Resilient sheet support structure for large loads
By designing a plate-type support structure composed of multiple arc segments, and utilizing shear deformation to transmit torsional force, the problems of acoustic decoupling and force transmission under high load and torque in wind power generation equipment were solved, achieving improved high rigidity and sound insulation.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- FM ENERGIE GMBH & CO KG
- Filing Date
- 2024-11-04
- Publication Date
- 2026-05-29
AI Technical Summary
Existing support structures struggle to achieve effective acoustic decoupling and torsional force transmission when transmitting large loads and torques, especially in wind power equipment. Furthermore, the rigidity of conventional elastomers in the torsional direction increases with the load, resulting in limited sound insulation performance.
The structure employs a plate-type support structure composed of multiple arc segments. These arc segments are connected to the intermediate plate via elastic layer element units, allowing the transmission of torsional force under shear deformation. The intermediate plate is axially deformable to adapt to load changes, forming an approximately linear characteristic curve.
It achieves effective force transmission and acoustic decoupling under high torque conditions, reduces the influence of progressive stiffness, and improves the torsional stiffness and sound insulation of the equipment.
Smart Images
Figure CN122122403A_ABST
Abstract
Description
Technical Field
[0001] This invention relates to support structures for components subjected to large loads and torques. In particular, it relates to novel, resilient bearings with a plate-like structure that connect large, heavy, and moving parts, such as those in wind power generation equipment, like transmission mechanisms or generators, to power drive systems or rotor shafts, wherein the torsional forces acting therein can be transmitted through the pure shear deformation of the resilient elements. Background Technology
[0002] The bearings according to the invention described below are primarily, but not exclusively, designed for bulk acoustic decoupling in wind power equipment, but also in other equipment and machinery, while achieving limited elastic mobility.
[0003] The flexible support structure for heavy machine components, such as those frequently used in modern, efficient wind power, is known in principle. Therefore, torque extenders with two opposing bushings are typically used, either integrated into the drivetrain strut or arranged on both sides in front of and behind the drivetrain strut.
[0004] EP 1 197 677 A1, for example, describes a support structure for a transmission mechanism in a wind power generation device, comprising an arrangement of torsional elastomeric elements that thereby suppress body noise, the elastomeric elements being largely incapable of transmitting the torque of the transmission mechanism. Therefore, an additional wedge-shaped element subjected to pressure load is present, which transmits the majority share of the torque, thereby generating a progressive spring characteristic curve through the wedge-shaped element.
[0005] EP 2 352 930 A1 describes a resilient support structure for wind power generation equipment, which consists of a combination of stacked leaf springs supported vertically along the axial direction and a circularly arranged resilient tapered bearing. The stacked leaf springs exhibit a gradual decrease in torsional rigidity, while the tapered bearing, with its progressive stiffness characteristics, primarily participates in torque transmission.
[0006] EP 3 012 479 A1 describes a bearing for a wind power generation device, which consists of two disc-shaped bearing members joined together, each with a multi-faceted profile, connected to each other by tangentially oriented stacked leaf spring elements. These springs, while soft in the thrust direction, are arranged tangentially to generate the primary torque through a pressure assembly formed by a star-shaped arrangement.
[0007] EP 3 892 876 A1 discloses a hydraulic cam coupling in which the base cam of the output disc is connected to the base cam of the output disc by a resilient spring element and is arranged at an angle of attack relative to the planes of the two opposing discs and tilted relative to each other. While this coupling is soft in axial movement due to the function of the hydraulic system, it is rigid and progressive in the direction of torque pressure in order to transmit high torsional loads.
[0008] WO 2022 / 171363 A1 describes a coupling for transmitting torque and high axial force, which has high torsional stiffness and low universal joint stiffness, wherein the coupling disc is equipped with a circularly arranged, axially oriented, resilient bushing. Here, the torsional force in the radial direction is transmitted through the bushing, which is progressively distributed in the radial direction.
[0009] For the known support structures and systems described above, the elastomers used are largely subjected only to compressive loads. Consequently, the elastomer components are strongly progressive, resulting in only moderate sound insulation even under high torsional loads. This progressiveness is most pronounced when bulk sound is particularly noticeable due to the large torque of the transmission mechanism. Another feasible solution is to circularly and fixedly connect the transmission mechanism of the wind turbine to the frame. However, bulk sound decoupling is not possible here. In the past, to achieve bulk sound decoupling in such systems despite this limitation, additional devices and measures were used to decouple the entire rotor shaft transmission unit of the wind turbine.
