DE102023105482A1 - Elastomer bushing and elastic bearing especially for wind turbines - Google Patents

Abstract

The present invention relates to an elastomer bushing for an elastic bearing of a drive train component of a wind turbine, in particular a gearbox on a support structure, such as a machine support, of a wind turbine, comprising a bearing device which decouples the drive train component and the support structure from one another and which in particular comprises two half shells, wherein the bearing device is designed to roll on the drive train component and/or the support structure.

Description

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

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

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

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

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

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

According to this, an elastomer bushing is provided for an elastic bearing, in particular of a drive train component, in particular of a wind turbine. For example, it is an elastomer bushing for an elastic bearing of a gearbox on a supporting structure, such as a machine support, of a wind turbine. Elastic bearings are used in wind turbines to absorb the dynamic loads that act on the drive train component and the supporting structure. The elastomer bushing can be used to dampen and/or decouple vibration and/or structure-borne noise. With regard to the basic installation situation of the elastomer bushing or the elastic bearing, please refer to EP2 516 883 , the relevant content of which is incorporated into the present application by reference.

The elastomer bushing according to the invention comprises a bearing device that decouples the drive train component and the support structure from one another. For example, the bearing device forms the elastomer bushing. The bearing device is formed in particular from two half-shells. Alternatively, the bearing device can be formed, for example, from a single part or from more than two parts. Purely by way of example, exemplary embodiments of elastomer bushings according to the invention are described below using the exemplary embodiment of a bearing device formed from two half-shells. It is clear that the embodiments apply analogously to the other preferred embodiments of the bearing device. The bearing device is designed to roll on the drive train component and/or the support structure. The bearing device or the half-shells can each be made from an elastomer piece, in particular monolithic and/or with a Shore hardness of more than 85 Shore A. The Shore hardness is a material characteristic value for elastomers and plastics, which is defined in the standards DIN EN ISO 868, DIN ISO 7619-1 and ASTM D 2240-00. The half shells can be made of be made of the same material and/or have the same dimensions. In an assembled state in the elastic bearing, the two half-shells can rest on one another at the front to form a particularly cylindrical passage, for example for a fastening part of the drive train component, such as the torque support or the axle bolt. The wall thickness of the half-shells can be significantly smaller than their circumferential extent. In cross-section, the half-shells can have a c-shape or a half-ring shape. The preferred Shore hardness of the half-shells, in particular of the elastomer piece material, ensures the necessary load-bearing capacity. This means that the elastomer bushing can be designed in such a way that it acts as an elastomer body with spring-elastic properties in the radial direction, in particular vertically and horizontally, as well as in the spatial directions in between, while in the axial direction, i.e. in the longitudinal axis direction of the elastomer bushing, it has a significantly lower supporting effect (loose bearing) or a significantly lower restoring force resulting from a small axial spring stiffness. This means that, on the one hand, the high loads in the radial direction acting on elastic bearings in wind turbines can be counteracted by a high spring stiffness, but on the other hand, the conflicting objective of achieving the lowest possible stiffness in the axial direction can be resolved by minimizing the transferable forces in the axial direction (longitudinal direction). For example, in a normal operating state, forces of significantly more than 250 kN act on an elastomer bushing of an elastic bearing, in particular in the range from 750 kN to 1000 kN, whereby a minimum radial stiffness in the vertical direction of 150 kN/mm is advantageous. In the horizontal direction, forces in the range from 0 kN to 500 kN act on the elastomer bushing in the normal operating state, whereby a minimum radial stiffness in the horizontal direction of 160 kN/mm is preferable. In an axial direction oriented in the longitudinal axis of the elastomer bushing, a maximum stiffness of 12 kN/mm is sufficient to meet the requirements of the elastic bearing. The rolling decoupling measure according to the invention limits or keeps the axial stiffness low, but still maintains the desired spring stiffness transverse to the longitudinal axis, whereby the elastomer bushing can move in a floating manner in its longitudinal axis direction, i.e., for example, in the direction of a main or rotor shaft enclosed in the gearbox, or can dodge and absorb only a small amount of axial force in order to establish the lowest possible axial stiffness.

For example, the strength member can be designed in such a way that in the case of extreme loads, for example with a maximum vertical load of over 3000 kN, a compression transverse to the longitudinal axis direction of more than 1%, in particular of about 1.5%, occurs. In the vertical direction, due to the compression transverse to the longitudinal axis direction, an expansion can occur which is in the range of 5% - 10%, in particular at least 6.4%.

In this context, a further aspect of the present invention consists in retrofitting 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 replacing the existing elastomer bushings made of half-shell pairs formed from elastomer pieces with the elastomer bushing according to the invention.

