DE102023132979A1 - Bearing arrangement and wind turbine - Google Patents

Abstract

A bearing arrangement (1), in particular in a wind turbine, comprises a bearing ring (3) and a connecting component (2) connected to the bearing ring (3), wherein at least one insert element (11, 13) is arranged between the bearing ring (3) and the connecting component (2) to counteract any migration of the bearing ring (3) relative to the connecting component (2), which insert element is designed as a sheet metal part with a non-metallic coating on one side, in particular on both sides.

Description

The invention relates to a bearing assembly designed according to the preamble of claim 1, which comprises means that counteract the movement of a bearing ring relative to a connecting component resulting from microslippage. Furthermore, the invention relates to a wind turbine with such a bearing assembly.

The DE 10 2019 118 810 A1 deals with the topic of bearing ring creep in the direction of rotation around the bearing's axis of rotation. As a countermeasure against such bearing ring creep, which could lead to premature wear, the use of positive-locking components is recommended, which prevent both rotation and axial displacement of a bearing ring.

A further anti-rotation and axial locking of a rolling bearing is in the DE 10 2013 220 834 A1 described. In this case, too, there is a positive connection between different components of a bearing arrangement.

Another bearing arrangement with a locking device for the torsion and axial locking of a rolling bearing in a housing is known from DE 10 2012 222 790 B4 The securing device comprises a self-retaining locking washer.

The EP 1 644 648 B1 The invention concerns a bearing ring and a wheel bearing unit. In this case, a bearing ring is secured against circumferential movement by means of bolts that are secured by a press fit or thread. The bolts penetrate a flange formed by the bearing ring.

One in the DE 10 2014 220 258 A1 The bearing assembly described comprises a bearing inner ring, on the inner surface of which a press fit is formed. It is proposed that a coating be arranged at least in some areas on the press fit surface. DE 10 2014 220 258 A1 deals with both assembly-related aspects and the topic of microslip, which can be related to high operating temperatures and the resulting dimensional changes.

The DE 86 26 727 U1 discloses a camshaft assembly consisting of a shaft tube and slipped elements. In this case, the risk of microslippage is reduced by expanding a tube during manufacturing.

• Forschungsbericht FVA 479 IV, IGF-Nr. 16985 BR, Forschungsvereinigung Antriebstechnik e.V.: Abhilfemaßnahmen Wälzlagerwandern, Definition und Auslegung von konstruktiven und tribologischen Abhilfemaßnahmen gegen tangentiale Wanderbewegungen von Wälzlagerringen, 2015

Regarding the topic of rolling bearing ring creep, please refer to the following publication:

• Research report FVA 479 IV, IGF No. 16985 BR, Research Association for Drive Technology eV: Remedial measures for rolling bearing creep, definition and design of constructive and tribological remedial measures against tangential creep of rolling bearing rings, 2015

As part of the research project, various solutions, including form-fitting ones, were developed and their effectiveness was investigated experimentally and using complex 3D FE analyses. A steel intermediate ring placed between a bearing ring and a surrounding structure was investigated both experimentally and experimentally.

The DE 10 2012 221 739 A1 describes a bearing assembly intended for use in a wind turbine, which comprises at least one rolling bearing, namely a tapered roller bearing. The rolling bearing has a first bearing ring connected to the rotor of the wind turbine and a second bearing ring connected to a housing. The first bearing ring connected to the rotor has a cylindrical seating surface with which it sits on a cylindrical section of the rotor. To prevent the bearing ring from being susceptible to cracking, DE 10 2012 221 739 A1 proposes machining the cylindrical seat surface by a hard turning process. Furthermore, it is proposed to arrange a ring element, which is to be made of fiber-reinforced plastic, between an end face of the same bearing ring and an end face of a shoulder of the rotor designed for axial engagement.

The DE 10 2016 203 022 A1 discloses a method for heat treating a steel alloy that can be used in the manufacture of bearings. This case also addresses the potential for microslippage in bearing components. The bearing component can, for example, be a race of a rolling bearing.

