Elastic lamella bearing for large loads

Abstract

The invention relates to bearing structural components that are subject to large loads and torques. The invention specifically relates to novel elastic bearings which connect large, heavy structural components that are subject to movement, such as transmissions or generators, to drive trains or rotor shafts of wind turbines, the impacting torsional forces being able to be transmitted merely as a result of shear strain of the elastic elements.

Description

[0001] Elastic slatted bearings for heavy loads

[0002] The invention relates to the mounting of components subject to heavy loads and torques. In particular, the invention relates to novel elastic bearings with a lamellar structure that connect large, heavy, and moving components, such as gearboxes or generators with drive trains or rotor shafts, for example, in wind turbines. Acting torsional forces can be transmitted through pure shear deformation of the elastic elements.

[0003] The bearings according to the invention presented below are intended primarily, but not exclusively, for structure-borne sound decoupling in wind turbines but also other systems and machines while allowing limited elastic mobility.

[0004] Elastic mounting of heavy machine parts, such as those regularly used in modern, high-performance wind turbines, are known in principle.

[0005] Torque supports with two opposing bushings are usually used, which are integrated into the gearbox support or are arranged on both sides in front of and behind the gearbox supports.

[0006] EP 1 197677 A1, for example, describes a gearbox mount for wind turbines. It comprises an arrangement of torsionally acting, and thus structure-borne sound-damping, elastomer elements that are largely unable to transmit the gearbox's torque. Therefore, additional compressively loaded wedge elements are provided, which transmit a significant portion of the torque, creating a progressive spring characteristic through the wedge elements.

[0007] EP 2 352 930 A1 describes an elastic bearing for wind turbines, which consists of a circularly arranged combination of layered springs stacked on top of each other in the axial direction with elastic conical elements. While the layered springs exhibit a low torsional progression, the conical bearings, with their progressive stiffness properties, play a significant role in torque transmission.

[0008] EP 3 012 479 A1 describes a bearing for wind turbines consisting of two disc-shaped, interlocking bearing components with a polygonal contour, which are connected by tangentially aligned layered spring elements. Although these springs are very soft in the thrust direction, they are arranged tangentially in such a way that the essential torque is generated via a pressure component formed by the star-shaped arrangement.

[0009] EP 3 892 876 A1 discloses a hydraulic cam clutch in which the carrier cams of the driven disk are connected to the carrier cams of the driven disk via elastic spring elements. They have an angle of attack relative to the plane of the two opposing disks and are arranged at an inclination relative to one another. Although this clutch is soft during axial displacement due to its hydraulic function, it is stiff and progressive in the torque and compression direction in order to be able to transmit the high torsional loads. WO 2022 / 171363 A1 presents a clutch for transmitting torques and high axial forces with high torsional and low cardanic stiffness. The clutch disks are equipped with circularly arranged, axially aligned elastic bushings. The torsional force is transmitted in the radial direction via the bushings, which are progressive in the radial direction.

[0010] In the known bearings and systems described above, the elastomer used is largely only subjected to compressive loads. This makes the elastomer components highly progressive, resulting in only moderate sound insulation under high torsional loads. This progression is most pronounced when structure-borne noise is particularly pronounced due to the high torques of the gearboxes. Another option is to firmly connect the gearbox of a wind turbine to the machine frame in a circular manner. However, this does not allow for structure-borne noise decoupling. To achieve this in such systems, the entire rotor shaft-gearbox unit of the wind turbine was decoupled in the past using additional devices and measures.

[0011] The German utility model 9317524.8 describes a torque coupling of a hydraulic pump which has a meandering elastomer track between two toothed discs and is arranged in such a way that it experiences shear deformation under load and thus contributes to the structure-borne sound insulation of the system.

[0012] The torques of modern wind turbines are already well over 1,000 kNm. With a diameter of approximately 3 m, for example, a wind turbine gearbox rotor bearing, more than 6,000 kN of circumferential force must be transmitted. This is not possible with conventional thrust elements, such as those described in the aforementioned utility model 9317524.8, on the available or required circumferential surface of such a large bearing.

