the inner circumference of the interface region, a blade bearing which is very stiff in the radial direction can be realized with a low material usage, wherein, in operation, the radial deformation of the bearing rings and thus the undesired relative movement of the guide rails of the two bearing rings with respect to one another is minimized.
The first bearing ring can be formed integrally with the hub, i.e. the hub and the first bearing ring are part of one and the same component. For example, the first bearing ring can be formed from the material of the hub by machining, such as turning or milling, the hub. This embodiment can also be referred to as a concept "fully integrated bearing ring" in order to specify that such an integration of the bearing ring is such that the bearing ring is not a separate part, but rather is an integral part of the hub. In this embodiment, the number of components forming the rolling bearing is particularly low, since the outer ring, which is a separate component, is dispensed with. In this embodiment, no fastening means, such as screws, are required for connecting the first bearing ring to the hub.
Instead of having a "fully integrated bearing ring", the first bearing ring can be designed as a separate bearing ring, which is designed separately from the hub. In this embodiment, the first bearing ring is connected to the hub via a connecting element. Such a connecting element can be, for example, a screw which is screwed, for example, into a threaded bore provided in the hub. The embodiment of the bearing ring according to the invention with a separate bearing ring, which is designed separately from the hub, can be described in the concept of a "partially integrated bearing ring", so that it can be distinguished better in terms of expression from the previously described solution with a "completely integrated bearing ring". On the contrary, the generic term "integrated bearing ring" describes both solutions with a fully integrated bearing ring and solutions with a partially integrated bearing ring.
In both of the previously described embodiments "fully integrated bearing ring" and "partially integrated bearing ring", the material of the hub contributes to the radial reinforcement of the integrated bearing ring. In particular, the hub material contributes to the bending stiffness of the rolling bearing against moments acting on the rolling bearing via the rotor blades. Both the cross-sectional area of the integrated bearing ring and the cross-sectional area of the hub material in the interface region of the bearing ring contribute to the sectional second moment of the cross-section of the relevant part. The cross-sectional secondary shaft moment of the unit consisting of hub and integrated bearing ring, which is critical for the bending resistance, is thus greater than in bearing arrangements in which the rolling bearing ring is not integrated in the hub.
According to one embodiment of the invention, the rolling bearing is arranged on the outer circumference of the interface region. In this case, the first bearing ring preferably forms an inner ring of the rolling bearing.
If the rolling bearing is arranged on the outer circumference of the hub interface region and the first bearing ring forms the inner ring of the rolling bearing, the first bearing ring can be formed in one piece with the hub. In this design, which is arranged on the outer circumference, the bearing ring can also be produced from the material of the hub by means of a cutting process, for example turning or milling, as in the design in which the first bearing ring is located on the inner circumference of the joint region.
In accordance with a preferred embodiment of the rolling bearing arranged on the outer circumference of the connection region, the first bearing ring is provided as a separate part and forms the inner ring of the rolling bearing. The first bearing ring is then constructed separately from the hub and is connected to the hub by means of connecting elements, for example bolts. In this embodiment, for assembly reasons, it is necessary to design the second bearing ring, which forms the outer ring, in a split manner in the axial direction, i.e. it is formed by two part-rings. In addition, the partial rings forming the split outer ring can also be implemented in segments in the circumferential direction, thereby further simplifying assembly or disassembly. In this embodiment, the first bearing ring can be segmented as viewed in the circumferential direction and/or the axial direction. In this context, that is to say that the first bearing ring or the partial ring forming the second bearing ring is segmented in the circumferential direction means that the ring is composed of a plurality of bearing ring segments or partial ring segments over its circumferential extent.