The invention is based on the object of providing measures against bearing ring creep that are more advanced than the cited prior art and are particularly suitable for large rolling bearings, for example in wind turbines.

This object is achieved according to the invention by a bearing arrangement having the features of claim 1. The bearing arrangement comprises, in a basic concept known per se, a bearing ring and a connecting component connected thereto, wherein an insert element is arranged between the bearing ring and the connecting component, which counteracts any migration of the bearing ring relative to the connecting component. Migration of the bearing ring is understood here to mean movements of the bearing ring in its circumferential direction due to micro-slippage. According to claim 1, a sheet metal part, for example a sheet steel part, which is coated on at least one side, in particular on both sides, is provided as the insert element that prevents or at least reduces micro-slippage. The coating is made of a non-metallic material. If the sheet metal part is only coated on one side, a non-metallic coating is present on the connecting component, so that in this case too, the components bearing ring, insert element, and connecting component form two flat, stacked contact areas, each formed between a metallic and a non-metallic material.

The sheet metal part coated on one or both sides can, in particular, be arranged in a self-retaining manner in the bearing ring seat. In either case, the coating of the sheet metal part is already present on the sheet metal before the bearing assembly is mounted. The bearing ring, which is installed in the rest of the bearing assembly with the coated sheet metal part interposed, can be an inner ring or an outer ring. In the case of an axial bearing, it can also be a housing washer or a shaft washer.

Regarding the coating of the sheet metal part, various coating materials are available, with the same or different coatings being applied to both sides of the sheet metal part. In any case, inserting the sheet metal part coated on one or both sides requires significantly less manufacturing effort than coating a bearing ring during assembly of the bearing assembly.

The bearing assembly, into which the insert element in the form of the non-metallically coated sheet metal part is integrated, can also be designed as a lightweight construction in the case of large bearings, whereby the term "lightweight construction" in this case is to be seen in relation to comparably dimensioned bearings of conventional design. Especially in lightweight constructions of large dimensions, for example in wind turbines, reduced stiffness of shafts and housings compared to more massive constructions can play a role with regard to the micro-slip of bearing rings in the bearing seat. The insert element, present as a sheet metal part within the bearing assembly according to the application, adapts to any changes in the shape of the surrounding machine elements during operation of the bearing assembly and thus fulfills its function in every operating state.

The coating on the sheet metal part, for example, is an elastomer coating. Depending on the bearing dimensions, the thickness of the elastomer coating can be less than 2 mm. For example, the thickness of the elastomer coating ranges from 200 µm to 2 mm. For bearings of any size, the thickness of the elastomer coating corresponds in particular to at least 0.2 ‰ and at most 5 ‰ of the largest joint diameter between the bearing ring and the connecting component.

Alternatively, a paint coating can be considered for the sheet metal part intended as an insert element. In this case, too, the coating thickness is at least 0.2 ‰ and at most 5 ‰ of the largest joint diameter. Depending on the dimensions of the bearing arrangement, the paint layer can, for example, be less than 200 µm thick. In addition to elastomer coatings and paint coatings, other non-metallic coatings on the sheet metal part are also possible.

For both an elastomer coating and a paint coating, the sheet metal part has a thickness of at least 0.2 mm and a maximum of 5 mm. In general, the thickness of the sheet metal part is in the range of 0.02 ‰ to 5 ‰ of the largest joint diameter. If the bearing ring is an inner ring of a rolling bearing to be mounted on a shaft, the largest joint diameter corresponds to the inner diameter of the bearing ring, assuming a cylindrical inner surface of the bearing ring. The specified thickness is to be measured without the non-metallic coating.

A coating in the form of a paint can, for example, be powder coated. This can drastically reduce microslip amplitudes compared to uncoated metal parts. The sufficient wear resistance of the powder coating ensures that even in the case of local microslip, the properties of the bearing assembly remain virtually unchanged over a long operating period.