[0013] The object of the invention is therefore to provide a bearing for high loads and torques, particularly for gearbox-rotor bearings in wind turbines, which enables power transmission with improved acoustic decoupling without progressive elements. Progression in this context refers to the behavior of rubber / elastomer under pressure or load. The force per spring travel increases with increasing deflection, so that the stiffness of the elastomer increases with increasing travel.

[0014] This problem was solved by the elastic lamella bearings according to the invention, as described in the claims and below, in which the elastic elements undergo shear deformation. The existing shear stiffness changes only insignificantly under the action of a load, resulting in an approximately linear characteristic curve.

[0015] The subject of the invention is therefore a bearing arrangement for connecting two rotationally symmetrical machine parts which are subject to high torques or forces, in particular between the gearbox and rotor bearing housing of wind turbines, comprising a circular bearing ring equipped with elastic elements and a concentric opening, which is firmly connected to both the first machine part and the second machine part and is arranged and functionally equipped in such a way that torsional forces can be transmitted by pure shear deformation of the elastic elements.

[0016] The bearing arrangement is distinguished from known corresponding bearings in that the bearing ring (18) according to the invention is constructed from a plurality of circular segments (1) which directly or indirectly abut one another or are partially interlocked with one another in an overlapping manner, and each of the individual circular segments (1) has a lamellar structure made up of at least one elastic layer element unit (10) (10').

[0017] Each of these circular segment-shaped elastic layer element units (10)(10') is in turn constructed according to the invention from:

[0018] (i) at least one, two, three, four or more, preferably two or four, elastic layers (2) adapted to the circular shape, which are radially aligned with respect to the circular bearing ring,

[0019] (ii) one or more intermediate sheets (3)(4) between the individual layers (2), which project radially inwards and radially outwards and thus protrude beyond the layers (2), and

[0020] (iii) fixed radially outer and radially inner spacer elements (6)(7) which are arranged above and below the elastic layers (2) in a fitting manner between the projecting intermediate plates (3)(4) and preferably form-fit the circular segment radially outwards and inwards.

[0021] The radially inner intermediate plates (3) are firmly connected to the first machine part via connecting elements (13)(19), and the radially outer intermediate plates (4) are firmly connected to the second machine part via connecting elements (12)(20). According to the invention, the lamellar structure of a circular segment (1) can be constructed from one, two, or more layered element units (10)(10') which, viewed in the axial direction, are arranged one above the other and firmly connected to one another, allowing the bearing to be adapted to the requirements of the system.

[0022] In one embodiment of the invention, a layered element unit (10) (10') is constructed from four or more elastic, parallel layers (2) and corresponding projecting radially inner and radially outer intermediate sheets (3) (4). However, a unit (10) can also have only one elastic layer (2) or, for example, four, eight, or twelve elastic layers (2).

[0023] The individual circular segment-shaped components of a circular segment (1) are connected and clamped together with connecting elements, in particular screw connections.

[0024] According to the invention, the circular segments have a circular segment angle (21) between 20° and 60° relative to the center of the bearing ring (18). The circular segments can have different or identical segment angles. The value of the segment angle determines the number of circular segments in the bearing ring. In a typical embodiment of the invention, the bearing ring consists of twelve circular segments with an identical segment angle of 30°.

[0025] In a further preferred embodiment of the invention, the elastic bearing arrangement is designed such that it can also absorb axial deformations, if necessary, which can occur during operation together with torsional deformations. This is achieved according to the invention in that a free space or distance is provided between the radially inner elastic layers (2) and the radially outer spacer elements (6)(7), whereby the radially outward-projecting and / or radially inward-projecting projections of the intermediate plates (3)(4), which connect the elastic layers to the spacer elements, are now axially movable and thus deformable. The intermediate plates or their projections thus function as diaphragm plates (110) in these areas. At least two intermediate plates (3) / 4) lying one on top of the other must be used.In this case, the respective outer intermediate plate is firmly connected to the respective elastomer layer (2), while the contacting intermediate plates are arranged so as to slide relative to one another, so that they can move relative to one another upon axial deformation. The number of intermediate plates (3)(4), or their projections acting as membrane plates (110) in this area, as well as the distance formed by the free space between the elastic layers (2) and the spacer elements (6)(7), thus determine the desired rigidity or deformability of the membrane plates (110) as part of the intermediate plates (3)(4) in this area. For the size of the bearings required for wind turbines, a distance between said elements of 10-100 mm, in particular 50-100 mm, is usually sufficient to enable sufficient axial deformability of the bearings or couplings according to the invention.