According to one embodiment of the invention, the first interface region of the hub has a first cylindrical contact surface, against which the side face of the first bearing ring contacts. The first cylindrical contact surface extends parallel to the rotational axis of the roller bearing. Since the side faces of the first bearing ring bear against this cylindrical first bearing face of the hub, the cross section of the first bearing ring and the cross section of the hub interface region together form a common cross section which forms the cross section which is critical for determining the second axial moment of the cross section which determines the resistance of the composite consisting of the first bearing ring and the hub interface region against deformation, in particular against deformation caused by bending stresses. The reinforcement of the hub material of the first bearing ring particularly contributes to an increased resistance of the rolling bearing against deformation in the radial direction. In particular, such a relative deformation of the first and second bearing rings with respect to one another, which leads to a displacement of the guide rails of the two bearing rings away from one another in the radial direction, is thereby avoided or at least limited to a low extent. It is this relative movement of the guide rails caused by the deformation of the bearing rings that leads to increased wear of the blade bearings of the wind power installation.
In addition to the first cylindrical contact surface, according to one embodiment of the invention the hub also has a second cylindrical contact surface. The cylindrical second contact surface extends substantially perpendicularly to the cylindrical first contact surface in the radial direction toward the center of the rolling bearing. The end face of the first bearing ring abuts against the cylindrical second abutment face. In this way, the first bearing ring is supported on the hub with its end face facing away from the rotor blade, as viewed in the longitudinal direction of the rotor blade, in a form-fitting manner. By this support of the bearing ring, the rigidity of the composite body consisting of bearing ring and hub is further increased. The material of the hub contributes to an increase in the cross section, viewed in the axial direction, which is critical for the deformation stiffness.
The two cylindrical first and second contact surfaces of the hub form a receiving pocket for the first bearing ring, which is L-shaped in cross section and circumferentially surrounds the latter. In the cylindrical second contact surface, internal threads can be formed for blind holes distributed over the circumference, which are each aligned with a through-hole of the first bearing ring. The first bearing ring is fixedly connected to the hub by means of screws screwed into the blind holes. The first bearing ring and the hub form a rigid component assembly. In this component composite, the first bearing ring has in particular a significantly higher rigidity against the tilting moment which is exerted on the first bearing ring by the second bearing ring connected to the rotor blade.
A number of influencing factors need to be taken into account when dimensioning the interface region of the hub for stiffening. In one aspect, the dimensioning of the interface region is influenced by the thickness of the first bearing ring in the radial direction and in the axial direction. On the other hand, the diameter of the first bearing ring is also taken into account in the dimensioning of the interface region. In addition, the force flow is also important, i.e. it is necessary to take into account in which direction the forces acting on the first bearing ring act on the hub and in particular on the interface region of the hub. The force flow may be different in different hub structure types. The dimensioning of the interface region of the hub is also relevant whether the first bearing ring is "fully integrated" (i.e. is an integral part of the hub), or whether it is "partially integrated", i.e. connected to the hub as a separately constructed part by means of connecting elements, such as bolts or the like. Due to the large number of different influencing factors which differ in their effect in different wind energy installations, unfortunately no unique dimensioning criterion is given which, in all conceivable application cases, always leads to the strengthening of the rolling bearing according to the invention. The specific design of the hub and in particular of the hub interface region is therefore based in each case on a finite element analysis by means of the determination of the flow and the deformation.
The subject matter of the invention is also a wind power installation with at least one rotor blade fastened to a hub and 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 by means of a bearing arrangement according to the invention. Such wind power plants fail less frequently, since the blade bearings have an increased life and therefore have to be replaced or repaired less frequently on the basis of the invention. The availability of a wind power installation equipped with a bearing arrangement according to the invention is greater than the availability of a wind power installation in which the rotor blades are fixed to the hub by means of a bearing arrangement according to the prior art. The invention therefore provides a significant contribution to the economy of the wind energy plant.
Drawings
The invention is further elucidated below on the basis of the drawings showing different embodiments.
Fig. 1 shows a perspective view of a rotor hub of a wind energy plant with an integrated rolling bearing.
FIG. 2 shows a radial half-section through the hub interface region.
Fig. 3 shows an enlarged view of detail B from fig. 2 according to a first embodiment of the invention.