[0010] German utility model 9317524.8 describes a torque decoupling of a hydraulic pump, which has a meandering elastomeric channel between two meshing discs and is arranged such that it undergoes shear deformation under load and thereby contributes to the bulk acoustic isolation of the system.
[0011] The torque of modern wind power generation equipment has significantly exceeded 10,000 kNm. For a wind power generation equipment, such as a rotor bearing in the transmission mechanism with a diameter of approximately 3 m, this necessitates the transmission of a tangential force greater than 6,000 kN. This is impossible to achieve with conventional propulsion elements, such as those described in the aforementioned utility model 9317524.8, on the separate or necessary circumferential surfaces of such large bearings. Summary of the Invention
[0012] Therefore, the objective of this invention is to provide a support structure for rotor support structures of transmission mechanisms in wind power generation equipment under large loads and torques, which allows for better acoustic decoupling of force transmission without progressive elements. In this respect, "progressive" refers to the characteristics of the rubber / elastomer under pressure or load. Here, for each spring stroke, the force increases with the increasing inward spring displacement, causing the stiffness of the elastomer to increase with the increase of the stroke.
[0013] The task is accomplished by the resilient sheet support structure according to the invention, as described in the claims and below, in which the resilient elements undergo shear deformation. Here, the shear stiffness present changes only negligibly under load, resulting in an approximately linear characteristic curve.
[0014] Therefore, the subject of this invention is a bearing device for connecting two rotationally symmetrical machine parts, particularly a transmission mechanism housing and a rotor bearing housing, in a wind power generation device, which are subjected to high torque or force. The bearing device comprises a circular bearing ring equipped with a resilient element and concentric openings, which is fixedly connected not only to a first machine part but also to a second machine part and is arranged and functionally equipped to transmit torsional force through the pure shear deformation of the resilient element.
[0015] Compared to known corresponding bearings, the bearing device is distinguished by the fact that the bearing ring (18) according to the invention is composed of a plurality of arcuate segments (1) that directly or indirectly abut or partially overlap and mesh with each other, and each of the arcuate segments (1) has a sheet-like structure composed of at least one elastic layer element unit (10) (10'). Each of these arcuate elastic layer element units (10) (10') according to the invention is further composed of the following components: (i) at least one, two, three, four or more, preferably two or four, resilient layers (2) that match the circular shape, said resilient layers being radially oriented relative to the circular bearing ring; (ii) An intermediate plate or two intermediate plates (3) (4) located between the various layers (2), the intermediate plates protruding radially inward and radially outward and thus extending beyond the layers (2); and (ii) Fixed radially outer and radially inner spacer elements (6) and (7), which are arranged above and below the elastic layer (2) between the protruding intermediate plates (3) and (4) and preferably radially outward and inwardly locking the arc segment.
[0016] Here, the radially inner intermediate plate (3) is fixedly connected to the first machine component via connecting elements (13) (19), and the radially outer intermediate plate (4) is fixedly connected to the second machine component via connecting elements (12) (20).
[0017] According to the present invention, the sheet-like structure of the arc segment (1) can be composed of one, two or more layer element units (10) (10'), which are arranged vertically along the axial direction and fixedly connected to each other, thereby enabling the bearing to be matched with the requirements of the equipment.
[0018] In one embodiment of the invention, the layer element unit (10) (10') is composed of four or more resilient, parallel layers (2) and corresponding protruding radially inward and radially outward intermediate plates (3) (4). However, the unit (10) may also have only one resilient layer (2) or, for example, four, eight or twelve resilient layers (2).
[0019] The various arc-shaped components of the arc segment (1) are connected and clamped to each other by connecting elements, especially threaded connections.
[0020] According to the invention, the arc segments have a circular sector angle (21) between 20° and 60° relative to the center of the bearing ring (18). The arc segments can have different or the same sector angle. The value of the sector angle determines the number of arc segments in the bearing ring. In a common embodiment of the invention, the bearing ring consists of twelve arc segments, each having the same sector angle of 30°.