[0026] As already mentioned, the bearing arrangement according to the invention preferably consists of several circular segments (1), which preferably have a possibly identical segment angle (21) between 20° and 60°. A complete bearing ring according to the invention can thus preferably comprise approximately between 6 and 18, preferably 12, circular segments (1), which are connected or interlocked with one another as described. In principle, two circular segments (1) with an angle of 180° or just a single ring (360° segment) can be used.

[0027] It has been shown that it is advantageous if the membrane sheets (110) of the individual, for example 6 - 18, circle segments (1), which allow a certain axial deformation, are all or partially functionally connected to one another in a ring-like manner in order to avoid the occurrence of locally occurring moments during torsional loading.

[0028] In principle, the bearing arrangement according to the invention can comprise, instead of the membrane plates (110) described above, other types of elements or devices which allow axial deformability of the bearing.

[0029] The thickness and number of elastic layers (2) are decisive for the properties of the bearing according to the invention, including its torsional mobility, and thus the ability to reduce structure-borne noise of the system.

[0030] According to the invention, a single elastomer layer (2) of a bearing ring with a diameter of, for example, 2-3 m can have a thickness between 5 and 40 mm, preferably between 10 and 30 mm. Diameters for rotor-gearbox bearings of 2, 3, or more meters are common in modern wind turbines.

[0031] The bearings according to the invention can, through shear deformation of the corresponding components under normal operating conditions, enable a tangential torsion travel of 30-150%, preferably 30-60%, of the thickness of a single elastomer layer (2). In practice, the torsion travel for systems with the layer thicknesses specified above is approximately 2 to 15 mm, which roughly corresponds to a rotation angle of up to 1°.

[0032] Based on the specified layer thicknesses (2), number of layers and size of the components, the bearing arrangements according to the invention have a torsional stiffness of 20 6 Nm / ° up to 100 6 Nm / ° and can therefore absorb correspondingly high torques.

[0033] In a common embodiment of the invention, the individual circular segments (1) are arranged flush with one another along their end faces, forming a corresponding bearing ring. In a modified embodiment of the invention, the individual circular segments can also be arranged at least partially overlapping, with the overlap occurring primarily via the outer sheets and the spacer elements (6)(7). This overlap allows the forces and loads acting on the bearing ring to be distributed more evenly.

[0034] In another embodiment of the invention, individual circular segments (1) can be omitted, resulting in improved repair and maintenance options (e.g., access opening for maintenance personnel). By increasing the number of layer element units (10), the change in torsional stiffness caused by the omission can be compensated.

[0035] It may be necessary, particularly during extreme events on the system, to limit torsional mobility to prevent damage. For these cases, a further embodiment of the invention is provided, which includes stop devices for the torsionally movable parts of the circular segments. Two examples of such stop devices are shown in Figures 10-15 and are described in more detail below.

[0036] As already mentioned, the described bearing arrangement or coupling according to the invention can be used in particular for decoupling structure-borne sound from two interconnected, preferably rotationally symmetrical, machine parts subject to torque. Therefore, the invention also particularly relates to a wind turbine, comprising a tower, nacelle, rotor, and gearbox / generator, which has such a bearing arrangement or coupling according to the invention, which is preferably arranged to connect the rotor housing (15)(16) to the gearbox / generator housing (17) of the turbine.

[0037] Detailed description of the invention with reference to the figures: FIG. 1 shows a bearing arrangement (18) in the form of a ring of circular segments (1) according to the invention, without a machine frame and rotor shaft. Detail 1 shows a removable / assemblable individual, layered circular segment (1). The bearing ring is formed here by 12 narrow circular segments (1) that are joined together in a form-fitting manner to form a ring, forming a concentric opening for receiving and securing, for example, a rotor bearing housing.