According to an exemplary embodiment, the bearing device is designed as a rolling bearing. Because there is essentially only rolling friction resistance between the components to be supported and the components of the bearing device, the axial rigidity can be reduced as desired, while it can still be reliably ensured that there is sufficient radial rigidity. The rolling bearing can also be designed in two parts in accordance with the two-part design of the half shells and consist of two segments with a semicircular cross section, which form the complete bearing when assembled. For example, the rolling bearing can have at least one, in particular several, rolling elements, which can be spherical, for example, or can have a cylindrical shape. Furthermore, it is conceivable that the rolling element has a profiled outer contour, for example depending on how high the axial rigidity is to be set. The rolling elements can be adjusted or designed in such a way that they can deform by approximately 10% to 20% in relation to the initial geometry in a normal load range or a normal operating state of loads between 750 kN and 1000 kN, whereby in an extreme load range with loads in particular significantly above 1000 kN, deformations of more than 40%, 50% or up to 60% in relation to the initial geometry are possible.

According to a further exemplary embodiment, the rolling bearing comprises at least one rolling element, in particular elastically deformable, preferably twistable, in particular made of an elastomer material. The rolling element is deformable in particular in the radial direction of the elastomer bushing. In other words, the deformability of the rolling element is used to make it flexible in a certain direction in order to increase the rigidity of the elastomer bushing or the bearing in this direction. of the bearing device. The rolling element can both perform a rolling movement (in the longitudinal direction) and dampen mechanical oscillations and/or vibrations that are introduced into the elastic bearing and/or the elastomer bushing via the components to be supported. The flexibility or deformability, in particular the torsion ability, of the rolling element can be used to build up a restoring force in the corresponding load direction that counteracts the force. This can increase the rigidity and limit the deformability. The rolling elements can be designed as closed or segmented rings or as discrete individual bodies, for example as balls. In the case of a rolling element designed as a closed ring, the bearing device is constructed in one piece. The cross-section of the rolling element can be round, oval, elliptical, polygonal, such as diamond or rectangular, or other shapes, as long as the desired rolling function in the longitudinal axis direction is ensured. In contrast to conventional rolling bearings, in which a strong deformation of the rolling elements is undesirable, according to the invention the desired radial stiffness, in particular in the vertical and horizontal directions, should be able to be set or achieved via the deformability of the rolling element. For example, the rolling element can be deformed in such a way that it can be compressed up to 60% of its initial size. In the axial direction, the rolling element is able to provide a very small resistance force, which corresponds, for example, to less than 5%, in particular less than 3% or less than 1% of the radial resistance forces.

The rolling bearing can also comprise a plurality of rolling elements, in particular identically constructed and adjacent in the longitudinal axis direction, which together form the rolling bearing and perform a substantially identical rolling movement during the rolling movement of the bearing device. An intermediate segment can be arranged between each two adjacent rolling elements in the longitudinal axis directions, which can consist of a different material than the rolling element itself. The intermediate segments can serve, for example, to limit the axial relative movement between the rolling elements. For example, the intermediate segments can also serve to move the rolling movement amplitude of the rolling bearing as a whole. Furthermore, the intermediate segments can be elastically deformable in the longitudinal axis direction. Furthermore, it is possible for two adjacent rolling elements to be connected to one another or coupled to one another. For example, this can be done at defined positions using connecting means or connection points. In a further exemplary embodiment, the rolling element or the plurality of 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, points in the longitudinal axis direction and another star point, in particular two opposing star points, are oriented perpendicular to it. According to an exemplary development, the rolling element comprises a part-circular insertion strip, a particularly part-circular shape of the plug-in strip, onto which at least two, in particular three, four or five, rolling element segments are plugged to form a rolling element each, wherein the rolling element segments are mounted so as to be rotatable relative to the plug-in strip. For example, the rolling element segments can also be rigidly connected to the plug-in strips. Furthermore, it is possible for the rolling element to be provided with stiffening ribs, which can be oriented, for example, transversely, in particular perpendicularly, to the longitudinal axis direction. In a further exemplary embodiment, the rolling element has a cross-sectional shape that varies in its direction of extension. In this case, it can be provided that a thickening, in particular in a star shape, is present in the six o'clock position in particular in order to ensure contact between the rolling element and the bearing block part or the gear bolt.

In a further exemplary embodiment of the present invention, the bearing device, in particular the rolling element of the rolling bearing, is further configured to twist at least in sections when rolling on the drive train component and/or the support structure and/or to build up a restoring force directed against the rolling movement. The restoring force can be understood as the effort of the bearing device to return to the original, in particular undeformed, state. Because the rolling is accompanied by a twisting or twisting of the rolling element, the axial rigidity in the direction of the rolling movement can be increased compared to a pure rolling movement, in particular set to a desired level. Alternatively or additionally, a restoring force that increases linearly, in particular at least temporarily, can accompany the rolling, optionally in combination with a twisting or twisting of the rolling element. In this respect, the bearing can be designed in such a way that during the initial rolling movement up to a certain movement amplitude and/or a limit value of the restoring force, the bearing has a desired low stiffness, while from this certain predetermined point in time onwards the axial stiffness is then increased to a level which makes further rolling movement difficult or impossible.