[0021] In another, and preferred, embodiment of the invention, the resilient bearing device is configured such that it can also withstand axial deformation that may occur during operation along with torsional deformation. This is achieved according to the invention by providing a free space or gap between the radially inner resilient layer (2) and the radially outer spacer elements (6) (7), thereby allowing the radially outward and / or radially inward protruding portions of the intermediate plates (3) (4) that connect the resilient layers and the spacer elements to now move axially and thus deform. The intermediate plates or their protruding portions thus function as diaphragm plates (110) in these areas. Here, at least two intermediate plates (3) (4) placed vertically should be used. Here, the corresponding outer intermediate plates are fixedly connected to the corresponding elastomeric layers (2), while the intermediate plates in contact with each other are arranged to slide relative to each other, so that they can move relative to each other during axial deformation. The number of intermediate plates (3) and (4), or the number of their protrusions that function as diaphragm plates (110) in this region, and the spacing between the elastic layer (2) and the spacer elements (6) and (7) formed by free space, thereby determine the desired rigidity or deformability of the diaphragm plate (110) as a component of the intermediate plates (3) and (4) in this region. For the dimensions of the bearings necessary for wind power generation equipment, the 10-100 mm, especially 50-100 mm, spacing between the mentioned elements is generally sufficient to achieve adequate axial deformability of the bearings or couplings according to the invention.
[0022] As already mentioned, the bearing device according to the invention preferably consists of a plurality of arc segments (1), which preferably have the same sector angle (21) between 20° and 60°, if necessary. A complete bearing ring according to the invention can thus preferably comprise, for example, between 6 and 18, preferably 12 arc segments (1), which are connected or meshed with each other as described. In principle, two arc segments (1) each having an angle of 180° can be used, or a single unique ring (360° segment) can also be used.
[0023] It has been shown that it is advantageous that the individual diaphragm plates (110) capable of achieving a certain axial deformation, such as 6-18 arc segments (1), are functionally connected to each other in a ring shape, so as to avoid localized torques during the presence of torsional loads.
[0024] In principle, the bearing device according to the invention can replace the diaphragm plate (110) described above with other types of elements or devices that allow for axial deformability of the bearing.
[0025] The thickness and quantity of the elastic layer (2) are crucial to the characteristics of the bearing according to the invention, including its torsional mobility and thereby its ability to reduce the noise of the device.
[0026] A single elastomeric layer (2) of a bearing ring having a diameter of, for example, 2-3 m, can, according to the invention, have a thickness between 5 and 40 mm, preferably between 10 and 30 mm. Diameters of 2 m, 3 m, or more for rotor drive bearings are common in modern wind power equipment.
[0027] The bearing according to the invention can achieve a tangential torsional stroke of approximately 30-150%, preferably 30-60%, of the thickness of a single elastomeric layer (2) under normal operating conditions through shear deformation of the corresponding components. In practice, for devices with the layer thickness described above, the torsional stroke is approximately 2 to 15 mm, which roughly corresponds to a rotation angle of up to 1°.
[0028] Regarding the described layer thickness (2), number of layers, and order of magnitude of components, the bearing device according to the present invention has 20 6 Nm / ° to 100 6 It has a torsional stiffness of Nm / ° and is therefore able to withstand high torque accordingly.
[0029] In a common embodiment of the invention, the arc segments (1) are arranged flush with each other at their ends to form corresponding bearing rings. In a modified embodiment of the invention, the arc segments can also be arranged at least partially overlapping, wherein the overlap is first achieved by the outer plate and the spacer elements (6) (7). By overlapping, the forces and loads acting on the bearing rings can be distributed more evenly.
[0030] In another embodiment of the invention, the individual arc segments (1) can be omitted, thereby creating improved feasible solutions during maintenance and repair (e.g., for access points for maintenance personnel). By increasing the number of layer element units (10), the torsional rigidity caused by the omission of the arc segments can be compensated for.
[0031] It may become necessary, especially in the event of extreme events occurring on the equipment, to limit torsional mobility in order to prevent damage. In these cases, another embodiment of the invention provides a stop device for the torsional movement of the component in the arc segment. Two examples of such a stop device are provided in... Figure 10-15 It is shown in the figure and will be described in detail below.