[0038] FIG. 2 shows a single disassembled circular segment (1) in the clamped state, consisting of two layer element units (10) and (10'), each layer element having four elastomer layers (2) and spacers (6)(7), and the circular segment thus comprising a total of eight elastic layers (2) and four spacers (6). The intermediate sheets are divided into radially outward-facing sheets (4) and inward-facing sheets (3), and are referred to below as radially outer and radially inner intermediate sheets. Intermediate sheets (4) also close off the circular segment on both sides. In addition, on the axially outward-facing free side of the circular segment (1), a fixed outer ring segment (8) is attached, which serves to axially preload the elements and, like the radially outward-facing part of the intermediate sheets (4), has bores for connecting elements, such as screw connections.The radially outward-facing intermediate plates (4) are separated from the radially inward-facing intermediate plates (3) by the elastic layers (2) and thus alternate. The intermediate plates (4) protrude radially outwards beyond the layer elements (2), while inwards they are flush with the layer elements. Likewise, the intermediate plates (3) protrude inwards (directed towards the opening of the bearing ring) beyond the layer elements and outwards they are flush with the layer elements. The outward and inward projections of the intermediate plates (3)(4) are provided with corresponding holes for connecting elements (not shown), via which they are connected to the corresponding machine parts.Between the freely projecting intermediate plates, fixed spacer elements are provided that are dimensioned and shaped accordingly to the thickness of the elements. Spacer elements (6) are inserted into the radially outward-facing spaces and spacer elements (7) are inserted into the radially inward-facing spaces formed by the corresponding overhanging intermediate plates (3)(4). The spacer elements are also equipped with appropriately arranged bores for receiving connecting elements. This results in a compact, lamellar circular segment that, together with the other segments of the bearing ring, withstands high axial forces and loads and, at the same time, is elastically movable torsional with a rotation angle of up to approximately 2°, preferably 0.2 - 1°.

[0039] The number of layer elements (2) and thus also the number of intermediate sheets is variable according to the invention and depends on the technical conditions and requirements of the system. Advantageously, the components are assembled into layer element units (10)(10'), which in turn can be individually assembled into larger lamella structures. Bearing arrangements according to the invention with four to eight layer elements (2) or one or two layer element units (10)(10') with two to four layer elements (2) are particularly suitable for wind turbines, whereby the thickness of the elastic layers can vary between 5 and 40 mm, preferably between 10 and 30 mm.

[0040] FIG. 3 shows a circular segment (1) as described above (Fig. 2), with four elastomer layers (2) in a clamped state, with the spacer elements (6) (7) omitted for clarity. Four elastomer layers (2) are firmly connected to intermediate plates (4) (3).

[0041] One can see the staggered arrangement of three radially outer and two radially inner intermediate plates with holes (20)(19) for fastening as well as the four elastomer layers (2).

[0042] FIG. 4 shows a single disassembled circular segment (1) according to FIG. 2, but in an unstressed state. In this case, a prestressing path (9) of a few millimeters is provided between the elastic layers (2) and the respective sheets (3)(4), which is closed by clamping with screws or similar means.

[0043] FIG 5 (A)(B ) shows the circle segment from Fig. 4 in section. (A) shows the unbraced element with the prestressing dimensions (9) and (B) the braced element, each connected to machine parts (hatching).

[0044] FIG. 6 (a)-(d) shows the elastic bearing star (18) placed between the rotor bearing housing (15(16) and the gearbox housing (17) of a wind turbine and its fastening (a) in side view, (b) in perspective, (c) in section and (e) as a detail of (c).

[0045] FIG. 7 shows a gear rotor unit corresponding to FIG. 6 with the elastic bearing star according to the invention made up of partially overlapping circular segments (1) according to FIG. 3.

[0046] In the drawing, two circle segments are omitted to show the arrangement of the radially outer spacer elements (6), the intermediate plates (4), and the outer ring segments (8).

[0047] CORRECTED SHEET (RULE 91) ISA / EP and the offset of the elements (10) compared to (10') due to the overlap.

[0048] FIG 8 refers to Fig. 7 and shows the bearing star (18) with two omitted circular segments (1) without rotor bearing housing and without gear and without an outer ring segment (8).