Fig. 4 shows an enlarged view of 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.
Detailed Description
In the different figures, identical components are always denoted by the same reference numerals and are therefore generally also named or referred to respectively only once.
Fig. 1 shows a perspective view of a rotor hub 10 (hereinafter referred to as "hub") for a wind energy plant. The hub 10 has an interface region 11 to which a rotor blade of a wind power plant, not shown in fig. 1, is connected with its rotor blade root. The interface region 11 is of annular design. A total of three connection regions 11 are provided on the hub 10. The rolling bearing 1 is accommodated in the upper interface region 11 in fig. 1. The roller bearing 1 forms a blade bearing, by means of which the rotor blade can be rotated about its longitudinal axis relative to the hub 10, so that the angle of attack of the rotor blade can be adapted to the wind during operation of the wind energy installation.
Fig. 2 shows a radial half-section through the hub 10 according to fig. 1 through the interface region 11 accommodating the rolling bearing 1. It can be seen that the rolling bearing 1 is completely surrounded by the interface region 11 of the hub 10. The rolling bearing 1 comprises a first bearing ring 2 and a second bearing ring 3. The hub material surrounding the roller bearing 1 contributes to the radial reinforcement of the integrated bearing ring 2. The first embodiment of the bearing arrangement according to the invention shown in fig. 2 is shown in fig. 3, once again in an enlarged view. The specific structure of the bearing structure according to the first embodiment of the present invention is further explained with reference to fig. 3.
The first embodiment of the bearing arrangement according to the invention shown in fig. 3 has a first bearing ring 2. The first bearing ring 2 has a peg 6 extending radially towards the centre of the first bearing ring 2. The pin 6 has two guide tracks 7,8 for the first rolling elements 4a,4b and a guide track 9 for the second rolling element 5. Correspondingly, the second bearing ring 3 has two guide tracks 7 ', 8 ' for the first rolling elements 4a,4b and a guide track 9 ' for the second rolling elements 5.The first bearing ring 2 is in the exemplary embodiment shown in fig. 3a component of the hub 10, i.e. it is completely integrated in the hub 10. The guide rails 7,8,9 are thus also part of the hub 10. The "connection" of the first bearing ring 2 to the hub 10 is thus very firm and stiff. No other fastening means, such as bolts, are necessary for connecting the first bearing ring to the hub 10. In terms of the manufacturing process, the first bearing ring 2 can be formed from the material of the hub 10, for example by machining methods such as turning or milling.
The first bearing ring 2 has a peg 6. The bolt 6 has two horizontally oriented guide rails 7, 8. The guide rails 7,8 are formed by guide rail plates 20 or wires 21 applied to the pin 6. The pin 6 furthermore has, on its radially inwardly directed end face, a guide 9 for the second rolling elements 5.The guide rail 9 is likewise formed by a guide rail plate 20 or a wire 21. The rail plate 20 or the wire 21 is advantageously applied to the rails 7,8,9 of the bolt 6 in a form-fitting manner. The hub 10 or the peg 6 thus serves as a carrier for the rail plate 20 or the wire 21. The guideway plates 20 or the wires 21 are hardened or made of hard to very hard material. That is, the rolling bodies 4a,4b,5 do not directly contact the surface of the pin 6 facing the rolling bodies, but the rolling bodies 4a,4b,5 roll on the rail plate 20 or the wire 21. By using separate rail plates 20 or wires 21, the material of the hub 10 does not have to be a hardenable material, in particular a hardenable steel. In order to produce a guide rail on which the rolling bodies roll directly, the surface of the pin 6 does not need to be hardened. It is possible to use low-cost materials for the hub 10, since the required stiffness of the rails 7,8,9 is provided by the individual rail plates 20 or wires 21.
Alternatively, the rails 7,8,9 of the bolt 6 can also be hardened or coated with a hard material. In this case, the rail plate 20 or the wire 21 is not required. The rolling bodies 4a,4b,5 can then roll directly on the guide rails 7,8, 9.