[0032] As already mentioned, the described bearing device or coupling according to the invention is particularly suitable for bulk acoustic decoupling of two interconnected, preferably rotationally symmetrical and torque-susceptible machine components. Therefore, a wind power generation device, comprising a tower, nacelle, rotor, and drive / generator, is also the subject of this invention, having such a bearing device or coupling according to the invention, preferably arranged such that it connects the rotor housing (15) (16) to the drive / generator housing (17) of the device. Detailed Implementation
[0033] Figure 1 A bearing assembly (18) in the form of a ring, comprising an arcuate segment (1) according to the invention, is shown without a frame and rotor shaft. Section 1 shows a detachable / installable, single, layered arcuate segment (1). The bearing ring here is composed of 12 narrow arcuate segments (1) that are joined together in a form-locking manner to form a ring while creating concentric openings for receiving and securing, for example, a rotor bearing housing.
[0034] Figure 2The diagram shows a single detached arc segment (1) in a clamped state, which consists of two layer element units (10) and (10'), each of which has four elastomeric layers (2) and spacer retainers (6) (7), and the arc segment thus comprises a total of eight elastomeric layers (2) and four spacer retainers (6). The intermediate plate is divided into a radially outward-pointing plate (4) and a radially inward-pointing plate (3), and is referred to below as the radially outer and radially inner intermediate plates. The intermediate plate (4) also encloses the arc segment on both sides. Furthermore, a fixed outer annular segment (8) is disposed on the axially outward-pointing free side of the arc segment (1), which is used to pre-clamp the element in the axial direction and, like the radially outward-pointing portion of the intermediate plate (4), has drilled holes for connecting the element, especially for threaded connections. The radially outward-pointing intermediate plate (4) is separated from the radially inward-pointing intermediate plate (3) by elastomeric layers (2) and thus alternates. The intermediate plate (4) protrudes radially outward beyond the layer element (2), and terminates inward flush with the layer element. Similarly, the intermediate plate (3) protrudes inward (towards the opening of the bearing ring) beyond the layer element and terminates outward flush with the layer element. The outward and inward protrusions of the intermediate plates (3) and (4) are equipped with corresponding drill holes (not shown) for connecting elements, through which they are connected to corresponding machine parts. Between the freely protruding intermediate plates, fixed spacer elements of correspondingly determined size and formed are provided according to the thickness of the element, wherein spacer elements (6) are fitted into radially outward gaps and spacer elements (7) are fitted into radially inward gaps, which are formed by the corresponding protruding intermediate plates (3) and (4). The spacer elements are also equipped with correspondingly arranged drill holes for receiving connecting elements. Thus, there exists a compact, sheet-like arc segment that, together with the other segments of the bearing ring, withstands high axial forces and loads and is simultaneously capable of torsional elastic movement with a rotation angle, for example, up to 2°, preferably 0.2-1°. The number of layer elements (2) and thus the number of intermediate plates are also variable according to the invention and depend on the technical conditions and requirements of the equipment. Advantageously, components are combined into layer element units (10) (10'), which themselves can be individually combined into larger sheet structures. For wind power generation equipment, bearing devices 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, wherein the thickness of the elastic layer can vary between 5 and 40 mm, preferably between 10 and 30 mm.
[0035] Figure 3 As shown above ( Figure 2The arc segment (1) having four elastomer layers (2) is shown in the clamped state, wherein the spacer elements (6) and (7) are omitted for clarity. The four elastomer layers (2) are fixedly connected to the intermediate plate (4) and (3).
[0036] It can be seen that there is a staggered arrangement of three radially outer and two radially inner intermediate plates and four elastomer layers, wherein the intermediate plates have drill holes (20) (19) for fixing.
[0037] Figure 4 Showing a single disassembled, according to Figure 2 The arc segment (1), but in the case of not being clamped. In this case, a pre-clamping stroke (9) of a few millimeters is provided between the elastic layer (2) and the corresponding plates (3) (4), which is closed by clamping by means of bolts or similar elements.
[0038] Figure 5 (A) and (B) are shown in cross-section. Figure 4 The arc segment in the middle. Here (A) shows the unclamped element along with the pre-clamping dimension (9), and (B) shows the clamped element, which is connected to the machine part accordingly (shaded line).
[0039] Figure 6 (a)-(d) show the flexible bearing star (18) and its fixation placed between the rotor bearing housing (15) (16) and the transmission housing (17) of the wind power generation equipment in (a) side view, (b) perspective view, (c) section view and (e) as a cut-off portion of (c).
[0040] Figure 7 It shows according to Figure 6 The transmission mechanism rotor unit has a resilient bearing star element (Lagerstern) according to the invention, the bearing star element being constructed according to... Figure 3 It is composed of overlapping arc segments (1).
