DE102022132745A1 - Elastomer bushing and elastic bearing for wind turbines - Google Patents

Abstract

The present invention relates to an elastomer bushing for an elastic bearing of a drive train component of a wind turbine, in particular a gearbox on a housing, such as a machine support, of a wind turbine, comprising two half-shells each made from an elastomer piece and a bearing device which at least partially decouples at least one half-shell from the drive train component and/or the housing and has a reduced static and/or sliding friction compared to the elastomer material.

Description

The present invention relates to an elastomer bushing for an elastic bearing of a drive train component of a wind turbine. Furthermore, the present invention relates to an elastic bearing, in particular a decoupling bearing, for supporting a drive train component, in particular a gearbox, of a wind turbine, in particular on its housing, such as a machine carrier.

In wind turbines, a large amount of torque is transferred from the motor to the gearbox and from there to the generator. To reduce the dynamic loads on the gearbox and the supporting structure, elastic bearings are usually used in the gearbox supports. The elastic bearings have elastic bushings for oscillation and vibration decoupling, which are integrated into the drive train bearings and are, for example, part of the floating bearing unit in the drive train. The floating bearing unit is made up of four elastic bushings and the roller bearing unit in the gearbox. The elastic bushings are connected to the gearbox via the torque support (axle bolt) and to the housing or machine support via bearing blocks. The elastic bushings must, on the one hand, withstand the high and fluctuating forces acting on the bearings, for example as a result of wind, and, on the other hand, be as soft as possible in the longitudinal direction to ensure that the axle bolt can move freely.

From the EN 102020119832 A1 A generic elastic bearing with improved flexibility in terms of adjustability of the axial and/or radial stiffness is disclosed, which consists of two half-shells made of an elastomer with a predetermined hardness, which have a varying axial stiffness in the direction of their longitudinal axis. Thus, on the one hand, the considerable load requirements, especially in the radial direction, can be met and at the same time the axial stiffness can be adjusted depending on the specific requirements. The EN 102020119832 A1 The elastic bearing described does indeed have a good ratio of radial stiffness to axial stiffness, i.e. high stiffness in the vertical and horizontal directions and lower stiffness in the axial direction. However, it has been found that the axial stiffness is still too high for the intended purpose.

Furthermore, the US 2013/0202232 A1 A bearing for a main shaft of a wind turbine is described which is complex in terms of construction and is difficult to assemble, in which multi-part plain bearing elements are combined with a multi-layer casing, whereby the inner surface of the casing is coupled with a plain bearing element and a sliding piece.

It is an object of the present invention to improve the disadvantages of the known prior art, in particular to provide an elastomer bushing and an elastic bearing for wind turbines in which the conflicting objectives of high radial stiffness and low axial stiffness are resolved and/or which has a reduced axial stiffness without the radial stiffness being reduced.

This problem is solved by the features of the independent claims.

According to this, an elastomer bushing is provided for an elastic bearing of a drive train component of a wind turbine. For example, it is an elastomer bushing for an elastic bearing of a gearbox on a housing, such as a machine frame, of a wind turbine. Elastic bearings are used in wind turbines to absorb the dynamic loads that act on the drive train component and the housing. The elastomer bushing can be used to dampen and decouple oscillations and/or vibrations. With regard to the basic installation situation of the elastomer bushing or the elastic bearing, please refer to EP 2 516 883 A1 , the relevant content of which is incorporated into the present application by reference.

The elastomer bushing according to the invention comprises two half shells, each made from an elastomer piece, in particular monolithic and/or with a Shore hardness of more than 85 Shore A. The Shore hardness is a material characteristic value for elastomers and plastics, which is defined in the standards DIN EN ISO 868, DIN ISO 7619-1 and ASTM D 2240-00. The half shells can be made from the same material and/or have the same dimensions. In an assembled state in the elastic bearing, the two half shells can rest on one another at the front to form a particularly cylindrical passage, for example for a fastening part of the drive train component, such as the torque support or the axle bolt. The wall thickness of the half shells can be significantly smaller than their circumferential extent. In cross section, the half shells can have a c-shape or a half-ring shape. The preferred Shore hardness of the half shells, especially of the elastomer piece material, ensures the necessary load capacity, whereby, for example, compared to standard rubber-metal elastomer bushings, up to four times higher loads can be absorbed with comparable deformation, while at the same time it is possible to Elastomer bushings can be made significantly smaller. This allows for lower component weight, lower component costs and smaller component dimensions.