If the sheet metal part is coated with a lubricating coating, microslippage occurs to a greater extent. In this case, wear-resistant transfer films form, which remain in the bearing seat.

Compared to lacquer layers, elastomer layers with which the insert element has a lower stiffness. In this case, micromovements are absorbed by elastic deformation, thus effectively counteracting microslip.

According to a first group of embodiments, the insert element is located radially between the bearing ring and a connecting component. This applies both in cases where the connecting component is a shaft and in cases where the connecting component is a housing into which the bearing ring is to be inserted.

According to a second group of exemplary embodiments, in addition to the aforementioned insert element, which has a supporting function in the radial direction, a second, annular disc-shaped insert element is provided, which is subjected to a force in the axial direction. Embodiments are also feasible in which only one annular disc-shaped insert element supporting in the axial direction is provided. In particular, such an annular disc-shaped element can be segmented.

As far as possible segmentations are concerned, there are numerous design options for insert elements to minimize or completely suppress micromovements. This applies both to insert elements that absorb radial forces and to insert elements that support the bearing ring in its axial direction. In the case of annular insert elements that are loaded in the radial direction of the bearing arrangement, several, for example two, three, or more such elements can be arranged one behind the other in the longitudinal direction of the bearing center axis. Furthermore, it is possible to use several ring sections as insert elements instead of a closed ring, which can be spaced apart from one another in the circumferential direction. This applies both to the case of a single annular arrangement of insert elements and in cases where, as already mentioned, several such annular arrangements are arranged one behind the other in the longitudinal direction, i.e., the axial direction, of the bearing arrangement.

Insert elements whose primary or sole function is to support the bearing ring in the axial direction while simultaneously suppressing micro-movements can also be formed from individual, spaced-apart ring segments, for example four segments, each extending over approximately 90°. Furthermore, in the case of axially supporting insert elements, it is possible to nest several such elements within each other, whereby, for example, two or three insert elements of different diameters can be present. Finally, it is possible to combine subdivisions in the circumferential direction with a gradation of diameters. For example, segmentation into four circumferential sections in combination with two diameter ranges used for axial support results in a total of eight individual elements, which are arranged together in an overall annular disk-shaped space between the bearing ring and a surface of the connecting component.

Segmented bearings are particularly advantageous from a manufacturing perspective for large bearings. Compared to a one-piece design of insert elements, the smaller size of the individual elements significantly simplifies coating.

The segmentations or other subdivisions of insert elements can create free spaces within the bearing arrangement, which can in particular absorb temperature-related dimensional changes and/or can be used as space to absorb abrasion.

If the bearing arrangement absorbs both radial and axial forces and comprises two different insert elements—a radially supporting insert element with a cylindrical ring shape and an axially loaded insert element with the basic shape of a ring disk—the forces acting on the different insert elements can vary in magnitude. For example, the radial direction represents the main load direction, which is associated with a bearing contact angle of less than 45°. If, on the other hand, the contact angle is in the range of 45° to 90°, the bearing arrangement has predominantly or entirely the characteristics of an axial bearing.

The material and the layer thickness of the various coatings provided by the insert elements, which are mechanically loaded radially in one case and axially in the other, each relative to the center axis of the entire bearing arrangement, can be adapted to the resulting loading direction of the bearing ring, i.e. to the division of the force acting on the bearing ring into a radial and an axial component.

Such coordination can be expressed, for example, by the fact that the sheet metal part with the stiffer coating due to its thickness and material is located in the force flow of the larger force component. The comparatively stiff, elastically less flexible coating is, in particular, the thinner of the two coatings. If the bearing arrangement predominantly the character of a radial bearing, which is particularly the case with a contact angle of not more than 30°, this means, for example, that the essentially cylindrical insert element is coated on both sides with a varnish, in particular powder varnish or anti-friction varnish, whereas the second, annular disc-shaped insert element is provided on both sides with a comparatively thick elastomer coating.