[0049] Fig. 9 shows a specific embodiment of the invention. From the originally

[0050] In the bearing ring composed of 12 circular segments (1), every second circular segment was removed. The modular design of the bearing arrangement according to the invention makes it easy to accommodate special system requirements or repairs. Missing elements can be compensated for by increasing the number of layers of the remaining elements.

[0051] Figs. 10-15 show two further embodiments of the invention in different views. Here, the circular segments are provided with stop devices intended to limit torsional mobility. This is useful in extreme events to prevent damage to the bearing. A first embodiment of the invention comprises stop cams, while a second embodiment provides stop plates.

[0052] Fig. 10 shows a circular segment (1) without spacer elements (6) / 7) with four elastomer layers (2), three radially outward-facing intermediate plates (4), and two radially inward-facing intermediate plates (3), wherein the radially outer intermediate plates (4) are provided with cams (50) on their inner circular edge. The rear cams are not visible. The cams (50) are designed to protrude into recesses (52) on the outer edge of a radially inward-facing spacer element (7), as shown in Fig. 13 (section AA).

[0053] Alternatively or additionally, cams (51) can be mounted on the outer edge of a radially inner intermediate plate (3), which protrude into recesses (53) on the inner edge of a radially outer spacer element (6), as shown in Fig. 13 (section BB). The recesses are larger than the respective cams, which thus have a clearance (54)(55). In the event of particularly strong torsion of the bearing, the cams strike the edges of the recesses.

[0054] FIG 11 shows a circle segment according to Fig. 10 but with 8 layers, where the cams are not visible in the representation.

[0055] FIG. 12 shows the element of FIG. 11 in top and side views. FIG. 13 shows the two sections AA and BB of FIG. 12. Here, in AA, the cam recess function of the intermediate plate outer diameter (4) can be seen. In BB, the cam recess function of the intermediate plate inner diameter (3) is visible.

[0056] FIG. 14, 15 illustrates a stop device in the form of a stop plate (102).

[0057] Fig. 14 shows an arrangement of the circular segments (1) according to the invention between the gearbox and rotor bearing housing of a wind turbine. A stop element in the form of a plate (102) is located between the end faces of two circular segments.

[0058] FIG. 15 shows the section A marked in Fig. 14 in an enlarged view. On the plate

[0059] (102) the radially inner intermediate plates (3) which are movable during shear deformation can strike at a defined stop angle (103) by being extended in their length by a maximum movement path (101) of the predetermined torsional stop angle

[0060] (103) are shortened. The stop angle 103 is drawn larger for clarity. The arrows (101) show the movement of the radially inner intermediate plates (3) when the bearing star rotates in one direction. The stop angle (103) is drawn larger here than in reality to allow a view of the intermediate plates. The stop angle is slightly larger than the maximum specified angle of rotation.

[0061] FIG 16 (a) describes a segment of a multi-plate clutch according to the invention with outwardly directed diaphragm plates (110) in the form of intermediate plates (3) that can be bent within a specific range. This shows the segment of a multi-plate clutch with an additional diaphragm coupling (110) that is located radially outside the elastic elements (2). The diaphragm coupling (110) results from a free space or distance between elastic layers (2) and the outer or inner spacer elements (6)(7). The multi-plate clutch shown consists of the intermediate plates of the clutch that are extended radially outward. Upon axial displacement of the clutch, the intermediate plates, which are softly mounted in the rubber, bend in such a way that axial displacement is possible.

[0062] FIG. 16 (b) describes a segment of the same multi-plate clutch, but with inwardly directed projecting intermediate plates (3). In contrast to FIG. 16 (b), the intermediate plates here are extended radially inward, so that additional axial displacement is also possible through bending of the intermediate plates serving as a diaphragm. In principle, a design with one outwardly directed and one inwardly directed diaphragm clutch is also possible. (no image). FIG. 17 (a) shows a section through a gearbox machine frame bearing with a multi-plate clutch according to the invention, which is supplemented by an additional inwardly directed diaphragm clutch (110), as shown in FIG. 16.