Furthermore, the elastomer bushing according to the invention comprises a bearing device that decouples at least one half-shell from the drive train component and/or the housing at least in sections and has a reduced static and/or sliding friction compared to the elastomer material of the half-shells. The elastomer bushing can thus be designed in such a way that it acts as an elastomer body with spring-elastic properties in the radial direction, in particular vertically and horizontally and in the spatial directions in between, while in the axial direction, i.e. in the longitudinal axis direction of the elastomer bushing, it is designed as a supporting plain bearing and thus generates only minimal reaction forces. On the one hand, this means that the high loads acting on elastic bearings in wind turbines in the radial direction can be counteracted by a high spring stiffness, but on the other hand the conflicting objectives of achieving the lowest possible stiffness in the axial direction can be resolved by minimizing the transferable forces into axial forces. For example, in a normal operating state, forces between 750 kN and 1000 kN act on an elastomer bushing of an elastic bearing, whereby a minimum radial stiffness in the vertical direction of 150 kN/mm is advantageous. In the horizontal direction, forces in the range of 0 kN to 500 kN act on the elastomer bushing in the normal operating state, whereby a minimum radial stiffness in the horizontal direction of 160 kN/mm is preferable. In an axial direction oriented in the longitudinal axis of the elastomer bushing, a maximum stiffness of 12 kN/mm is sufficient to meet the requirements of the elastic bearing. Because the sliding and/or static friction in the axial direction, i.e. the longitudinal axis direction of the bushing, is reduced by the inventive measure of the at least partially decoupling bearing device, but the desired spring stiffnesses transverse to the longitudinal axis direction are nevertheless maintained, the elastomer bushing can move in a floating manner or give way in its longitudinal axis direction, i.e., for example, in the direction of a main shaft connecting the transmission to the machine carrier, and in doing so absorb only a small amount of axial forces in order to establish the lowest possible axial stiffness.

In this context, a further aspect of the present invention consists in retrofitting existing elastomer bushings made of half-shell pairs formed from elastomer pieces with the bearing device according to the invention, at least one half-shell being decoupled from the drive train component and/or the housing at least in sections.

According to an exemplary embodiment of the present invention, the bearing device has a coating that covers an outer and/or inner circumference of the half-shell. The coating can also cover the outer and/or inner circumference of the corresponding half-shell only in sections, i.e. only in sections in the circumferential direction and/or in the longitudinal axis direction. The coating essentially results in a sandwich construction of half-shell, coating and drive train component and/or housing part, so that the decoupling between the half-shell and the drive train component or housing part, which reduces the axial rigidity, is realized. The coating can be shaped to the corresponding half-shell and/or the housing or the drive train component. For example, the coating can cover the half-shell flatly and/or at least 50%, in particular at least 60%, 70%, 80% or at least 90%, in particular in order to achieve the largest possible decoupling between the drive train component and the housing and the best possible reduction in axial rigidity.

According to an exemplary development of the elastomer bushing according to the invention, the coating is designed as a bushing, in particular as a half-bush, and/or made of plastic, such as PTFE, polyamide, PET polyester, or polyethylene terephthalate, or of metal, such as brass, bronze or sintered metal, or a dry lubricant, such as graphite. For example, the coating is designed in two parts, corresponding to the half-shells, with one coating assigned to each half-shell. The coating can also be designed in several parts and include further parts in order to cover sections of the inner and/or outer peripheral surfaces of the housing and/or the drive train component.

In a further exemplary embodiment of the elastomer bushing according to the invention, the bearing device has a lubricant, in particular a solid and/or grease lubricant. In particular, the bearing device is formed from this. The measures described according to the invention provide easy-to-implement options for establishing the conflicting objectives of high rigidity in the radial direction, both horizontally and vertically, and in every direction in between, while the axial rigidity is to be as low as possible in order to meet the requirements of the gearbox manufacturers.

According to a further exemplary embodiment of the present invention, the bearing device has a coating, in particular made of PTFE, in particular the bearing device is formed from it. By coating the half-shell, a firmly adhering layer made of a particularly shapeless material can be applied to the surface of the half-shell, wherein the coating can be applied, for example, by chemical, mechanical, thermal and/or thermomechanical process technology. For example, the half-shell can be mechanically and/or chemically pretreated before the coating is applied.