Various developments provide for the insert element to be coated with different materials on both sheet metal sides. For example, the insert element is coated with an elastomer on one side and a lacquer on the other. In this case, the less elastically flexible, more mechanically resistant coating, which can be in the form of a lacquer layer, can have a thinner layer than the second, comparatively softer coating, in particular the elastomer coating.

When assembling the bearing assembly, it is possible to first bring the insert element into contact with the bearing ring with the more elastically flexible side, namely the side coated with an elastomer. The assembly consisting of the bearing ring and insert element can then be assembled with the connecting component, which is typically a shaft.

The bearing assembly is particularly suitable for use in a wind turbine according to claim 9, regardless of the number of insert elements that counteract microslip and thus the migration of a bearing ring. The bearing assembly can be, for example, a main rotor bearing or a gearbox bearing in a wind turbine. In both cases, the bearing assembly according to the application is designed, for example, as a tapered roller bearing. Regardless of the shape of the rolling elements, the bearing assembly can also be used in other stationary or mobile systems or machines.

• 1 in einer Schnittdarstellung Komponenten einer Lageranordnung einschließlich mehrerer aus beidseitig beschichtetem Blech gefertigter Einlegeelemente zur Verhinderung von Lagerringwandern,
• 2 die Anordnung nach 1 in einer weiteren Schnittdarstellung,
• 3 den Aufbau eines Einlegeelementes der Anordnung nach 1,
• 4 eine alternative Gestaltung eines Einlegeelementes für die Lageranordnung nach 1,
• 5 in Umfangsrichtung segmentierte, radial abstützende Einlegeelemente für die Lageranordnung nach 1,
• 6 mehrere ringförmige, in Axialrichtung hintereinander angeordnete, radial abstützende Einlegeelemente für die Lageranordnung nach 1,
• 7 in Umfangsrichtung segmentierte, axial abstützende Einlegeelemente für die Lageranordnung nach 1,
• 8 in Umfangsrichtung sowie in Radialrichtung segmentierte, axial abstützende Einlegeelemente für die Lageranordnung nach 1,
• 9 in schematischer Darstellung Komponenten einer Lageranordnung einschließlich mehrerer, verschiedenartig gestalteter Einlegeelemente zur Verhinderung von Mikroschlupf und Lagerringwandern,
• 10 in einer Darstellung analog 3 und 4 ein zur Verwendung in einer Lageranordnung vorgesehenes Einlegeelement, welches zwei verschiedene nichtmetallische Beschichtungen aufweist,
• 11 Komponenten einer Lageranordnung, wobei sich Beschichtungen zur Verhinderung von Lagerringwandern teils auf einem Einlegeelement und teils auf einer Welle als Anschlussbauteil befinden.

Several embodiments of the invention are explained in more detail below with reference to a drawing. These show, partly simplified:

• 1 in a sectional view of components of a bearing arrangement including several insert elements made of sheet metal coated on both sides to prevent bearing ring migration,
• 2 the arrangement according to 1 in another sectional view,
• 3 the structure of an insert element of the arrangement according to 1 ,
• 4 an alternative design of an insert element for the bearing arrangement according to 1 ,
• 5 Circumferentially segmented, radially supporting insert elements for the bearing arrangement according to 1 ,
• 6 several ring-shaped, radially supporting insert elements arranged one behind the other in the axial direction for the bearing arrangement according to 1 ,
• 7 Circumferentially segmented, axially supporting insert elements for the bearing arrangement according to 1 ,
• 8 axially supporting insert elements segmented in the circumferential and radial directions for the bearing arrangement according to 1 ,
• 9 a schematic representation of components of a bearing arrangement including several differently designed insert elements to prevent micro-slip and bearing ring creep,
• 10 in a representation analogous 3 and 4 an insert element intended for use in a bearing arrangement, which has two different non-metallic coatings,
• 11 Components of a bearing arrangement, with coatings to prevent bearing ring migration being located partly on an insert element and partly on a shaft as a connecting component.

