Elastomer bushing and elastic bearing, especially for wind turbines

Abstract

Elastomer bushing (3) for an elastic bearing (1) of a drive train component of a wind turbine, in particular a gearbox, on a supporting structure, such as a machine carrier of the wind turbine, comprising a bearing device (9) decoupling the drive train component and the supporting structure from each other, which comprises two half-shells (5, 7), wherein the bearing device (9) is configured to roll on the drive train component and / or the supporting structure.

Description

[0001] The present invention relates to an elastomer bushing for an elastic bearing, in particular for a drivetrain component, especially of a wind turbine. Furthermore, the present invention relates to an elastic bearing, in particular a decoupling bearing, for mounting a drivetrain component, in particular a gearbox, of a wind turbine on its supporting structure, such as a machine carrier.

[0002] In wind turbines, a high torque is transmitted from the rotor to the gearbox and from there to the generator. To reduce the dynamic loads on the gearbox and supporting structure, elastic bearings are typically used in the gearbox supports. These elastic bearings incorporate elastic bushings for vibration and shock isolation, which are integrated into the drivetrain bearing arrangement and are, for example, part of the floating bearing unit within the drivetrain. The floating bearing unit consists of two or four elastic bushings. The elastic bushings are connected to the gearbox via the torque arm (axle bolt) and to the supporting structure or machine carrier via bearing blocks.The elastic bushings are required to withstand the high and fluctuating forces acting on the bearing, for example due to wind, and to be as soft as possible in the longitudinal direction so that play in the axle bolt is ensured.

[0003] German patent DE 10 2020 119 832 A1 discloses a generic elastic bearing with improved flexibility regarding the adjustability of axial and / or radial stiffness. This bearing consists of two half-shells made of an elastomer with a predetermined hardness, exhibiting varying axial stiffness along their longitudinal axis. This allows the bearing to meet significant load requirements, particularly in the radial direction, while simultaneously adjusting the axial stiffness according to specific requirements. Although the elastic bearing described in DE 10 2020 119 832 A1 possesses a good ratio of radial to axial stiffness—high stiffness in the vertical and horizontal directions and lower stiffness in the axial direction—it has been found that the axial stiffness remains too high for the intended application.

[0004] Furthermore, US 2013 / 0 202 232 A1 describes a structurally complex and complex-to-assemble bearing for a main shaft of a wind turbine, in which multi-part sliding bearing elements are combined with a multi-layered casing, wherein the inner surface of the casing is coupled to a sliding bearing element and a sliding piece.

[0005] DE 10 2010 042 296 A1 discloses a rolling bearing for a wind turbine. GB 484 877 A and GB 595 578 A disclose improved elastic joints and bearings, respectively. Furthermore, CN 1 11 765 044 A discloses an overspeed protection device for a wind generator, and DE 102 42 707 B3 discloses a wind turbine with a concentric gearbox / generator arrangement.

[0006] The object of the present invention is to improve upon the disadvantages of the known prior art, in particular to provide an elastomer bushing and an elastic bearing for wind turbines in which the conflict of objectives between high radial stiffness and low axial stiffness is resolved and / or which has reduced axial stiffness without reducing radial stiffness.

[0007] This task is solved by the characteristics of independent claims.

[0008] This application provides an elastomer bushing for an elastic bearing, particularly for a drivetrain component, especially of a wind turbine. For example, it is an elastomer bushing for an elastic bearing of a gearbox on a support structure, such as a machine frame of a wind turbine. Elastic bearings are used in wind turbines to absorb the dynamic loads acting on the drivetrain component and the support structure. The elastomer bushing can provide damping and decoupling of vibrations, structure-borne noise, and / or vibrations. Regarding the basic installation situation of the elastomer bushing or the elastic bearing, reference is made to EP 2 516 883 B1, the relevant content of which is incorporated into the present application by reference.

[0009] The elastomer bushing according to the invention comprises a bearing assembly that decouples the drivetrain component and the support structure from one another. For example, the bearing assembly forms the elastomer bushing. The bearing assembly is formed from two half-shells. Alternatively, the bearing assembly can, for example, be formed from more than two parts. By way of example only, exemplary embodiments of elastomer bushings according to the invention are described below using the exemplary embodiment of a bearing assembly formed from two half-shells. It is clear that the descriptions apply analogously to the other preferred embodiments of the bearing assembly. The bearing assembly is designed to roll on the drivetrain component and / or the support structure. The bearing assembly or the half-shells can each be made from a single piece of elastomer, in particular monolithically and / or with a Shore hardness of more than 85 Shore A.Shore hardness is a material property for elastomers and plastics, defined in the standards DIN EN ISO 868, DIN ISO 7619-1, and ASTM D 2240-00. The two halves can be made of the same material and / or have the same dimensions. When installed in the elastic bearing, the two halves can abut each other face-to-face to form a cylindrical opening, for example, for a drivetrain component fastener such as a torque arm or axle bolt. The wall thickness of the halves can be significantly less than their circumference. In cross-section, the halves can have a C-shape or a semi-circular shape.The preferred Shore hardness of the half-shells, particularly the elastomer material, ensures the necessary load-bearing capacity. This allows the elastomer bushing to be designed so that it acts as a spring-elastic elastomer body in the radial direction, especially vertically and horizontally, as well as in the intermediate spatial directions, while in the axial direction, i.e., in the longitudinal direction of the elastomer bushing, it has a significantly lower supporting effect (floating bearing) or a significantly lower restoring force resulting from a low axial spring stiffness. Thus, on the one hand, a high spring stiffness can counteract the high loads acting on elastic bearings in wind turbines in the radial direction, and on the other hand, the conflict of aiming for the lowest possible stiffness in the axial direction is resolved by minimizing the transmissible forces in the axial (longitudinal) direction.For example, forces significantly exceeding 250 kN, particularly in the range of 750 kN to 1000 kN, act on an elastomer bushing of an elastic bearing under normal operating conditions, 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 under normal operating conditions, with a minimum radial stiffness in the horizontal direction of 160 kN / mm being preferable. In an axial direction oriented along the longitudinal axis of the elastomer bushing, a maximum stiffness of 12 kN / mm is sufficient to meet the requirements of the elastic bearing. The axial stiffness is limited by the rolling decoupling measure according to the invention.kept low, yet maintaining the desired spring stiffness perpendicular to the longitudinal axis direction, allowing the elastomer bushing to move freely in its longitudinal axis direction, i.e., for example in the direction of a main or rotor shaft enclosed in the gearbox, or to deflect and thereby absorb only small axial forces in order to establish the lowest possible axial stiffness.