In a further exemplary embodiment of the elastomer bushing according to the invention, at least one half-shell has a greater radial stiffness in a first radial direction transverse to the longitudinal axis direction, in particular vertical direction, than in a second radial direction transverse to the longitudinal axis direction, in particular horizontal direction. For example, at least one half-shell can have a stiffening structure oriented in the first radial direction, in particular horizontal, such as a stiffening projection or a stiffening rib, which is able to absorb further forces in order to increase the radial stiffness in this direction. For example, between 750 kN and 1000 kN act on an elastomer bushing of an elastic bearing in a normal operating state, with a minimum radial stiffness in the vertical direction of 150 kN/mm being advantageous. In the horizontal direction, forces in the range of 0 kN to 500 kN act on the elastomer bushing in the normal operating state, with a minimum radial stiffness in the horizontal direction of 160 kN/mm being preferable. In an axial direction oriented in the longitudinal axis of the elastomer bushing, a maximum stiffness of 12 kN/mm is sufficient to meet the requirements of the elastic bearing.

According to an exemplary development of the present invention, at least one half-shell has at least one contact projection extending in the direction of the longitudinal axis, in particular by at least 30%, 40%, or at least 50% of the longitudinal extent of the half-shell, such as a contact web for the bearing device, in particular the lining. In an exemplary further development, the at least one half-shell has two contact projections which are arranged at a distance from one another in the circumferential direction such that the bearing device, in particular the lining, rests on the front side, i.e. at the circumferential ends, on both contact projections. For example, the lining or the bearing device can be clamped between the two contact projections. The contact projection, in particular the contact projections, can have a contact flank that is strongly inclined with respect to the outer and/or inner surface of the half-shell and/or a rear flank facing away from the bearing device or the lining, which is inclined with respect to the outer and/or inner circumference of the half-shell, in particular is less inclined than the contact flank.

In a further exemplary embodiment of the elastomer bushing according to the invention, two circumferential ends of the half shells facing each other, which rest on each other in particular to form the bushing, are designed to form a tongue and groove and/or dovetail joint with two bearing block parts on the wind turbine side, in particular on the machine support side, for receiving the elastomer bushing in a particularly clamping manner. The positive and/or force-fitting connection of the half shells with the bearing block parts ensures reliable and simple assembly, since the assembly sequence and position of the components are defined, and also provides a secure safeguard against relative movement of the components to each other transversely to the longitudinal axis direction.

In an exemplary development of the elastomer bushing according to the invention, the circumferential ends are formed as radial projections extending in the direction of the longitudinal axis of the half-shells, the cross-section of which is shaped in the radial direction to engage behind a groove formed in the bearing block parts. In other words, the radial projection extends at least 30%, 40% or 50% of the longitudinal extension of the half-shells and protrudes radially from the outer circumference of the half-shells in order to be able to engage in the grooves formed in the bearing block parts and in particular to be able to engage behind the groove flanks of the groove. This ensures that the half-shells are held in a positionally secure manner in the bearing block parts.

In an exemplary embodiment of the present invention, at least one elastomer piece comprises polyurethane. For example, it is polyurethane-polyester or polyester-urethane rubber. Urelast is preferably used. The materials mentioned for the elastomer piece have proven to be particularly advantageous, in particular because of their high load-bearing capacity, high tensile strength and very good wear behavior. Above all, because of the high load-bearing capacity, it is possible to make the elastomer bushing smaller. This results in advantages in terms of installation space, material expenditure and costs. Urelast is generally a cast elastomer.

According to a further exemplary embodiment of the elastomer bushing according to the invention, the half shells each have a central axis which are oriented concentrically to one another when the half shells rest on one another and/or in the assembled state in the bearing, in particular in the operating state. The concentric arrangement results in further installation space advantages. In order to establish different stiffnesses in different directions, it is no longer necessary to configure the half shells ovally or elliptically, for example, and/or to arrange them eccentrically to one another in the assembled state in the elastic bearing. In the assembled state, the elastomer piece half shells essentially form a ring shape, with a particularly cylindrical passage for a fastening part of the drive train component, such as the torque arm or the axle bolt, and an at least approximately round outer circumference, which in the assembled state in the bearing, in particular in the operating state, is contacted by two bearing block parts, in particular is completely surrounded and/or in particular is clamped.