In the exemplary embodiment according to fig. 3, the first bearing ring 2, which is formed in one piece 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 split, as viewed in the axial direction, i.e. it is formed from two partial rings 3a,3 b. The partial rings have guide rails 7 ', 8 ', 9 ' corresponding to the guide rails 7,8,9 of the first bearing ring 2, which are formed by hardened, in particular induction-hardened, surface regions of the partial rings 3a,3 b. The rolling bodies 4a,4b,5 roll directly on the hardened rails 7 ', 8 ', 9 ' of the partial rings 3a,3 b. The partial rings 3a,3b have through holes aligned with each other. Through which the bolts connecting the inner ring 3 of the rolling bearing 1 with the rotor blades at the rotor blade root can pass. In this way, the rotor blades connected to the inner ring 3 are arranged so as to be rotatable relative to the hub 10, so that, for example, the positioning ("pitching") of the rotor blades relative to the wind can be changed during operation.
A second embodiment of the bearing arrangement according to the invention is shown in fig. 4. In contrast to the embodiment according to fig. 3, the first bearing ring 2 is designed as a separate part, which is designed separately from the hub 10. The first bearing ring 2 forms an outer ring of the rolling bearing 1 and the second bearing ring 3 forms an 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 hole in the hub 10 is internally threaded. The first bearing ring 2 is connected to the hub 10 by means of bolts 13. The bolts 13 pass through holes in the first bearing ring 2 and are screwed into blind holes in the hub 10. In this way, the first bearing ring 2 is connected in a rotationally fixed manner to the hub 10.
The first bearing ring 2 has a pin 6 with guide rails 7,8,9 for the rolling bodies 4a,4b, 5. In contrast to the embodiment according to fig. 3, no guide rail plate 20 or wire 21 is required in order to provide a sufficiently stiff guide rail for the rolling bodies. Alternatively, the surface of the pin 6 is hardened, so that the surface itself forms the guide 7,8,9 for the rolling bodies. The rolling bodies 4a,4b,5 roll directly on the surfaces of the pin 6 forming the guide rails 7,8, 9. The guide rails 7,8,9 of the peg 6 are preferably induction hardened. The first bearing ring 2 can in particular be made of hardenable steel, so that the guide rails 7,8,9 of the pin 6 are hardened by induction hardening, so that the rolling bodies 4a,4b,5 are provided with sufficiently hard and wear- resistant guide rails 7,8, 9.
In the exemplary embodiment according to fig. 4, the second bearing ring 3 is formed by two partial rings 3a,3 b. The first partial ring 3a has guide rails 7' for the rolling bodies 4 a. The guide 7' is a complementary guide to the guide 7 of the first bearing ring 2. The second part ring 3b has a guide 8' for the rolling bodies 4b, which is a complementary guide to the guide 8 of the first bearing ring 2. The second part-ring 3b furthermore has a guide 9' for the rolling bodies 5, which is a complementary guide to the guide 9 of the first bearing ring 2. The guide rails 7 ', 8 ', 9 ' of the second bearing ring 3 are also hardened, in particular induction hardened. The rolling bodies 4a,4b,5 roll directly on the hardened rails 7,8,9 and 7 ', 8 ', 9 '.
In the embodiment according to fig. 4, the partial rings 3a,3b forming the inner ring are likewise connected to the rotor blade as described above for the embodiment according to fig. 3.
As an alternative to the embodiment described above with reference to fig. 3 and 4, guide rails 9' for the rolling bodies 5 can also be provided on the first part-ring 3 a. In this case, the dividing plane between the partial rings 3a,3b is then located below the rolling elements 5, rather than above the rolling elements 5 as shown in fig. 3 and 4.