[0010] For example, the load-bearing beam can be designed such that, in extreme load cases, such as a maximum vertical load exceeding 3000 kN, compression perpendicular to the longitudinal axis of more than 1%, particularly of approximately 1.5%, occurs. In the vertical direction, compression perpendicular to the longitudinal axis can result in expansion of 5% to 10%, particularly at least 6.4%.

[0011] In this context, a further aspect of the present invention is to retrofit existing elastic bearings with elastomer bushings made of half-shell pairs formed from elastomer pieces with the elastomer bushing according to the invention, in particular to replace the existing elastomer bushings made of half-shell pairs formed from elastomer pieces with the elastomer bushing according to the invention.

[0012] According to an exemplary embodiment, the bearing assembly is designed as a rolling bearing. Because the resistance between the components to be supported and between the components of the bearing assembly is essentially limited to rolling friction, the axial stiffness can be reduced as desired, while still reliably ensuring sufficient radial stiffness. Corresponding to the two-part design of the half-shells, the rolling bearing can also be designed in two parts, consisting of two semicircular segments in cross-section, which together form the complete bearing when assembled. For example, the rolling bearing can have at least one, and preferably several, rolling elements, which can be, for instance, spherical or cylindrical.Furthermore, it is conceivable that the rolling element has a profiled outer contour, for example, depending on the required axial stiffness. The rolling elements can be designed or configured such that they can deform by approximately 10% to 20% relative to their original geometry under normal load conditions or operating conditions of loads between 750 kN and 1000 kN. In extreme load conditions, particularly with loads significantly exceeding 1000 kN, deformations of more than 40%, 50%, or even up to 60% relative to the original geometry are possible.

[0013] According to another exemplary embodiment, the rolling bearing comprises at least one rolling element, preferably elastically deformable and torsionally flexible, made in particular of an elastomeric material. The rolling element is deformable, in particular, in the radial direction of the elastomeric bushing. In other words, the deformability of the rolling element is utilized to make it compliant in a specific direction, thus allowing the stiffness of the elastomeric bushing or the bearing assembly to be adjusted in that direction. The rolling element can perform both a rolling motion (in the longitudinal direction) and damping of mechanical oscillations and / or vibrations that are introduced into the elastic bearing and / or the elastomeric bushing via the components to be supported. The compliance orThe deformability, particularly the torsional flexibility, of the rolling element can be used to generate a restoring force in the corresponding load direction, counteracting the applied force. This increases stiffness and limits deformability. Rolling elements can be designed as closed or segmented rings, as well as discrete individual bodies, such as spheres. In the case of a rolling element designed as a closed ring, the bearing assembly is a single piece. The cross-section of the rolling element can be round, oval, elliptical, polygonal (such as rhombus- or rectangular), or any other shape, as long as the desired rolling function in the longitudinal axis direction is ensured.In contrast to conventional rolling bearings, where significant deformation of the rolling elements is undesirable, the desired radial stiffness, particularly in the vertical and horizontal directions, can be set or achieved according to the invention via the deformability of the rolling element. For example, the rolling element is deformable to such an extent that it can be compressed to up to 60% of its original size. In the axial direction, the rolling element is able to provide a very low resistance force, which corresponds, for example, to less than 5%, in particular less than 3% or less than 1% of the radial resistance forces.

[0014] The rolling bearing can also comprise several rolling elements, particularly those of identical construction and adjacent in the longitudinal axis direction, which together form the rolling bearing and perform a substantially identical rolling motion during the rolling movement of the bearing assembly. An intermediate segment, made of a different material than the rolling element itself, can be arranged between each pair of adjacent rolling elements in the longitudinal axis direction. These intermediate segments can, for example, serve to limit the axial relative movement between the rolling elements. They can also, for example, serve to control the overall rolling motion amplitude of the rolling bearing. Furthermore, the intermediate segments can be elastically deformable in the longitudinal axis direction. It is also possible for each pair of adjacent rolling elements to be connected or coupled to one another.For example, this can be achieved at defined positions via connecting means or connection points. In another exemplary embodiment, the rolling element or the multiple rolling elements can have a star-shaped profile in cross-section, wherein, in particular, the star shape is oriented such that one star point, in particular two opposing star points, point in the longitudinal axis direction and another star point, in particular two opposing star points, are oriented perpendicular to it. According to an exemplary further development, the rolling element comprises a semicircular insertion strip, in particular a semicircular shape of the insertion strip, onto which at least two, in particular three, four or five, rolling element segments are inserted to form one rolling element each, wherein the rolling element segments are rotatably mounted relative to the insertion strip.For example, the rolling element segments can also be rigidly connected to the mounting strips. Furthermore, it is possible for the rolling element to be provided with stiffening ribs, which may be oriented, for example, transversely, and especially perpendicularly, to the longitudinal axis. In another exemplary embodiment, the rolling element has a cross-sectional shape that varies in its direction of extension. It may be provided that a thickening, particularly a star-shaped one, is present in the six o'clock position to ensure contact between the rolling element and the bearing block component or the gearbox pin.