[0063] FIG. 17 (b) shows two enlarged sections of the multi-plate clutch according to FIG. 17 (a) with the diaphragm directed inward (intermediate plates). The diaphragm is shown deformed in direction (113).

[0064] To enable larger deformations, it is advisable to use several thin sheets, as these exhibit significantly lower bending stresses for the same deformation, while the same torsional forces can be transmitted with the same total thickness of the sheets. Thus, the bending stress resulting from axial displacement is halved for two sheets with the same total thickness and the same radial extension, while the transmittable torsional forces remain the same.

[0065] In FIGS 16 and 17, the diaphragm coupling therefore consists of two sheets 3A and 3B. It is also possible to use more than two sheets.

[0066] FIG 18 shows a section of another design of a diaphragm coupling similar to the embodiment in FIG. 17, but with three sheets (3). In the illustrations shown, the sheets are shown flush next to one another. In the event of axial or cardanic displacement, friction occurs between the elements 3A and 3B (cardanic displacement occurs due to an inclination between the drive side, e.g. gearbox, and the output side, e.g. rotor bearing / machine support). The friction creates mechanical damping of the diaphragm, which prevents it from oscillating. The damping is advantageous in order to prevent the sheets from oscillating. The diaphragm sheets 3A, 3B, 3B, etc. can also be mounted friction-free with a gap in order to avoid friction between the sheets and thus the generation of noise and fretting corrosion.

Claims

1. Bearing arrangement or coupling for connecting two rotationally symmetrical machine parts which are subject to high torques or forces, in particular between the gearbox and rotor bearing housing of wind turbines, comprising a circular bearing ring (18) equipped with elastic elements and a concentric opening, which is firmly connected to both the first machine part and the second machine part and is arranged and functionally equipped such that torsional forces can be transmitted by pure shear deformation of the elastic elements, characterized in that the circular bearing ring (18) is constructed from a plurality of circular segments (1) which directly or indirectly abut one another or are partially interlocked with one another, and each of the individual circular segments (1) has a lamellar structure made of at least one elastic layer element unit (10) (10'), which is composed of: (i) at least one, two, three, four or more elastic layers (2) which are radially aligned with respect to the circular bearing ring, (11) one or more intermediate plates (3)(4) projecting radially outwards and inwards with respect to the elastic layers (2) between the individual layers (2), and (iii) fixed radially outer and radially inner spacer elements (6)(7) which are arranged above and below the elastic layers (2) and are separated from one another by the projections of the intermediate plates (3)(4), wherein the radially inner intermediate plates (3) are fixedly connected to the first machine part via connecting elements (13)(19) and the radially outer intermediate plates (4) are fixedly connected to the second machine part via connecting elements (12)(20).

2. Bearing arrangement according to claim 1, characterized in that the lamellar structure of a circular segment (1) consists of two or more layer element units (10)(10') which, viewed in the axial direction, are arranged one above the other and firmly connected to each other, thereby enlarging the lamellar structure of the circular segment.

3. Bearing arrangement according to claim 2, characterized in that a layer element unit (10) (10') is constructed from four or more elastic layers (2) and corresponding projecting radially inner and radially outer intermediate plates (3)(4).

4. Bearing arrangement according to one of claims 1 - 3, characterized in that the circular segments (1) are equipped on both sides with end plates (5) which are fastened to the two outer layer element units (10)(10').

5. Bearing arrangement according to claim 4, characterized in that outer ring segments (8) are provided on the end plates (5), which have bores for the connecting elements (12).

6. Bearing arrangement according to one of claims 1 - 5, characterized in that the circular segments have a preferably identical segment angle (21) between 20° and 60°, preferably 30°, with respect to the center of the bearing ring (18).

7. Bearing arrangement according to one of claims 1 - 6, characterized in that it is designed by additional elements (110) so that it can also absorb axial deformations which occur together with torsional deformations.

8. Bearing arrangement according to claim 7, characterized in that the radially outwardly projecting and / or the radially inwardly projecting projections of the intermediate plates (3)(4) are arranged in a free space or distance between the elastic layers (2) and the respective spacer elements (6)(7) located on the outside thereof, which allows the intermediate plates (3)(4) to take over the function of membrane plates (110) in this area and thus be axially deformable.