In an exemplary development of the elastomer bushing according to the invention, its radial stiffness transverse to the longitudinal axis is greater than its axial stiffness in the longitudinal axis direction. For example, the axial stiffness is less than 10%, in particular less than 5% or less than 2% of the radial stiffness. The specified ratios have proven to be particularly advantageous with regard to the specific requirements in elastic bearings in wind turbines for supporting the drive train component on the housing, in particular the machine frame, of the wind turbine. When using the elastomer bushing in floating bearings, a particularly low axial stiffness is desired. It is also possible to design the radial stiffness depending on the orientation, whereby, for example, the radial stiffness in the horizontal direction can be greater or smaller than the radial stiffness in the vertical direction. For example, the radial stiffnesses in the various directions can differ from one another by 5% or 8% or even by more than 10%.

In a further exemplary embodiment of the elastomer bushing according to the invention, one half-shell has a greater radial stiffness transverse to the longitudinal axis than the other half-shell. For example, the stiffness deviation of the two half-shells from one another is between 0.1% and/or at most 5%.

According to a further aspect of the present invention, which can be combined with the preceding aspects and exemplary embodiments, an elastic bearing, in particular a decoupling bearing, is provided for supporting a drive train component, in particular a gearbox, of a wind turbine, in particular on its housing, such as its machine carrier. For example, it is an elastic bearing of a gearbox on a housing, such as a machine carrier, of a wind turbine. Elastic bearings are used in wind turbines to absorb the dynamic loads that act on the drive train component and the housing. Oscillation and/or vibration damping and decoupling can take place by means of the elastic bearing. With regard to the basic installation situation of the elastic bearing, reference should be made to EP 2 516 883 A1 , the relevant content of which is incorporated into the present application by reference.

The elastic bearing according to the invention comprises an elastomer bushing designed in particular according to one of the previously described aspects or exemplary embodiments and two bearing block parts for receiving the elastomer bushing in a particularly clamping manner.

In an exemplary development of the elastic bearing according to the invention, the bearing block parts have grooves facing each other, in particular identically designed, and radial projections are formed on two circumferential ends of the superimposed half shells facing each other. The grooves and the radial projections are coordinated in shape with each other. According to an exemplary development, the radial projections are shaped to engage behind groove flanks of the groove in the radial direction, in particular in the manner of a tongue and groove and/or dovetail connection. In the assembled state, the two grooves of the bearing block parts lie directly above each other and delimit a common receiving space for the radial projections of the half shells engaging therein. By matching the shape of the grooves and radial projections, in particular the positive and/or non-positive engagement of the groove flanks by the radial projections, a particularly compact and fixed elastic bearing is created, so that relative movements transverse to the longitudinal axis direction are excluded.

According to a further aspect of the present invention, which can be combined with the preceding aspects and exemplary embodiments, a wind turbine is provided with an elastic bearing according to one of the aspects described above.

Preferred embodiments are specified in the subclaims.

• 1 eine perspektivische Prinzipskizze zum Einsatzzweck beispielhafter Ausführungen erfindungsgemäßer elastischer Lager;
• 2 eine Detailansicht eines elastischen Lagers in Explosionsdarstellung;
• 3 eine beispielhafte Ausführung eines erfindungsgemäßen elastischen Lagers in Vorderansicht;
• 4 das elastische Lager aus 3 in Schnittansicht; und
• 5a -7b schematische Prinzipskizzen zu verschiedenen Ausführungsbeispielen elastischer Lager beziehungsweise erfindungsgemäßen Elastomerbuchsen.

In the following, further properties, features and advantages of the invention are described by means of Description of preferred embodiments of the invention with reference to the accompanying exemplary drawings, in which:

• 1 a perspective schematic diagram of the intended use of exemplary embodiments of elastic bearings according to the invention;
• 2 a detailed view of an elastic bearing in exploded view;
• 3 an exemplary embodiment of an elastic bearing according to the invention in front view;
• 4 the elastic bearing made of 3 in sectional view; and
• 5a -7b Schematic principle sketches of various embodiments of elastic bearings or elastomer bushings according to the invention.