Unless otherwise stated, the following explanations refer to all embodiments. Corresponding or essentially equivalent parts are identified by the same reference numerals in all figures.

A bearing assembly, designated overall by reference numeral 1, is intended for use in a wind turbine (not shown in detail). The bearing assembly 1 is a tapered roller bearing for supporting a shaft 2, which is generally referred to as a connecting component. A bearing ring 3, i.e., inner ring, contacts both a cylindrical surface 4 and an axial stop surface 5 of the shaft 2. A rolling element raceway is designated 6. Tapered rollers of known shape roll on the rolling element raceway 6. The bearing assembly 1, in a basic design known per se, is capable of absorbing radial forces as well as axial forces in one direction.

On the inner circumferential surface of the bearing ring 3 there is, as can be seen from the 1 and 9 emerges, an annular circumferential recess 8, so that a radial gap 7 between the bearing ring 3 and the shaft 2. In the present case, the gap 7 extends, measured in the longitudinal direction of the shaft 2 and thus the rotational axis of the bearing arrangement 1, over a greater width than the rolling element raceway 6. Thus, the gap 7 extends in the axial direction of the bearing arrangement 1 over more than half the width of the bearing ring 3.

Between one end face of the bearing ring 3 - in the arrangements according to the 1 and 9 A further axial gap 9 is formed on the left side of the bearing ring 3 and the axial stop surface 5. At this point, the bearing ring 3 has an annular disk-shaped recess 10. An insert element 11, 13 is inserted into each of the recesses 8, 10, which contacts the cylindrical surface 4 provided by the shaft 2 or the axial stop surface 5 and contributes significantly to preventing bearing ring creep, i.e., undesired rotation of the bearing ring 3 relative to the shaft 2.

The insert element designated 11, which has a cylindrical basic shape and concentrically surrounds the cylindrical surface 4, transmits radial forces between the bearing ring 3 and the shaft 2. The insert element 11 is, apart from the design according to 11 , which will be discussed separately, is a sheet metal part coated on both sides. In the present case, a sheet metal strip 12 bent into a sleeve is generally referred to as the base body of the insert element 11. The base body 12, in the form of a sheet metal strip, has a thickness d ₁₂ . d ₁₁ denotes the total thickness of the coated insert element 11.

The coatings of the insert element 11 are designed according to the 1 to 3 in the form of an inner powder coating layer 15 and an outer powder coating layer 16. The designation "inner" in this case means that the corresponding layer 15 is applied to the surface of the base body 12 facing the bearing ring 3. The thickness of the layers 15, 16 is designated d ₁₅ and d ₁₆ respectively and in this case is less than 200 µm. The thickness d ₁₂ of the base body, i.e. the sheet thickness, is in the range from 0.2 mm to 5 mm. The powder coating layers 15, 16 have a high coefficient of friction, so that microslip between the shaft 2 and the bearing ring 3 occurs to a very small extent at most compared to conventional bearing designs. Local microslip is tolerable due to the high wear resistance of the layers 15, 16.

The insert element 13 inserted into the annular disc-shaped recess 10 has, in principle, the same structure as the cylindrical insert element 11. A sheet metal disc 14 forms the annular disc-shaped base body of the insert element 13. The wall thickness of the base body 13 corresponds in the 1 sketched case corresponds to the wall thickness d ₁₂ of the base body 12.

In the case of the annular disc-shaped insert element 13, which supports the bearing in the axial direction, a first powder coating layer 15 contacts one end face of the bearing ring 3, while an outer powder coating layer 16 rests against the axial, flat stop surface 5. Both insert elements 11, 13 are provided as sheets coated on both sides before assembly of the bearing assembly 1. This eliminates the need for coating work on the bearing ring 3 or the shaft 2.

In 4 the structure of an alternative insert element 11 is outlined, which is intended for use in the bearing arrangement 1 according to 1 In a corresponding manner, an alternative annular disc-shaped insert element 13 can be designed, which is also used in the bearing arrangement 1 according to 1 can be installed, whereby the layer structure loaded in the axial direction according to 4 with the cylindrical insert element 11 according to 3 can be combined.