[0041] Two arc segments are omitted in the attached figures to illustrate the arrangement of the radially outer spacer element (6), the intermediate plate (4), and the outer annular segment (8), as well as the offset of element (10) relative to (10') caused by the overlap.
[0042] Figure 8 and Figure 7 The bearing star (18) is shown with regard to and without the rotor bearing housing and transmission mechanism and the outer annular segment (8), which has two omitted arc segments (1).
[0043] Figure 9A particular embodiment of the invention is shown. Each second arc segment is taken from the bearing ring initially composed of 12 arc segments (1). The modular construction of the bearing device according to the invention allows for easy consideration of specific equipment requirements or maintenance needs. Missing components can be compensated for by increasing the number of layers of the remaining components.
[0044] Figure 10-15 Two further embodiments of the invention are shown in different views. The arc segment here is provided with a stop device that should limit torsional movement. This is significant in extreme cases to prevent damage to the bearing. The first embodiment according to the invention includes a stop protrusion, while the second embodiment provides a stop plate.
[0045] Figure 10 An arc segment (1) is shown without the spacer elements (6 / 7), which has four elastomer layers (2), three radially outward-pointing intermediate plates (4), and two radially inward-pointing intermediate plates (3), wherein the radially outward-pointing intermediate plates (4) have protrusions (50) on their inner circular edges. The rear protrusions are not visible. The protrusions (50) are here provided for extending into the gaps (52) on the outer edges of the radially inward-pointing spacer elements (7), as in Figure 13 As shown in the middle (section AA).
[0046] As an alternative or supplementary solution, a protrusion (51) can also be placed on the outer edge of the radially inner intermediate plate (3), the protrusion extending into the recess (53) on the inner edge of the radially outer spacer element (6), such as in Figure 13 As shown in section BB. The recess is larger than the corresponding protrusion, which thus has free space for movement (54) (55). When the bearing is subjected to particularly violent torsion, the protrusion thereby strikes the edge of the recess.
[0047] Figure 11 It shows according to Figure 10 It has an arc segment, but it has 8 layers, and the protrusions on the arc segment are not visible as shown in the illustration.
[0048] Figure 12 Shown in top and side views Figure 11 Components.
[0049] Figure 13 It shows Figure 12 The two sections AA and BB. Here, in AA, the function of the protrusion clearance of the outer diameter (4) of the middle plate can be seen. In BB, the function of the protrusion clearance of the inner diameter (3) of the middle plate can be seen.
[0050] Figure 14 , 15 A stop device in the form of a stop plate (102) is shown.
[0051] Figure 14 The arrangement of the arc segment (1) according to the invention between the transmission mechanism and the rotor bearing housing of the wind power generation device is shown. There are stop elements in the form of plates (102) between the end sides of the two arc segments.
[0052] Figure 15 The enlarged diagram shows the... Figure 14 The section A is marked in the figure. The radially inner intermediate plate (3), which is movable during shear deformation, can strike the plate (102) at a defined stop angle (103) by means of the intermediate plate being shortened in length by the maximum stroke (101) of the predetermined torsional stop angle (103). The stop angle (103) is drawn larger for better illustration. The arrow (101) shows the movement of the radially inner intermediate plate (3) as the bearing star rotates in one direction. The stop angle (103) is drawn here larger than it actually is so that the intermediate plate can be seen. The stop angle here is slightly larger than the maximum predetermined rotation angle.
[0053] Figure 16 (a) A segment of the sheet-type connector according to the invention is depicted, the sheet-type connector having a diaphragm plate (110) that points outward and is in the form of a flexible intermediate plate (3) in a specific region. A segment of the sheet-type connector with an additional diaphragm plate (110) is shown here, the diaphragm plate being located radially outside the elastic element (2). The diaphragm plate (110) is generated here from the free space or gap between the elastic layer (2) and the spacer elements (6) (7) located on the outside or inside. The sheet-type connector shown here consists of an intermediate plate extending radially outward from the connector. When the connector moves axially, the intermediate plate, which is softly supported in rubber, bends so that axial movement is possible.
[0054] Figure 16 (b) depicts a segment of the same plate joint, but the plate joint has an inwardly projecting intermediate plate (3). With Figure 16 (b) In contrast, here the intermediate plate extends radially inward, thus enabling additional axial movement through the bending of the intermediate plate, which serves as the diaphragm. In principle, an embodiment with an outwardly pointing diaphragm connector and an inwardly pointing diaphragm connector is also possible (no figure).