The embodiment according to fig. 4 has a number of further advantages. One advantage is that the construction of the rolling bearing is very similar to the construction of the 3-row roller swivel connections known from the prior art for "blade bearings" for use. It is advantageous for the designer that the behavior of the rolling bearing 1 itself and its components is basically known. Another advantage is that a known and proven-to-practice threaded connection of the inner ring and the rotor blade can be retained. A third advantage is that all components of the bearing can be constructed of the same materials as are already known and proven in prior art 3-row roller swivel connections. A further advantage is that the embodiment according to fig. 4 provides a solution for the customer to complete the assembly, who can integrate it in the hub and connect it to the rotor blade 10 in the supply state.
Fig. 5 shows a third embodiment of the bearing arrangement according to the invention, 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 interface region 11 of the hub 10.
The first bearing ring 2 is integrated in the hub 10 by being constructed in one piece with the hub 10. The first bearing ring 2 is thus completely integrated in the hub 10. The "connection" of the first bearing ring 2 to the hub 10 is thus very firm and rigid. No special fastening means, such as bolts, are required for connecting the first bearing ring 2 to the hub 10. In a production solution, the first bearing ring 2 can be formed from the material of the hub 10, for example by a machining method such as turning or milling.
The first bearing ring 2 has radially outwardly extending pegs 6. The pin 6 has guide rails 7,8,9 for the rolling bodies 4a,4b, 5.The guide rails 7,8 are oriented horizontally. The guide rails 9 are arranged on the radially outwardly directed end faces of the pins 6. The first rolling elements 4a,4b subjected to axially acting forces roll on the horizontally oriented guide rails 7 and 8. The second rolling elements 9, which are subjected to radially acting forces, roll on the guide rails 9 which are directed radially outward. Similar to the exemplary embodiment according to fig. 3, the guide rails 7,8,9 are formed by guide rail plates 20 or wires 21, which are hardened or are formed from hard to very hard materials. That is, the rolling bodies 4a,4b,5 do not directly contact the surface of the pin 6 facing the rolling bodies, but the rolling bodies 4a,4b,5 roll on the rail plate 20 or the wire 21. The rail plate 20 or the wire 21 is advantageously applied to the rails 7,8,9 of the bolt 6 in a form-fitting manner. The guideway plates 20 or the wires 21 are hardened or made of hard to very hard material. The hub 10 or the peg 6 thus serves as a carrier for the rail plate 20 or the wire 21. The guide rails 7,8,9 together with the guide rail plates 20 or the wires 21 can thus be said to form part of the hub 10. By using separate guide rail plates 20 or wires 21, the material of the hub 10 does not have to be a hardenable material, in particular a hardenable steel. In order to produce a rail on which the rolling bodies can roll directly, it is not necessary to harden the surface of the stud 6. A low cost material can be used for the hub 10 because the required stiffness of the rails 7,8,9 is provided by separate rail plates 20 or wires 21.
Alternatively, the rails 7,8,9 of the bolt 6 can also be hardened or coated with a hard material. In this case, the rail plate 20 or the wire 21 is not required. The rolling bodies 4a,4b,5 can then roll directly on the guide rails 7,8, 9.
In the exemplary embodiment according to fig. 5, the first bearing ring 2, which is formed in one piece 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 split, as viewed in the axial direction, i.e. it is formed from two partial rings 3a,3 b. The partial rings have guide tracks 7 ', 8 ', 9 ' corresponding to the guide tracks 7,8,9 of the first bearing ring 2, which are formed by hardened, in particular induction hardened, surface regions of the partial rings 3a,3 b. The rolling elements 4a,4b,5 roll directly on the hardened guide tracks 7 ', 8 ', 9 ' of the partial rings 3a,3 b. The partial rings 3a,3b have through holes aligned with each other. Through which the bolts connecting the outer ring 3 of the rolling bearing 1 with the rotor blades at the rotor blade root can pass. In this way, the rotor blades connected to the outer ring 3 are arranged rotatably relative to the hub 10, so that, for example, the positioning ("pitching") of the rotor blades relative to the wind can be changed during operation.