9. Bearing arrangement according to claim 8, characterized in that at least two adjacent axially bendable and mutually slidable membrane plates (110) are arranged between two adjacent elastic layers (2) and connect them to one another.

10. Bearing arrangement according to claim 8 or 9, characterized in that the distance formed by the free space between the elastic layers (2) and the spacer elements (6) (7) is 10 - 100 mm, depending on the number of membrane sheets (110) and the desired axial deformability.

11. Bearing arrangement according to one of claims 8 - 10, characterized in that the membrane plates (110) of a circular segment (1) are functionally connected to the membrane plates (110) of an adjacent circular segment (1).

12. Bearing arrangement according to one of claims 1 - 11, characterized in that the thickness of an individual elastomer layer (2) is 5 - 40 mm, preferably 10 - 30 mm for a bearing ring diameter between 2 m and 3 m.

13. Bearing arrangement according to claim 12, characterized in that the elastomer layers (2) and intermediate plates (3)(4) of the bearing ring (18) have a tangential torsion path due to shear deformation under normal operating conditions, which is 30 - 150%, preferably 30 - 60%, of the thickness of an individual elastomer layer (2).

14. Bearing arrangement according to one of claims 1 - 13, characterized in that the spacer elements (6)(7) are shaped and arranged such that they close off a respective circular segment (1) to the outside and inside.

15. Bearing arrangement according to one of claims 1 - 14, characterized in that between the spacer elements (6)(7) and adjacent intermediate plates (3)(4) a preload path in the form of a gap (9) is provided, which is closed when the components are clamped.

16. Bearing arrangement according to one of claims 1 - 15, characterized in that all or some of the adjacent circular segments (1) are connected to one another in an overlapping manner, the overlap being effected by relative displacement of radially outer and radially inner spacer elements (6) (7) and / or the end plates (5) and / or the end ring segments (8) of the respective circular segments.

17. Bearing arrangement according to one of claims 1 - 16, characterized in that individual or several circular segments (1) are omitted from the bearing ring (18).

18. Bearing arrangement according to one of claims 1 - 17, characterized in that the circular segments (1) have stop elements (50) (51) (52) (53) (54) (55) (102) (101) (103) which limit the torsional movement of the elastomer layers (2) and intermediate plates (3) (4) of a circular segment (1) in the event of extreme operational events.

19. Bearing arrangement according to claim 18, characterized in that cams (50)(51) with correspondingly shaped recesses (52)(53) which provide a predetermined movement space (54)(55) for the cams are provided as stop elements, wherein (i) the cams (50) are mounted on a radially outer intermediate plate (4) and project into recesses (52) of radially inner spacer elements (7), and (ii) the cams (51) are attached to a radially inner intermediate plate (3) and project into recesses (53) of radially outer spacer elements (6), wherein the predetermined free space (54)(55) determines the maximum stop path of the respective cams and thus limits the torsional path and the shear deformation of the components involved in a circular segment (1).

20. Bearing arrangement according to claim 18, characterized in that a plate (102) is provided as the stop element, which is fastened flush to the end face of a circular segment (1), and the radially inner intermediate plates (3) of the adjacent circular segment (1) opposite the plate (102) are shortened in length by a maximum movement path (101) of a predetermined torsional stop angle (103) and are thus able to strike the plate (102) in the event of an extreme event and thus to limit the torsional path and the shear deformation of the components involved in a circular segment (1).

21. Bearing arrangement according to claim 20, characterized in that the predetermined stop angle (103) is greater than the torsional rotation angle of a circle segment (1) under normal operating conditions.

22. Use of a bearing arrangement or a coupling according to one of claims 1 - 21 for decoupling structure-borne sound from two interconnected rotationally symmetrical machine parts subjected to a torque.

23. Wind turbine comprising a tower, a nacelle, a rotor, and a gearbox or generator, characterized in that it has a bearing arrangement according to one of claims 1 - 21.

24. Wind turbine according to claim 23, characterized in that the bearing arrangement connects the rotor bearing housing (15)(16) to the gearbox or generator housing (17) of the turbine.

Images