[0015] In a further exemplary embodiment of the present invention, the bearing assembly, in particular the rolling element of the rolling bearing, is further configured to twist at least section by section during rolling on the drivetrain component and / or the support structure and / or to generate a restoring force directed against the rolling motion. The restoring force can be understood as the tendency of the bearing assembly to return to its original, and in particular undeformed, state. Because the rolling element twists or rotates during rolling, the axial stiffness in the direction of the rolling motion can be increased compared to a pure rolling motion, and in particular adjusted to a desired level. Alternatively or additionally, a restoring force, which in particular increases linearly at least temporarily, can occur during rolling, optionally in combination with twisting or rotating the rolling element.Therefore, the bearing can be designed in such a way that during the initial rolling movement up to a certain amplitude of movement and / or a limit of the restoring force, the bearing has a desired low stiffness, while from this certain predetermined point in time the axial stiffness is increased to a level that makes further rolling movement difficult or prevents it altogether.

[0016] In a further exemplary embodiment of the present invention, the bearing assembly is designed as a rolling bearing and comprises at least one rolling element with a rolling section, in particular a semi-ring-shaped section, and a base. The rolling section can, for example, also be semi-cylindrical. Furthermore, the rolling element is designed such that the rolling section twists relative to the base as it rolls against the drivetrain component and / or the support structure. This twisting can be achieved by the base being rigidly connected to the rolling element and not moving with it during the rolling motion. This results in a relative movement between the rolling element and the base, which, due to the rolling motion, leads to a twisting or torsion of the rolling element.For example, the rolling element can be axially symmetric in cross-section and have a particularly constant rolling section, at whose opposite ends a section of the base is arranged, so that the rolling section can twist in the area between the base sections.

[0017] According to an exemplary embodiment of the elastomer bushing according to the invention, the rolling bearing comprises at least one rolling element, which is particularly elastically deformable, with a reinforcing element, for example made of plastic, polyamide, glass fiber, carbon fiber, fabric, or metal, preferably embedded within it. The reinforcing element can be dimensioned according to requirements with regard to the desired increase in strength. For example, the reinforcing element can be thin-walled and / or plate-like. In particular, the reinforcing element can be pre-deformed relative to its shape in the installed or operating state or be pre-stressed within the rolling element, thereby achieving a higher radial load capacity.

[0018] In a further exemplary embodiment of the present invention, the bearing assembly is designed as a rolling bearing and comprises at least two, in particular at least three, four or at least five, rolling elements arranged side by side in the longitudinal axis direction, which are arranged and / or matched to one another such that, when the elastomer bushing is subjected to a radial load exceeding a limit load, in particular greater than 1,500 kN, in particular greater than 1,600 kN, greater than 1,700 kN or greater than 1,800 kN, the at least two rolling elements are pressed against each other to abruptly increase the radial stiffness in the longitudinal axis direction. For example, the rolling elements can be designed such that they exhibit a linear spring characteristic up to the limit load.From the point of limiting load onwards, the radial stiffness can be increased abruptly or abruptly by pressing the rolling elements against each other, particularly since the at least two rolling elements lock against each other, preventing further deformation, especially compression. For example, the at least two rolling elements can be arranged at rest in the longitudinal axis direction, particularly up to their limiting load, at a distance from each other that decreases with increasing radial load, until the predetermined limiting load causes the rolling elements to be pressed against each other.

[0019] According to an exemplary embodiment of the elastomer bushing according to the invention, the rolling bearing further comprises a base that retains the rolling elements and remains essentially undeformed when the elastomer bushing is subjected to radial load. The base can primarily, and in particular exclusively, serve to retain the rolling elements and also to enable the mounting of the bearing assembly's half-shells with the components to be supported. For example, the base is designed as a substantially flat, plate-like connecting web for joining the at least two rolling elements and / or has a flat cross-section. Furthermore, the base can be configured to be received, in particular by clamping or floating action, between two bearing block parts of a bearing, especially according to the invention, for supporting a drivetrain component, so that the bearing assembly or the elastomer bushing remains in position during assembly.If the bearing is clamped, it is fixed both circumferentially and longitudinally. In the case of a floating bearing, the bearing is fixed circumferentially. Securing the longitudinal position can be achieved, for example, by a thickened area of ​​the rolling elements, particularly in their center, to prevent them from losing contact with the gearbox pin and / or clamping half.