Fig. 6 shows a fourth embodiment of the invention. As in the exemplary embodiment according to fig. 5, the rolling bearing 1 is arranged on the outer circumference of the interface region 11 of the hub 10. In contrast to the embodiment in fig. 5, in the exemplary embodiment shown in fig. 6 the first bearing ring 2 is designed as a separate component, which is designed separately from the hub 10. The first bearing ring 2 forms an inner ring of the rolling bearing 1 and the second bearing ring 3 forms an outer ring of the rolling bearing 1. The first bearing ring 2 has through holes which align with corresponding blind holes in the material of the hub 10. The blind hole of the hub 10 is internally threaded. The first bearing ring 2 is connected to the hub 10 by means of bolts 13. The bolts 13 pass through holes in the first bearing ring 2 and are screwed into blind holes in the hub 10. Thereby rotationally fixedly connecting the first bearing ring 2 with the hub 10.
The first bearing ring 2 has a pin 6 with guide rails 7,8,9 for the rolling bodies 4a,4b, 5. In contrast to the embodiment according to fig. 5, no guide rail plate 20 or wire 21 is required in order to provide a sufficiently stiff guide rail for the rolling bodies 4a,4b, 5. Alternatively, the surface of the stud 6 is hardened, so that the surface itself constitutes the guide 7,8,9 for the rolling bodies. The rolling bodies 4a,4b,5 roll directly on the surfaces of the bolt 6 forming the guide rails 7,8, 9. The guide rails 7,8,9 of the peg 6 are preferably induction hardened. The first bearing ring 2 can in particular be made of hardenable steel, so that the guide rails 7,8,9 of the pin 6 are hardened by induction hardening to provide the rolling bodies 4a,4b,5 with sufficiently hard and wear- resistant guide rails 7,8, 9.
In the embodiment according to fig. 6, the second bearing ring 3 is composed of two partial rings 3a,3 b. The first partial ring 3a has guide rails 7' for the rolling bodies 4 a. The guide 7' is a complementary guide to the guide 7 of the first bearing ring 2. The second part ring 3b has a guide 8' for the rolling bodies 4b, which is a complementary guide to the guide 8 of the first bearing ring 2. Furthermore, the first part-ring 3a has a guide 9' for the rolling bodies 5, which is a complementary guide to the guide 9 of the first bearing ring 2. The guide rails 7 ', 8 ', 9 ' of the second bearing ring 3 are hardened, in particular induction hardened. The rolling bodies 4a,4b,5 roll directly on the hardened rails 7,8,9 and 7 ', 8 ' and 9 '.
In the embodiment according to fig. 6, the partial rings 3a,3b forming the outer ring are likewise connected to the rotor blade as described above for the embodiment according to fig. 5.
Instead of the previously described embodiments according to fig. 5 and 6, guide rails 9' for the rolling bodies 5 can also be provided on the second part-ring 3 b. In this case, the dividing plane between the partial rings 3a,3b is then located above the rolling elements 5, rather than below the rolling elements 5 as shown in fig. 5 and 6.
The embodiment according to fig. 6 has a number of further advantages. One advantage is that the construction of the rolling bearing 1 is very similar to that of the 3-row roller-swivel connection known from the prior art for "blade bearings" in use. It is advantageous for the designer that the behavior of the rolling bearing 1 itself and its components is basically known. Another advantage is that a known and proven-to-practice threaded connection of the outer ring and the rotor blade can be retained. A third advantage is that all components of the bearing can be constructed of the same materials as have been known and proven in prior art 3-row roller swivel connections. A further advantage is that the embodiment according to fig. 6 provides a completely assembled solution for the customer, who can integrate it in the hub 10 and connect it to the rotor blade in the supply state.