[0055] Figure 17(a) shows a cross-section of a transmission mechanism frame support structure having a plate-type coupling according to the invention, the plate-type coupling being connected as shown in... Figure 16 The additional inwardly pointing diaphragm connector (110) shown in the diagram is used to supplement this.
[0056] Figure 17(b) shows two enlarged cutaway portions of the sheet joint according to Figure 17(a), the sheet joint having an inwardly pointing diaphragm (intermediate plate). The diaphragm is drawn in a deformed state along direction (113).
[0057] To achieve greater deformation, it makes sense to use multiple thin plates, as these plates exhibit significantly lower bending stress under the same deformation, while being able to transmit the same torsional force with the same total plate thickness. Therefore, the bending stress generated from axial movement is halved when using two plates with the same total thickness and the same radial elongation, while the torsional force that can be transmitted remains the same.
[0058] exist Figure 16 In 17, the diaphragm connector is therefore composed of two plates 3A and 3B respectively. It is also possible to use more than two plates.
[0059] Figure 18 A cutaway portion of another embodiment of the diaphragm connector is shown similarly to the embodiment in Figure 17, but it has three plates (3). In the illustrated figure, the plates are shown flush side by side. Friction is generated between elements 3A and 3B during axial movement or also during universal joint movement (universal joint movement is generated by the inclined position between the drive side, such as the transmission mechanism, and the output side, such as the rotor bearing / frame). The friction generates mechanical damping of the diaphragm, which prevents oscillation. Damping helps prevent oscillation of the plates. Diaphragm plates 3A, 3B, 3C, etc., can also be installed frictionlessly at intervals to avoid friction between the plates and thus avoid the generation of noise and mating corrosion.
Claims
1. A bearing assembly or coupling for connecting two rotationally symmetrical machine parts, particularly located between a transmission mechanism housing and a rotor bearing housing in a wind power generation device, the machine parts being subjected to high torque or force, the bearing assembly or coupling comprising a circular bearing ring (18) equipped with a resilient element and concentric openings, the bearing ring being fixedly connected not only to a first machine part but also to a second machine part and arranged and functionally equipped to transmit torsional forces through the pure shear deformation of the resilient element. Its features are, The circular bearing ring (18) is composed of multiple arc segments (1), which are directly or indirectly mated or partially overlapped with each other, and each arc segment (1) has a sheet-like structure composed of at least one elastic layer element unit (10) (10'), which is composed of the following components: (i) at least one, two, three, four or more resilient layers (2), said resilient layers being radially oriented relative to the circular bearing ring; (ii) One or more intermediate plates (3) and (4) located between the various layers (2), protruding radially inward and radially outward relative to the elastic layer (2), and (iii) Fixed radially outer and radially inner spacers (6) and (7), said spacers being arranged above and below the elastic layer (2) and spaced apart from each other by protrusions of intermediate plates (3) and (4). The radially inner intermediate plate (3) is fixedly connected to the first machine component via connecting elements (13) and (19), and the radially outer intermediate plate (4) is fixedly connected to the second machine component via connecting elements (12) and (20).
2. The bearing device according to claim 1, characterized in that, The sheet-like structure of the arc segment (1) is composed of two or more layer element units (10) (10'), which are arranged vertically along the axial direction and fixedly connected to each other, thereby expanding the sheet-like structure of the arc segment.
3. The bearing device according to claim 2, characterized in that, The layer element unit (10) (10') consists of four or more elastic layers (2) and corresponding protruding radially inward and radially outward intermediate plates (3) (4).
4. The bearing device according to any one of claims 1-3, characterized in that, The arc segment (1) is equipped with end plates (5) on both sides, which are fixed to two external layer element units (10) (10').
5. The bearing device according to claim 4, characterized in that, An outer annular segment (8) is provided on the end plate (5), which has a drilled hole for connecting the element (12).
6. The bearing device according to any one of claims 1-5, characterized in that, The arc segment has a sector angle (21) that is preferably the same and located between 20° and 60°, preferably 30°, relative to the center of the bearing ring (18).
7. The bearing device according to any one of claims 1-6, characterized in that, The bearing assembly is constructed by an additional element (110) that enables it to also withstand axial deformation that occurs along with torsional deformation.