[0020] In a further exemplary embodiment of the elastomer bushing according to the invention, the elastomer bushing exhibits an axial stiffness in the longitudinal direction in the range of 4 kN / mm to 14 kN / mm, particularly in the range of 5 kN / mm to 13 kN / mm or in the range of 5 kN / mm to 12 kN / mm. Alternatively or additionally, the radial stiffness exhibits a sharp increase when the elastomer bushing is subjected to a radial load exceeding a limit load, particularly greater than 1,500 kN, 1,600 kN, 1,700 kN, or 1,800 kN. Up to the limit load, the radial stiffness can increase essentially linearly with the increase in load.

[0021] 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 the vertical direction, than in a second radial direction transverse to the longitudinal axis direction, in particular the horizontal direction. For example, at least one half-shell can have a stiffening structure oriented in the first radial direction, in particular horizontally, such as a stiffening projection or a stiffening rib, which increases the radial stiffness in this direction and is capable of absorbing further forces. For example, forces between 750 kN and 1000 kN act on an elastomer bushing of an elastic bearing in a normal operating condition, 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 under normal operating conditions, with a minimum radial stiffness in the horizontal direction of 160 kN / mm being preferable. In an axial direction oriented along the longitudinal axis of the elastomer bushing, a maximum stiffness of 12 kN / mm is sufficient to meet the requirements of the elastic bearing.

[0022] According to an exemplary embodiment of the present invention, the bearing device comprises two half-shells, and at least one half-shell has at least one contact projection, such as a contact rib, 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, for the bearing device. In a further exemplary embodiment, the at least one half-shell has two contact projections arranged circumferentially at a distance from each other such that the bearing device rests against both contact projections at its end faces, i.e., at the circumferential ends. For example, the lining or the bearing device can be clamped between the two contact projections.The mounting projection, in particular the mounting projections, can have a mounting flank that is strongly inclined relative to the outer and / or inner surface of the half-shell and / or a rear flank facing away from the bearing device, which is inclined relative to the outer and / or inner circumference of the half-shell, in particular is inclined less than the mounting flank.

[0023] In a further exemplary embodiment of the elastomer bushing according to the invention, the bearing assembly comprises two half-shells and two opposing circumferential ends of the half-shells, which rest against each other, particularly to form the bushing. These are designed to form a tongue and groove and / or dovetail connection with two bearing block parts on the wind turbine side, particularly on the machine carrier side, for receiving the elastomer bushing, in particular by clamping or floating. The positive and / or force-fit connection of the half-shells with the bearing block parts ensures, firstly, reliable and simple assembly, since the assembly sequence and position of the components are defined, and secondly, provides reliable protection against relative movement of the components to each other transversely to the longitudinal axis.

[0024] In an exemplary embodiment 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 radially to engage behind a groove formed in the bearing block parts. In other words, the radial projection extends by at least 30%, 40%, or 50% of the longitudinal extent of the half-shells and projects radially away from the outer circumference of the half-shells in order to engage in the grooves formed in the bearing block parts and, in particular, to engage behind the groove flanks. This ensures a secure positional engagement of the half-shells in the bearing block parts.

[0025] In an exemplary embodiment of the present invention, at least one elastomeric element comprises polyurethane. For example, polyurethane-polyester or polyester-urethane rubber is used. Urelast is preferred. The aforementioned materials for the elastomeric element have proven particularly advantageous, especially due to their high load-bearing capacity, high tensile strength, and very good wear resistance. Primarily because of the high load-bearing capacity, it is possible to make the elastomeric bushing smaller. This results in advantages with regard to installation space, material requirements, and costs. Urelast is generally a cast elastomer.

[0026] According to a further exemplary embodiment of the elastomer bushing according to the invention, the half-shells each have a central axis which, when the half-shells are in contact with each other and / or in the assembled state in the bearing, particularly in the operating state, are oriented concentrically to each other. Due to the concentric arrangement, further advantages in terms of installation space result. To establish different stiffnesses in different directions, it is no longer necessary, for example, to configure the half-shells as oval or elliptical and / or to arrange them eccentrically to each other in the assembled state in the elastic bearing.In the assembled state, the elastomer piece half-shells essentially form a ring shape, comprising a particularly cylindrical passage for a fastening part of the drivetrain component, such as the torque support or the axle bolt, and an at least approximately round outer circumference which, in the assembled state, is contacted in the bearing, particularly in the operating state, by two bearing block parts, in particular is completely surrounded and / or is received in a clamping or floating manner.

[0027] In an exemplary embodiment 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 direction. For example, the axial stiffness is less than 10%, and 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 mounting the drivetrain component on the supporting structure, in particular the machine frame, of the wind turbine. When using the elastomer bushing in floating bearings, a particularly low axial stiffness is desirable. Furthermore, it is possible to design the radial stiffness depending on the orientation, whereby, for example, the radial stiffness in the horizontal direction can be greater or less than the radial stiffness in the vertical direction.For example, the radial stiffnesses in the different directions can differ by 5%, 8%, or even more than 10%.

[0028] In another 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 between the two half-shells is between 0.1% and / or at most 5%.

[0029] 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 mounting a drivetrain component, especially a gearbox, of a wind turbine on its supporting structure, such as its machine frame. For example, this is an elastic bearing of a gearbox on a supporting structure, such as a machine frame, of a wind turbine. Elastic bearings are used in wind turbines to absorb the dynamic loads acting on the drivetrain component and the supporting structure. The elastic bearing can provide damping and decoupling of vibrations and / or structure-borne noise.With regard to the basic installation situation of the elastic bearing, reference is made to EP 2 516 883, the content of which is incorporated into the present application by reference.