Fastening means in the form of screws 13 are provided in the figures of the present application by way of example to connect the first bearing ring 2 in a rotationally fixed manner to the hub 10. Instead of such a threaded connection, the first bearing ring 2 can also be connected to the hub 10 by other fastening means. Suitable fixing means are, for example: a) a conical locking or clamping element which is screwed in from above or below and which locks or clamps the first bearing ring 2 relative to the hub 10, b) a clamping element or a plurality of clamping elements which clamps the first bearing ring relative to the hub 10, in particular with a positive fit, c) a locking nut which is screwed into the thread and is thereby arranged on the connection region 11 of the hub 10 and locks or clamps the second bearing ring 2 relative to the hub 10, d) a screw which is screwed by means of a screw from the outside of the hub 10 or from the outside of the connection region 11, which screw passes through the connection region 11 of the hub 10 and is screwed into a threaded hole provided in the first bearing ring 2.
In all of the above-described embodiments of the invention,
the bearing rings 2,3 can be designed in a divided manner,
the rolling bodies 4a,4b,5 can be held in the cage or in the cage part, or the rolling bodies can be spaced apart from one another by spacers arranged between the rolling bodies,
the cage/cage parts holding the rolling bodies 4a,4b,5 or the spacers arranged between the rolling bodies may be made of a metallic or non-metallic material. The metallic cage/cage part or the metallic spacer can be coated with plastic. The holder/holder part may be provided with a slider. The material of the slide differs from the material of the cage/cage part.
In all embodiments of the bearing arrangement according to the invention, the rolling elements 4a,4b are provided for receiving axial forces acting on the bearing ring 2, while the rolling elements 5 are provided for receiving radial forces acting on the bearing rings 2, 3.
In all embodiments of the bearing arrangement according to the invention, the rolling elements 4a,4b,5 can preferably be designed as cylindrical rollers or toroidal rollers. If the rolling bodies are configured as cylindrical rollers, the guide rail has a planar shape. If the rolling bodies are designed as toroidal rollers, a guide track shape is provided which is adapted to the roller shape.
Description of the reference numerals
1 rolling bearing
2 first bearing ring
3 second bearing ring
4a first rolling element
4b first rolling element
5 second rolling element
6 bolt
7, 7' guide rail
8, 8' guide rail
9, 9' guide rail
10 wheel hub
11 interface region
12 inner circumference
13 a connecting device; bolt
14 outer circumference of
15 first cylindrical contact surface
16 side face
17 second cylindrical contact surface
18 end face
20 guide rail plate
21 wire
Claims (7)
1. Bearing arrangement for supporting a rotor blade of a wind power plant, comprising a rolling bearing (1) for rotatably supporting the rotor blade about its longitudinal axis and a hub (10) for transmitting the rotation of the rotor blade to a rotor shaft of the wind power plant, wherein the rolling bearing (1) has a first bearing ring (2), a second bearing ring (3) and rolling bodies (4a,4b,5) arranged between the bearing rings (2,3), wherein the bearing rings (2,3) are rotatable relative to one another, wherein the first bearing ring (2) has a pin (6) extending radially towards the center of the first bearing ring (2) and having two guide rails (7,8) for the first rolling bodies (4a,4b) and a guide rail (9) for the second rolling bodies (5), wherein the second bearing ring (3) has a guide rail (9) for the first rolling bodies (4a,4b) and a guide rail (9') for the second rolling body (5), wherein one of the bearing rings (2,3) is connected to a hub (10) and the other of the bearing rings (3,2) is connected to a rotor blade, and wherein the hub (10) has an annular interface region (11) for connecting the rolling bearing (1),
it is characterized in that the preparation method is characterized in that,
one of the bearing rings (2,3) is integrated in the hub (10) in the interface region (11) such that the material of the hub (10) contributes to a reinforcement of the integrated bearing ring (2,3) in the radial direction, the rolling bearing (1) being arranged on an inner circumference (12) of the interface region (11); the first bearing ring (2) is a separate component which is connected to the hub (10) by means of a connecting device (13), and the interface region (11) of the hub (10) has a cylindrical first contact surface (15) against which the side surface (16) of the first bearing ring (2) contacts.