8. The bearing device according to claim 7, characterized in that, The radially outward and / or radially inward protruding portions of the intermediate plates (3) and (4) are arranged in a free space or gap between the elastic layer (2) and the correspondingly external spacer elements (6) and (7), which allow the intermediate plates (3) and (4) to function as diaphragm plates (110) in this region and thus be able to deform axially.
9. The bearing device according to claim 8, characterized in that, At least two axially flexible and slidable diaphragm plates (110) are arranged between two adjacent elastic layers (2) and connected to each other.
10. The bearing device according to claim 8 or 9, characterized in that, The gap formed by the elastic layer (2) and the spacer elements (6) (7) through free space is 10-100 mm depending on the number of diaphragm plates (110) and the desired axial deformability.
11. The bearing device according to any one of claims 8-10, characterized in that, The diaphragm plate (110) of the arc segment (1) is functionally connected to the diaphragm plate (110) of the adjacent arc segment (1).
12. The bearing device according to any one of claims 1-11, characterized in that, The thickness of a single elastomer layer (2) is 5-40 mm, preferably 10-30 mm, for bearing ring diameters between 2 m and 3 m.
13. The bearing device according to claim 12, characterized in that, The elastomeric layer (2) and intermediate plate (3) (4) of the bearing ring (18) have a tangential torsional stroke under normal operating conditions through shear deformation, the tangential torsional stroke being 30-150%, preferably 30-60%, of the thickness of a single elastomeric layer (2).
14. The bearing device according to any one of claims 1-13, characterized in that, The spacer elements (6) and (7) are shaped and arranged such that they close the corresponding arc segments (1) outward and inward.
15. The bearing device according to any one of claims 1-14, characterized in that, A pre-clamping stroke in the form of a gap (9) is provided between the spacer element (6) (7) and the adjacent intermediate plate (3) (4), the pre-clamping stroke being closed in the clamped state of the component.
16. The bearing device according to any one of claims 1-15, characterized in that, All or part of adjacent arc segments (1) are connected to each other by overlapping, wherein the overlapping is achieved by the relative movement of the radially outer and radially inner spacers (6) (7) and / or end plates (5) and / or closed annular segments (8) of the respective arc segments.
17. The bearing device according to any one of claims 1-16, characterized in that, One or more circular arc segments (1) are omitted from the bearing ring (18).
18. The bearing device according to any one of claims 1-17, characterized in that, The arc segment (1) has stop elements (50)(51)(52)(53)(54)(55)(102)(101)(103) that restrict the torsional movement of the elastomeric layer (2) and intermediate plate (3)(4) of the arc segment (1) in the event of an extreme operational event.
19. The bearing device according to claim 18, characterized in that, As a stop element, protrusions (50) and (51) are provided together with correspondingly formed gaps (52) and (53), the gaps providing the protrusions with a predetermined free space (54) and (55) for movement. (i) The protrusion (50) is placed on the radially outer intermediate plate (4) and extends into the recess (52) of the radially inner spacer (7), and (ii) The protrusion (51) is placed on the radially inward intermediate plate (3) and extends into the recess (53) of the radially outward spacer element (6). The pre-defined free space of motion (54) (55) determines the maximum stop stroke of the corresponding protrusion and thereby limits the torsional stroke and shear deformation of the component involved in the arc segment (1).
20. The bearing device according to claim 18, characterized in that, A plate (102) is provided as a stop element, which is flush with the end side of the arc segment (1), and the intermediate plate (3) of the adjacent arc segment (1) opposite to the plate (102) is shortened in length by the maximum stroke (101) of a predetermined torsional stop angle (103), thereby being able to impact the plate (102) in the case of extreme events and thereby limiting the torsional stroke and shear deformation of the components involved in the arc segment (1).
21. The bearing device according to claim 20, characterized in that, The pre-given stop angle (103) is greater than the torsion angle of the arc segment (1) under normal operating conditions.
22. An application of a bearing device or coupling according to any one of claims 1-21 for bulk acoustic decoupling of two interconnected, rotationally symmetric, torque-exposed machine parts.
23. A wind power generation device, comprising a tower, a nacelle, a rotor, and a transmission mechanism or a generator, characterized in that, It has a bearing assembly according to any one of claims 1-21.
24. The wind power generation equipment according to claim 23, characterized in that, The bearing assembly connects the rotor bearing housing (15) (16) of the equipment to the transmission mechanism housing or the generator housing (17).