[0030] The elastic bearing according to the invention comprises an elastomer bushing comprising a bearing device that decouples the drivetrain component and the support structure from each other, which in particular comprises two half-shells, wherein the bearing device is configured to roll on the drivetrain component and / or the support structure, wherein the elastomer bushing is designed in particular according to one of the exemplary aspects or exemplary embodiments described above, and two bearing block parts for receiving the elastomer bushing in a particularly clamping or floating manner.

[0031] In an exemplary embodiment of the elastic bearing according to the invention, the bearing block parts have mutually facing, and in particular identically shaped, grooves, and radial projections are formed on two mutually facing circumferential ends of the overlapping half-shells. The grooves and the radial projections are precisely matched to each other. According to an exemplary embodiment, the radial projections are shaped to engage behind the groove flanks in the radial direction, in particular in the manner of a tongue and groove joint and / or dovetail joint. In the assembled state, the two grooves of the bearing block parts lie directly above one another and define a common receiving space for the radial projections of the half-shells engaging therein.By aligning the grooves and radial projections, in particular by the positive and / or force-fit engagement of the groove flanks by the radial projections, a particularly compact and fixed elastic bearing is created, so that relative movements around the longitudinal axis direction are excluded.

[0032] According to an exemplary embodiment of the elastic bearing according to the invention, the elastic bearing further comprises a bearing journal supported by the elastomer bushing, which is provided with a device for supporting the bearing assembly in the longitudinal axis direction under a predetermined load condition, in particular under a predetermined radial load on the elastomer bushing. The elastomer bushing can be adjusted such that, under a predetermined radial load, which leads to a predetermined deformation or compression of the elastomer bushing, it reaches a degree of deformation with which the elastomer bushing is supported by the bearing assembly, thereby limiting, and in particular preventing, further deformation of the elastomer bushing in the longitudinal axis direction.According to an exemplary embodiment, the bearing pin has a radial projection arranged in relation to the bearing assembly such that, when the predetermined load condition is reached, the bearing assembly is pressed against the radial projection. For example, the elastic bearing further comprises an axial retainer, such as an axial locking washer, arranged on a side opposite the radial projection of the elastomer bushing and, in the predetermined load condition, together with the radial projection, forming a deformation limit on both sides for the elastomer bushing.

[0033] 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.

[0034] Preferred embodiments are specified in the dependent claims.

[0035] Further properties, features and advantages of the invention will be clarified below by describing preferred embodiments of the invention with reference to the accompanying exemplary drawings, which show: Fig. 1 a perspective schematic diagram illustrating the intended use of exemplary embodiments of elastic bearings according to the invention; Fig. 2 a front view of an exemplary embodiment of an elastic bearing according to the invention; Fig. 3 the elastic bearing made of Fig. 3 in section view; Fig. 4 a sectional view of another exemplary embodiment of an elastic bearing according to the invention; Fig. 5 the elastic bearing from the Fig. 2 to 4 in another sectional view; Fig. 6 - 9 different views of a bearing device of an exemplary embodiment of an elastomer bushing according to the invention in half-shell design; Fig. 10 a further perspective sketch of principle for the intended use of exemplary embodiments of elastic bearings according to the invention; Fig. 11-16 different views of further bearing devices of exemplary embodiments of an elastomer bushing according to the invention in half-shell design; and Fig. 17, Fig. 18 different views of a reinforcing element of a rolling element of an exemplary elastomer bushing.

[0036] Based on the Fig. Sections 1 to 18 describe exemplary embodiments of elastic bearings according to the invention, which are generally designated by reference numeral 1, and of elastomer bushings according to the invention, which are generally designated by reference numeral 3. The elastic bearing 1 serves, in principle, to provide elastic damping support to a gearbox 11 of a wind turbine on its supporting structure, in particular a machine carrier, in order to absorb and dampen the dynamic loads acting on the drivetrain component, the gearbox, and / or the supporting structure. Fig. Figure 1 schematically indicates the gearbox 11 and comprises a large-dimensioned main shaft 13, gearbox supports 15, 17, on each of which a gearbox bearing journal 19, 21 is arranged, which are mounted or supported on the supporting structure of the wind turbine via an elastomer bushing pair 3 assigned to each elastic bearing 1.

[0037] An elastic bearing 1 according to the invention comprises, according to the exemplary embodiments, the following main components: an elastomer bushing 3 according to the invention, which is formed from two half-shells 5, 7 forming a bearing device 9 that decouples the drive train component and the support structure from each other; two bearing block parts 23, 25, which are in particular identically designed, for receiving the elastomer bushing 3, in particular by clamping or floating, which are to be arranged on the support structure side and are decoupled or damped from each other by the elastic bearing 1 with regard to vibration and / or oscillation.

[0038] The transmission center point, indicated by a transmission center axis G, lies at the level of the bearing center point, indicated by the longitudinal axis A. Alternatively, the transmission center point G can be offset, particularly in the vertical direction, with respect to the longitudinal axis A.

[0039] Referring to the first embodiment of an elastic bearing 1 according to the invention as shown in the partial exploded view in Fig. Figure 1, on the right, shows the individual components in exploded view for clarity. The two clamping halves or bearing block parts 23, 25 define a cylindrical receiving space 27 for supporting the respective gearbox bearing journals 19, 21 and for receiving an elastomer bushing 3 for vibration-damping decoupling of the gearbox bearing journals 19, 21 from the supporting structure of the wind turbine. The two half-shells 5, 7 have a semicircular cross-section and a cross-section that varies section by 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 facing the other half-shell 7, 5, so that the half-shells 5, 7 define a semi-cylindrical, hollow interior space which serves to receive a connecting part of the drivetrain component, namely, for example, a gearbox support 15, 17.An inner wall 29 of the half-shells 5, 7, which limits the interior space, is uniformly curved along the longitudinal axis A.