2. The bearing arrangement according to claim 1, wherein the material of the hub (10) for reinforcement of the integrated bearing rings (2,3) is distributed in the interface region (11) such that relative deformation in the radial direction between the guide rails (7,8, 9; 7 ', 8 ', 9 ') of the first and second bearing rings (2,3) is minimized.
3. The bearing arrangement according to claim 1 or 2, wherein the first bearing ring (2) constitutes an outer ring of the rolling bearing (1).
4. A bearing arrangement according to any one of claims 1-2, wherein the hub (10) has a cylindrical second abutment surface (17) against which the end face (18) of the first bearing ring (2) abuts.
5.The bearing arrangement according to any of claims 1-2, wherein the first bearing ring (2) is configured in segments in the circumferential direction and/or in the axial direction.
6. The bearing arrangement according to any of the preceding claims 1-2, wherein the second bearing ring (3) is configured in segments in the circumferential direction and/or in the axial direction.
7. Wind power plant with at least one rotor blade fixed 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 by means of a bearing arrangement according to any one of claims 1 to 6.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102017206246.0 | 2017-04-11 | ||
| DE102017206246.0A DE102017206246A1 (en) | 2017-04-11 | 2017-04-11 | Bearing arrangement for mounting a rotor blade of a wind turbine |
| PCT/EP2018/059099 WO2018189143A1 (en) | 2017-04-11 | 2018-04-10 | Bearing arrangement for mounting a rotor blade of a wind turbine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110914538A CN110914538A (en) | 2020-03-24 |
| CN110914538B true CN110914538B (en) | 2022-06-03 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201880024519.XA Active CN110914538B (en) | 2017-04-11 | 2018-04-10 | Bearing arrangement for mounting a rotor blade of a wind turbine |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN110914538B (en) |
| DE (1) | DE102017206246A1 (en) |
| WO (1) | WO2018189143A1 (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102017128949A1 (en) * | 2017-12-06 | 2019-06-06 | Thyssenkrupp Ag | Rolling bearing assembly and method |
| DE102018217899A1 (en) * | 2018-10-18 | 2019-12-24 | Thyssenkrupp Ag | Rolling bearings, especially large roller bearings, preferably for wind turbines with optimized storage |
| DE102018218275A1 (en) * | 2018-10-25 | 2020-04-30 | Thyssenkrupp Ag | Rolling bearing arrangement and wind turbine |
| DE202019101697U1 (en) * | 2019-03-26 | 2020-07-02 | Liebherr-Components Biberach Gmbh | Slewing bearings |
| DE102020001930A1 (en) | 2020-03-25 | 2021-09-30 | Imo Holding Gmbh | Large warehouse |
| DE102020205669A1 (en) | 2020-05-05 | 2021-11-11 | Thyssenkrupp Ag | Method for producing ring segments and ring segments for a segmented rolling bearing ring with a hardened rolling bearing raceway |
| CN111692053A (en) * | 2020-07-08 | 2020-09-22 | 湘电风能有限公司 | Main shaft system transmission system of wind generating set |
| TR2021015600A2 (en) * | 2021-10-06 | 2022-09-21 | Tekno Kaucuk San As | A BEARING MECHANISM TO PREVENT FALSE BRINELLING DAMAGE IN BEARINGS THAT ARE STATIONARY OR oscillating at small amplitudes |
| CN114542406B (en) * | 2022-03-01 | 2023-03-24 | 哈电风能有限公司 | Bearing system of direct-drive wind power generator |
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- 2017-04-11 DE DE102017206246.0A patent/DE102017206246A1/en active Pending
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- 2018-04-10 CN CN201880024519.XA patent/CN110914538B/en active Active
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Also Published As
| Publication number | Publication date |
|---|---|
| WO2018189143A1 (en) | 2018-10-18 |
| CN110914538A (en) | 2020-03-24 |
| DE102017206246A1 (en) | 2018-10-11 |
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