In the case of the radially or axially supporting insert element 11 according to 4 Instead of two powder coating layers, there is an inner elastomer layer 17 and an outer elastomer layer 18. The elastomer layers 17, 18 have a thickness d ₁₇ and d ₁₈ , respectively, which, as can be seen from a comparison of the 3 and 4 shows, each of the layer thicknesses d ₁₅ , d ₁₆ significantly exceeds.

As in 10 As shown by way of example, a powder coating layer 15, 16 can be applied to one surface of the insert element 11, 13 and a comparatively thick elastomer layer 17, 18 can be applied to the opposite surface of the same insert element 11, 13, so that an asymmetrical cross-sectional design of the insert element 11, 13 is present. In both symmetrical and asymmetrical cross-sectional designs, it is possible to replace at least one powder coating layer 15, 16 with a layer of anti-friction coating.

In the case of 4 The thickness d ₁₇ , d ₁₈ of each elastomer layer 17, 18 is more than 200 µm, but less than 2 mm. Regarding the functionality of the elastomer layers 17, 18, there are significant differences from the function of the powder coating layers 15, 16. Compared to the thin, less flexible powder coating layers 15, 16, the elastomer layers 17, 18 exhibit significantly lower stiffness. Micromovements In this case, the forces are largely absorbed by elastic deformation. Ultimately, this also represents an effective measure for suppressing microslip.

The 5 and 6 illustrate different possibilities of subdividing the radial force absorbing insert element 11. According to 5 The insert element 11, formed as a sheet metal with a non-metallic coating on both sides, is divided into four non-contacting segments, each extending over a circumferential area of slightly less than 90°. The maximum joint diameter available for the installation of the segmented insert element 11 in this case is generally designated DF. The center axis of the bearing ring 3 and thus of the entire bearing assembly 1 is designated MA. 6 Three similar sleeve-shaped insert elements 11 are arranged one behind the other in the axial direction of the bearing arrangement 1, with all insert elements 11 contacting the cylindrical inner surface of the bearing ring 3 (not shown here) as well as the surface 4 of the shaft 2. In a manner not shown, the insert elements 11 can also be additionally segmented in the circumferential direction in this case.

The 7 and 8 show different variants of axially supporting insert elements 13. In the case of 7 is, in principle, comparable to the design according to 5 , a division into four equal segments is given. This division is according to 8 further developed in that the insert element 11 was additionally split into inner and outer segments, so that the insert element 11 is formed from a total of eight individual elements.

The design according to 9 differs from the embodiment according to 1 in that the radially loaded insert element 11 has a different structure than the axially supporting insert element 13. In the 9 In the design outlined, the sleeve-shaped insert element 11 is an elastomer-coated sheet metal part, whereas the annular disc-shaped insert element 13, which is not segmented here, is a sheet metal part painted on both sides. Conversely, in a manner not shown, the latter insert element 13 could also be provided with elastomer layers 17, 18, while the cylindrical insert element 11 is coated with paint layers 15, 16.

The 10 The design of an insert element 11 shown is also suitable for use as a radially supporting element as well as for use for axial support of the bearing ring 3. As can be seen from 10 As can be seen, a coating 16 formed as a lacquer layer is combined with an elastomer layer 17 on the opposite side of the base body 12. The elastomer layer 17 is significantly thicker than the lacquer layer 16.

Deviating from the examples of implementation according to the 1 to 10 is in the case of 11 One of the two non-metallic layers, namely the lacquer layer 16, is not applied to the insert element 11, but rather to the shaft 2. The base body 12 of the insert element 11 in this case carries exclusively an elastomer layer 17. This is intended for contacting the inner surface of the bearing ring 3, i.e. the inner ring of the bearing arrangement 1 designed as a rolling bearing.