[0040] According to the invention, the bearing assembly 9 is designed to roll longitudinally along the drivetrain component and / or the support structure. As shown in the exemplary figures, the bearing assembly 9 is formed by the pair of half-shells 5, 7, which, according to preferred embodiments, form a rolling bearing. The bearing assembly 9 ensures a reduction in axial resistance or the ability to absorb axial forces, while simultaneously providing the necessary radial deformability for the desired radial stiffness. The half-shells 5, 7 can have contact projections or contact ribs on their outer surfaces facing the respective bearing block parts 23, 25. These projections extend in the longitudinal axis direction A of the elastomer bushing and project radially from the outer surface of the half-shells 5, 7. The assembly state of the elastic bearing 1 is shown in Fig. 2 and in the sectional views according to the Fig. 3 to 5 are visible.

[0041] Especially from Fig. Figure 2 further shows the form-fit and / or force-fit connection between the half-shells 5, 7 and the bearing block parts 23, 25, which, according to the exemplary embodiment, is designed as a dovetail joint 37. The dovetail joint 37 comprises radial projections 39, 41 on the half-shell side, which extend in the longitudinal axis direction A and are arranged at a circumferential end of the half-shells 5, 7, as well as receiving grooves 43, 45 on the bearing block side, into which the fastening projections 39, 41 can engage. Due to the form-fitting and, in particular, the design as a dovetail joint 37, the projections are designed with respect to the grooves such that they engage behind them in the radial direction in order to be received therein with particular positional security. In the assembled state, the fastening projections 39, 41 are floatingly mounted within the receiving grooves 43, 45 in order to keep the axial stiffness as low as possible.In an alternative embodiment, if higher axial stiffness is desired, the fastening projections 39, 41 can be clamped within the receiving grooves 43, 45. Fig. 3 is a sectional view along line III-III from Fig. 2 shown.

[0042] For example, the storage device 9, as it appears in the preferred embodiments, in particular according to the Fig. 3 to 16 are implemented as rolling bearings with a plurality of rolling elements 47 arranged at a distance from each other in the longitudinal axis direction A, in order to achieve the desired low axial stiffness through the rolling ability of the rolling elements 47 on the components to be supported. Fig. 3 It can also be seen that the bearing journal 19, 21 is provided with a support device 53 which, according to the Fig. 3 is realized as a radial projection 55 and serves to support the bearing devices 9 in the longitudinal axis direction A under a predetermined load condition, such as a predetermined radial load on the elastomer bushing 1. Furthermore, in Fig. 4 A preferred embodiment of the rolling elements 47 is shown in that the rolling elements 47, which are made of a particularly elastically deformable material, are provided with a particularly embedded reinforcing element 57, for example made of plastic, such as polyamide, or metal.

[0043] The Fig. 4 and Fig. Figure 5 shows schematic views of another elastic bearing 1, where the Fig. 4 and a sectional view looking in the direction of the longitudinal axis A and the Fig. 5 are a sectional view with a viewing direction perpendicular to it. Fig. Figure 4 shows an exemplary embodiment in which the rolling elements 47 can be segmented in the circumferential direction.

[0044] Referring to the Fig. 6, Fig. Figures 7, 8, and 9 describe exemplary embodiments of bearing devices 9 of the elastomer bushings 3 according to the invention in more detail. The two in Fig. 6 and Fig. The 7 illustrated half-shells 5,7 form the bearing device 9, which in the assembled state ( Fig. 2) completely surround the bearing journal 19, 21 and rest against each other along the end face in the longitudinal axis direction A along the cutting direction. Structurally, the two half-shells 5, 7 are identical and each has several rolling elements 47 and a base 59 which holds the rolling elements 47 and is thus firmly connected to them. This base consists of two identically formed flat plate sections 61 that extend in the longitudinal axis direction A beyond the longitudinal extent of the rolling elements 47 and which, in the assembled state ( Fig. 2) are positively engaged in the bearing blocks 23, 25 by means of the fastening projections 39, 41 arranged thereon, in particular by clamping or floating. In other words, the base 59 is held in position in the assembled state and remains essentially undeformed during operation of the wind turbine under any force influences on the elastic bearing 1 or on the bearing assembly 9. The rolling elements 9 are in accordance with the Fig. 6 and Fig. 7 are formed as circular, cylindrical rolling sections in cross-section, which are shaped according to the curvature of the bearing journal 19, 21 and are designed to roll in the longitudinal axis direction A against the components to be supported. Because the rolling elements 47, in particular the rolling sections 63, are rigidly connected at both ends to the rigid base 59, the rolling of the rolling elements 47 or the rolling sections 63 in the longitudinal axis direction A is accompanied by a twisting or torsion of the rolling sections 63, in particular relative to the base 59, about their own axis, which generates a particularly elastic deformation restoring force that represents a resistance force against further relative movement or rolling movement of the rolling elements 47 relative to the components to be supported.On each of the outermost rolling elements 47, front and rear in the longitudinal axis direction, a stop projection 69, 71 is arranged, which is shaped according to the curvature of the half-shell, but can have any cross-sectional design. The stop projections 69, 71 can bear against a corresponding projection of one of the bearing block parts or the gear pin. In the circumferential direction, the stop projections 69, 71 extend less far than the rolling elements. The rolling motion of the rolling elements is in . Fig. 7 schematically indicated by means of the arrow with reference sign a, which leads to the twisting of the same indicated by means of the arrow with reference sign b.