Based on 1 to 7b Embodiments of elastic bearings according to the invention, which are generally provided with the reference number 1, as well as of elastomer bushings according to the invention, which are generally provided with the reference number 3, of elastic bearings 1 are described. The elastic bearing 1 serves according to the 1 and 2 to provide elastically damping support for a gearbox 11 of a wind turbine on its housing, in particular a machine carrier, in order to absorb and dampen the dynamic loads acting on the drive train component, the gearbox and/or the housing. 1 and 2 the gearbox 11 is indicated schematically and comprises a large-dimensioned main shaft 13, gearbox supports 15, 17, on each of which a gearbox bearing pin 19, 21 is arranged, which are mounted or supported on the housing of the wind turbine via a pair of elastomer bushings.

According to the embodiments, an elastic bearing 1 according to the invention comprises the following main components: an elastomer bushing 1 according to the invention, which is formed from two half-shells 5, 7 and a bearing device 9 that decouples the gear supports 15, 17 from the housing; two bearing block parts 23, 25, which are in particular identically designed, for receiving the elastomer bushing 1 in a particularly clamping manner, which are to be arranged or are arranged on the housing side and are decoupled or dampened from one another by the elastic bearing 1 with respect to oscillation and/or vibration.

Referring to the first embodiment of an elastic bearing 1 according to the invention according to 2 The individual components are shown in an exploded view for better clarity. The two clamping halves or bearing block parts 23, 25 delimit a cylindrical receiving space 27 for supporting the respective gear bearing journals 19, 21 and for receiving an elastomer bushing 1 for decoupling the gear bearing journals 19, 21 from the housing of the wind turbine in a way that dampens oscillations and/or vibrations. The two half-shells 5, 7 have a semicircular shape in cross-section and have a sectionally constant cross-section in the longitudinal direction, i.e. along the longitudinal axis A. The half-shells 5, 7 are concavely curved and have an open side that faces the other half-shell 7, 5, so that the half-shells 5, 7 delimit a semi-cylindrical, hollow interior, which serves to accommodate a connecting part of the drive train component, namely, for example, a transmission or torque support 19, 21. An inner wall 29 of the half-shells 5, 7 delimiting the interior is uniformly curved along the longitudinal axis A.

According to the invention, at least one half-shell 5, 7 is decoupled at least in sections from the drive train component and/or the housing by means of a bearing device 9 which has a reduced static and/or sliding friction compared to the elastomer material of the half-shells 5, 7. According to 2 to 4 the bearing device 9 is formed by a pair of half-bushings 31, 33, each forming a plain bearing lining, which can be made of plastic, such as PTFE, polyamide, PET polyester, or polyethylene terephthalate, or of metal, such as brass, bronze, sintered metal, or a dry lubricant such as graphite. The linings 31, 33 are arranged in a sandwich manner between the gear bearing journal 19, 21 or the half-shell 5, 7 assigned to it and the outer bearing block part 23, 25 and ensure a reduction in the axial resistance force or the ability to absorb axial forces. The linings 31, 33 are shaped in relation to the half-shell 5, 7 and lie flat on the outer surfaces facing the bearing block parts 23, 25 or cover them over a large area. The half shells 5, 7 have on their outer surfaces facing the respective bearing block parts 23, 25 contact projections or contact webs 35, 37, which extend in the longitudinal axis direction of the elastomer bushing and protrude in the radial direction from the outer surface of the half shells 5, 7 in order to create a support or contact for the lining bushings of the bearing device 9, which are also formed in the manner of a half shell. The assembly state is shown in 3 visible.

From a summary of the 2 and 3 Furthermore, the positive and/or non-positive connection between the half shells 5, 7 and the bearings block parts 23, 25, which according to the exemplary embodiment is designed as a dovetail connection 37. The dovetail connection 37 comprises half-shell-side radial projections 39, 41, which extend in the longitudinal axis direction A and are arranged at a circumferential end of the half-shells 5, 7, as well as bearing block-side receiving grooves 43, 45, into which the fastening projections 39, 41 can engage. Due to the matching shape and in particular the design as a dovetail connection 37, the projections are designed in relation to the grooves in such a way that they engage behind them in the radial direction in order to be received therein in a particularly fixed and secure position. In the assembled state, the fastening projections 39, 41 are clamped within the receiving grooves 43, 45. In 4 is a sectional view along the line IV-IV of 3 shown.