In a comparable design not shown, in the case of the axially supporting insert element 13, its base body 14 could also be provided with a non-metallic coating 15, 17 on only one side, while the second non-metallic layer 16, 18 is located on the axial stop surface 5.

List of reference symbols

1

Bearing arrangement

2

Shaft, connecting component

3

bearing ring

4

cylindrical surface

5

axial stop surface

6

Rolling element raceway

7

Gap space, radial

8

ring-shaped recess

9

Gap space, axial

10

Ring-shaped recess

11

Insert element, radially supporting

12

Base body of the insert element 11, sheet metal strip

13

Insert element, axially supporting

14

Base body of the insert element 13, sheet metal disc

15

Powder coating, inside

16

Powder coating, exterior

17

Elastomer layer, inside

18

Elastomer layer, outside

d11

Thickness of the insert element 11

d12

Thickness of the base body 12

d15

Thickness of the powder coating layer 15

d16

Thickness of the powder coating layer 16

d17

Thickness of the elastomer layer 17

d18

Thickness of the elastomer layer 18

DF

Joint diameter

MA

central axis

QUOTES CONTAINED IN THE DESCRIPTION

This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 10 2019 118 810 A1 [0002]
• DE 10 2013 220 834 A1 [0003]
• DE 10 2012 222 790 B4 [0004]
• EP 1 644 648 B1 [0005]
• DE 10 2014 220 258 A1 [0006]
• DE 86 26 727 U1 [0007]
• DE 10 2012 [0010]
• DE 10 2016 203 022 A1 [0011]

Cited non-patent literature

• Remedial measures for rolling bearing creep, definition and design of constructive and tribological remedial measures against tangential creep of rolling bearing rings, 2015 [0008]

Claims (10)

Bearing arrangement (1), with a bearing ring (3) and a connecting component (2) connected to the bearing ring (3), wherein an insert element (11, 13) is arranged between the bearing ring (3) and the connecting component (2) to counteract any migration of the bearing ring (3) relative to the connecting component (2), characterized in that a sheet metal part which is non-metallically coated on at least one side is provided as the insert element (11, 13). Bearing arrangement (1) according to Claim 1 , characterized in that the insert element (11, 13) is provided with an elastomer coating (17, 18) which has a thickness (d ₁₇ , d ₁₈ ) of 0.2 ‰ to 5 ‰ of the largest joint diameter. Bearing arrangement (1) according to Claim 1 , characterized in that the insert element (11, 13) is coated with a lacquer layer (15, 16) with a thickness (d ₁₅ , d ₁₆ ) of 0.2 ‰ to 5 ‰ of the largest joint diameter. Bearing arrangement (1) according to one of the Claims 1 until 3 , characterized in that the thickness (d ₁₂ ) of a metallic base body (12) of the insert element (11, 13) is 0.02 ‰ to 5 ‰ of the largest joint diameter. Bearing arrangement (1) according to one of the Claims 1 until 4 , characterized in that a plurality of insert elements (11, 13), namely at least one cylindrical, radially supporting insert element (11) and at least one axially supporting insert element (13), are arranged between the bearing ring (3) and the connecting component (2). Bearing arrangement (1) according to Claim 5 , characterized in that the various sheet metal parts functioning as insert elements (11, 13) differ from one another with regard to at least one of the two properties of layer thickness and coating material. Bearing arrangement (1) according to Claim 6 , characterized in that the bearing ring (3) is provided for supporting two force components of different sizes, namely an axial and a radial force component, wherein the insert element (11, 13) which is provided with the thinner, less elastically flexible coating (15, 16) compared to the other insert element (13, 11) is located in the force flow of the larger force component. Bearing arrangement (1) according to one of the Claims 1 until 7 , characterized in that the insert element (11, 13) is coated on its two sheet metal sides with different materials, namely on one side with an elastomer and on the second side with a varnish. Wind turbine, comprising at least one bearing arrangement (1) according to Claim 1 . Wind turbine according to Claim 9 , characterized in that the bearing arrangement (1) is designed as a tapered roller bearing.

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