[0045] In the Fig. 8 and Fig. Figure 9 shows another exemplary embodiment of the storage device 9 in two different views. From the Fig. 8 and Fig. Figure 9 shows a further bearing device 9 according to the invention. The figures schematically depict an extreme load event, which occurs, for example, with a radial load on the elastomer bushing 1 of, for example, more than 1,900 kN, wherein the radial load leads to such a strong deformation of the individual rolling elements 47 that the change in geometry from round to substantially oval (reference numeral 65) indicates that the rolling elements 47 come into mutual contact with each other, so that further deformation is precluded. In other words, the rolling elements 47 block each other against further deformation, whereby the radial stiffness changes abruptly, in particular from the previously approximately linear course depending on the radial load, which means that the forces occurring can be transmitted to the supporting structure of the wind turbine without damage. As shown in Fig. 8 and Fig. As can be seen in Figure 9, the rolling elements 47 come into contact on each other facing outer circumferential surfaces and form a circumferentially oriented pressure line contact 67.

[0046] Fig. Figure 10 shows an embodiment of a half-shell 5, 7 in which an intermediate segment 73 is arranged between each pair of adjacent rolling elements 47, which can limit a movement amplitude in the longitudinal axis direction A or can, for example, be elastically deformable.

[0047] In the execution according to Fig. 11 has the half-shell 5, 7 instead of the intermediate segments 73 connecting means 75 to couple the rolling elements 47 spaced apart in the longitudinal axis direction A, thereby forming a rolling element unit of several rolling elements 47.

[0048] The execution according to Fig. Figure 12 differs from the preceding embodiments of the half-shells 5, 7 essentially in that no intermediate segments or connecting elements are provided, but the rolling elements 47 have a star-shaped cross-section in sections. The star shape is oriented such that two opposing star points 77, 79 are oriented in the longitudinal axis direction. Two further opposing star points 81, 83 are oriented essentially perpendicular to this and point in the direction of the mutually adjacent drive rod component and yield structure.

[0049] In Fig. Figure 13 shows another exemplary embodiment of a half-shell 5, 7. This differs from the previous embodiments essentially in that the rolling elements 47 are formed in multiple parts. The rolling elements 47 comprise a mounting strip 85 connecting the base 59 and three rolling element segments 87 mounted on the mounting strip, which are arranged at a distance from each other in the extension direction of the mounting strip 85, which can be uniform in particular.

[0050] The execution of the exemplary half-shell 5, 7 according to Fig. 14 differs from the design of the half-shell 5, 7 from the preceding figures essentially in that several stiffening projections or stiffening ribs 89 are arranged at a distance from each other in the longitudinal axis direction A on the plates 61 forming the base 59, each oriented in the direction of the opposite plate 61.

[0051] In the Fig. 15 and Fig. Figure 17 shows another exemplary embodiment of a half-shell 5, 7, in which the rolling elements have a cross-section that varies in the direction of extension of the rolling elements. In the three o'clock and six o'clock positions, the rolling elements 47 have a thickening, which can be star-shaped, for example, to ensure contact with the bearing block halves and the gearbox pin.

[0052] The Fig. 17 and Fig. Figure 18 shows an exemplary embodiment of a reinforcing element 57, which can be embedded in the rolling element 47. We conclude from a review of the Fig. 17 and Fig.As can be seen from Figure 18, the rolling element 47 of the reinforcement carrier 57 has a thin cross-section compared to its longitudinal extent and is curved according to the curvature of the rolling element 47. A multitude of holes 93 are provided in the reinforcement carrier 57 to reinforce the embedding or interlocking within the material of the rolling element. The reinforcement carrier 57 can be manufactured for the operating condition at 1400 kN so that it is as stress-free as possible under this load. In the casting tool during the production of the half-shells 5, 7, the reinforcement carriers 57 to be embedded are therefore pre-stressed to prevent possible breakage of the reinforcement carrier in extreme load cases due to overloading.

[0053] As an alternative to the rectangular profile contour of the reinforcement element 57 shown, concave and convex profiles are also possible. Furthermore, several reinforcement elements 57 can be combined in a rolling element 47, in particular cast together, if required.

[0054] The features disclosed in the foregoing description, figures and claims can be important for the realization of the invention in its various embodiments, both individually and in any combination. Reference symbol list 1 elastic bearing 3 Elastomer bushing 5.7 Half-shell 9 Storage facility 11 gearboxes 13 Main wave 15, 17 Gearbox support 19, 21 bearing journals 23, 25 Bearing block part 27 Interior 29 Inner wall 37 Dovetail joint 39, 41 fastening projection 43, 45 recordings 47 rolling elements 53 Support device 55 radial lead 57 Strength components 59 base 61 plate 63 Roll-off section 65 oval rolling element section 67 Press line contact 69, 71 lead 73 Intermediate segment 75 Fasteners 77, 79, 81, 83 Star point 85 Sliding strip 87 rolling element segment 89 stiffening rib 91 Thickening 93 holes A Longitudinal axis direction R Radial direction G Transmission center axle a rolling motion b Torsion