5a to 7b show schematically various embodiments of elastomer bushings 1 according to the invention, in particular their bearing devices 9, wherein the 5a , 6a and 7a Sectional views looking in the direction of the longitudinal axis A and views 5b, 6b and 7b are sectional views looking transversely thereto. The embodiment of the 5a , 5b , shows an elastic bearing 1, in which an inner plain bearing lining 31, 33 is provided in order to decouple the half shell 5, 7 from the gear bearing journal 19, 21. The spring stiffness of the elastomer half shells 5, 7 is indicated by means of the springs 51. In the embodiment in the Plain bearing linings are provided both on the inside and outside, so that the plain bearings 5, 7 are decoupled or slidably mounted both with respect to the gear bearing journals 19, 21 and with respect to the outside bearing block parts 23, 25. In the embodiment according to the 7a and 7b is analogous to the embodiment of the 5a and 5b only one pair of sliding linings 31, 33 is provided, this is in 7a , 7b but oriented towards the outside, i.e. towards the bearing block part 23, 25.

The features disclosed in the above description, the figures and the claims can be important both individually and in any combination for the realization of the invention in the various embodiments.

List of reference symbols

1

elastic bearing

3

Elastomer bushing

5.7

Half shell

9

Storage facility

11

transmission

13

Main shaft

15, 17

Gearbox support

19, 21

Bearing journal

23, 25

Bearing block part

27

inner space

29

surface

31, 33

Covering

35, 37

Investment advantage

38

Dovetail joint

39, 41

Mounting projection

43, 45

Receiving groove

51

Feather

A

Longitudinal axis direction

QUOTES INCLUDED IN THE DESCRIPTION

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

Cited patent literature

• DE 102020119832 A1 [0003]
• US 20130202232 A1 [0004]
• EP 2516883 A1 [0007, 0023]

Claims (11)

Elastomer bushing for an elastic bearing of a drive train component of a wind turbine, in particular a gearbox on a housing, such as a machine carrier, of a wind turbine, comprising two half-shells each made from an elastomer piece and a bearing device which at least partially decouples at least one half-shell from the drive train component and/or the housing and has a reduced static and/or sliding friction compared to the elastomer material. Elastomer bushing according to Claim 1 , wherein the bearing device has a coating covering an outer and/or inner circumference of the half-shell. Elastomer bushing according to Claim 2 , wherein the coating is designed as a bushing, in particular a half-bush, and/or is made of plastic, such as PTFE, polyamide, PET polyester or polyethylene terephthalate, or of metal, such as brass, bronze, sintered metal or a dry lubricant, such as graphite. Elastomer bushing according to one of the preceding claims, wherein the bearing device comprises a lubricant, such as a solid-state and/or grease lubricant, in particular is formed therefrom. Elastomer bushing according to one of the preceding claims, wherein the bearing device has a coating, in particular made of PTFE, in particular is formed therefrom. Elastomer bushing according to one of the preceding claims, wherein at least one half-shell has a greater radial stiffness in a first radial direction transverse to the longitudinal axis direction, in particular vertical direction, than in a second radial direction transverse to the longitudinal axis direction, in particular horizontal direction. Elastomer bushing according to one of the preceding claims, wherein at least one half-shell has at least one contact projection extending in the direction of the longitudinal axis of the half-shell, such as a contact web, for the bearing device, in particular the lining, wherein in particular the at least one half-shell has two contact projections which are arranged at a distance from one another in the circumferential direction such that the bearing device rests against both contact projections. Elastomer bushing according to one of the preceding claims, wherein two circumferential ends of the half-shells facing each other are designed to form a tongue and groove and/or dovetail connection with two bearing block parts on the wind turbine side, in particular on the machine support side, for receiving the elastomer bushing in a particularly clamping manner. Elastomer bushing according to Claim 8 , wherein the circumferential ends are formed as radial projections extending in the direction of the longitudinal axis of the half-shells, the cross-section of which is shaped in the radial direction to engage behind a groove formed in the bearing block parts. Elastic bearing, in particular decoupling bearing, for supporting a drive train component, in particular a gearbox, of a wind turbine, in particular on its housing, such as a machine carrier, comprising an elastomer bushing designed according to one of the preceding claims and two bearing block parts for receiving the elastomer bushing, in particular in a clamping manner. Elastic bearing according to Claim 10 , wherein the bearing block parts have mutually facing, in particular identically formed grooves and radial projections are formed on two mutually facing circumferential ends of the half-shells, wherein the grooves and the radial projections are coordinated with one another in terms of shape, wherein in particular the radial projections are shaped to engage behind the grooves in the radial direction, in particular are formed in the manner of a tongue and groove and/or dovetail connection.

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