Claims

[1] Elastomeric bushing (3) for an elastic bearing (1) of a drive train component of a wind turbine, in particular a gearbox, on a support structure, such as a machine carrier of the wind turbine, comprising a bearing device (9) decoupling the drive train component and the support structure from each other, the bearing device comprising two half-shells (5, 7), wherein the bearing device (9) is configured to roll on the drive train component and / or the support structure. [2] Elastomer bushing (3) according to claim 1, wherein the bearing device (9) is designed as a rolling bearing. [3] Elastomer bushing (3) according to claim 2, wherein the rolling bearing comprises at least one rolling element (47) which is in particular elastically deformable, preferably torsionally deformable, and in particular made of an elastomer material. [4] Elastomer bushing (3) according to one of the preceding claims, wherein the bearing device, in particular the rolling element (47) of the rolling bearing, is further configured to twist at least section by section when rolling on the drive train component and / or the support structure and / or to build up a restoring force oriented against the rolling motion. [5] Elastomer bushing (3) according to one of the preceding claims, wherein the bearing device (9) is designed as a rolling bearing and has at least one rolling element (47) with a particularly semi-ring-shaped rolling section (63) and a base (59), wherein the rolling element (47) is designed such that when rolling on the drive train component and / or the support structure, the rolling section (63) twists relative to the base (59). [6] Elastomer bushing (3) according to one of claims 2 to 5, wherein the rolling bearing comprises at least one rolling element (47) which is particularly elastically deformable and includes a reinforcing element (57) which is particularly embedded and made of, for example, plastic such as polyamide, glass fiber, carbon fiber or metal. [7] Elastomer bushing (3) according to one of the preceding claims, wherein the bearing device (9) is designed as a rolling bearing and has at least two, in particular at least three, four or at least five, rolling elements (47) arranged side by side in the longitudinal axis direction, which are arranged and / or coordinated with each other in such a way that when the elastomer bushing (3) is subjected to a radial load above a limit load, in particular greater than 1500 kN, in particular greater than 1600 kN, 1700 kN or greater than 1800 kN, the at least two rolling elements (47) are pressed against each other to abruptly increase the radial stiffness in the longitudinal axis direction. [8] Elastomer bushing (3) according to one of claims 5 to 7, wherein the rolling bearing further comprises a base (59) retaining the rolling elements (47) which remains substantially undeformed when the elastomer bushing (3) is subjected to radial load. [9] Elastomeric bushing (3) according to one of the preceding claims, wherein the elastomeric bushing (3) has an axial stiffness in the longitudinal axis direction in the range of 4 kN / mm to 14 kN / mm, in particular in the range of 5 kN / mm to 13 kN / mm or in the range of 5 kN / mm to 12 kN / mm, and / or wherein the radial stiffness exhibits a sudden increase when the elastomeric bushing (3) is subjected to a radial load above a limit load, in particular greater than 1,500 kN, in particular greater than 1,600 kN, greater than 1,700 kN or greater than 1,800 kN. [10] Elastomer bushing (3) according to one of the preceding claims, wherein the bearing device (9) comprises two half-shells (5, 7) and at least one half-shell (5, 7) has at least one contact projection (69, 71) extending in the direction of the longitudinal axis of the half-shell (5, 7), such as a contact rib, for the bearing device (9), wherein in particular the at least one half-shell has two contact projections which are arranged at a distance from each other in the circumferential direction such that the bearing device (9) bears against both contact projections. [11] Elastomer bushing (3) according to one of the preceding claims, wherein the bearing device (9) comprises two half-shells (5, 7) and two mutually facing circumferential ends of the half-shells (5, 7) are designed to form a tongue and / or dovetail connection with two wind turbine-side, in particular machine carrier-side, bearing block parts (23, 25) for receiving the elastomer bushing (3) in a particularly clamping or floating manner. [12] Elastomer bushing (3) according to claim 11, wherein the circumferential ends are formed as radial projections extending in the direction of the longitudinal axis of the half shells (5, 7), the cross-section of which is shaped in the radial direction to engage behind a groove formed in the bearing block parts (23, 25). [13] Elastic bearing (1), in particular decoupling bearing, for supporting a drive train component, in particular a gearbox of a wind turbine on its supporting structure, such as a machine carrier, comprising an elastomer bushing (3), comprising a bearing device (9) decoupling the drive train component and the supporting structure from each other, which in particular comprises two half-shells (5, 7), wherein the bearing device (9) is configured to roll on the drive train component and / or the supporting structure, and two bearing block parts (23, 25) for in particular clamping or floating the elastomer bushing (3). [14] Elastic bearing (1) according to claim 13, wherein the bearing block parts (23, 25) have mutually facing, in particular identically designed, grooves and radial projections are formed on two mutually facing circumferential ends of the half-shells (5, 7), wherein the grooves and the radial projections are form-matched to each other, wherein in particular the radial projections are formed to engage behind the grooves in the radial direction, in particular in the manner of a tongue and groove joint and / or dovetail joint. [15] Elastic bearing (1) according to claim 13 or 14, further comprising a bearing pin supported by the elastomer bushing (3), which is provided with a device for supporting the bearing assembly (9) in the longitudinal axis direction under a predetermined load condition, in particular under a predetermined radial load on the elastomer bushing (3), wherein in particular a bearing pin has a radial projection which is arranged in relation to the bearing assembly (9) such that under the predetermined load condition the bearing assembly (9) is pressed against the radial projection.

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