In a further exemplary embodiment of the present invention, the bearing device is designed as a rolling bearing and has at least one rolling body with a particularly semi-annular rolling section and a base. The rolling section can also be semi-cylindrical, for example. Furthermore, the rolling body is designed such that the rolling section twists relative to the base when rolling on the drive train component and/or the support structure. The twisting can be achieved by the base being firmly connected to the rolling body and not moving with the rolling movement of the rolling body. This results in a relative movement between the rolling body and the base, which leads to a twisting or torsion of the rolling body due to the rolling movement. For example, the rolling body can be axially symmetrical in cross section and have a particularly constant rolling section, at the opposite ends of which a section of the base is arranged, so that the rolling section can twist in the area between the base sections.

According to an exemplary development of the elastomer bushing according to the invention, the rolling bearing has at least one particularly elastically deformable rolling element with a particularly embedded strength carrier, for example made of plastic, polyamide, glass fiber, carbon fiber, fabric or metal. The strength carrier can be dimensioned as required with regard to the desired increase in strength. For example, the strength carrier can be thin-walled and/or plate-like. In particular, the strength carrier can be pre-deformed or pre-stressed in relation to its shape in the installed or operating state and integrated into the rolling element, whereby a higher radial load capacity can be achieved.

In a further exemplary embodiment of the present invention, the bearing device is designed as a rolling bearing and comprises at least two, in particular at least three, four or at least five rolling elements arranged next to one another in the longitudinal axis direction, which are arranged and/or coordinated with one another in such a way that when the elastomer bushing is loaded in the radial direction 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, the at least two rolling elements are pressed against one another to suddenly increase the radial stiffness in the longitudinal axis direction. For example, the rolling elements can be designed in such a way that they have a linear spring characteristic curve up to the limit load. From the limit load, the radial stiffness can be increased suddenly or abruptly by pressing against one another, in particular because the at least two rolling elements block one another against further deformation, in particular compression. For example, the at least two rolling elements can be arranged in the longitudinal axis direction in a rest state, in particular up to their limit load, at a distance from one another which becomes smaller with increasing radial load until the rolling elements are pressed against one another at the predetermined limit load.

According to an exemplary development of the elastomer bushing according to the invention, the rolling bearing further comprises a base which holds the rolling elements in place and which remains essentially undeformed when the elastomer bushing is loaded in the radial direction. The base can primarily serve, in particular exclusively, to hold the rolling elements and also to be able to mount the half-shells forming the bearing device with the components to be mounted. For example, the base is designed as a substantially flat, plate-like connecting web for connecting the at least two rolling elements and/or has a flat cross-section. Furthermore, the base can be designed to be accommodated in a clamping or floating manner between two bearing block parts of a bearing, in particular according to the invention, for mounting a drive train component, so that the bearing device or the elastomer bushing remains in position in the assembled state. If the bearing is accommodated in a clamping manner, it is fixed both in relation to the circumferential direction and in relation to the longitudinal direction. In the case of floating mounting, the bearing is fixed in the circumferential direction. The longitudinal position can be secured, for example, by a thickened area of the rolling elements, particularly in the middle, in order to prevent them from losing contact with the gear bolt and/or clamping half.

In a further exemplary embodiment of the elastomer bushing according to the invention, the elastomer bushing has an axial stiffness in the longitudinal axis direction in the range from 4 kN/mm to 14 kN/mm, in particular in the range from 5 kN/mm to 13 kN/mm or in the range from 5 kN/mm to 12 kN/mm. Alternatively or additionally, the radial stiffness has a sudden increase when the elastomer bushing is loaded in the radial direction 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. Up to the limit load, the radial stiffness can increase essentially linearly with the increase in the load.

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

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

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

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

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

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

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

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

According to a further aspect of the present invention, which can be combined with the preceding aspects and exemplary embodiments, an elastic bearing, in particular a decoupling bearing, is provided for supporting a drive train component, in particular a gearbox, of a wind turbine, in particular on its supporting structure, such as its machine carrier. For example, it is an elastic bearing of a gearbox on a supporting structure, such as a machine carrier, of a wind turbine. Elastic bearings are used in wind turbines to absorb the dynamic loads that act on the drive train component and the supporting structure. The elastic bearing can be used to dampen and/or decouple oscillations and/or vibrations and/or structure-borne noise. With regard to the basic installation situation of the elastic bearing, reference should be made to EP2 516 883 , the relevant content of which is incorporated into the present application by reference.

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

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

According to an exemplary development of the elastic bearing according to the invention, the elastic bearing further comprises a bearing pin supported by the elastomer bushing, which is provided with a device for supporting the bearing device 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, this reaches a degree of deformation with which the elastomer bushing is supported by the bearing device, whereby in particular further deformation of the elastomer bushing in the longitudinal axis direction is limited, in particular prevented. According to an exemplary development, the bearing pin has a radial projection which is arranged in relation to the bearing device such that when the predetermined load condition is assumed, the bearing device is pushed against the radial projection. jump is pressed. For example, the elastic bearing further comprises an axial securing means, such as an axial locking disk, which is arranged on an opposite side in relation to the radial projection of the elastomer bushing and, in the predetermined load state, together with the radial projection, represents a deformation limit on both sides for the elastomer bushing.

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

Preferred embodiments are specified in the subclaims.

• 1 eine perspektivische Prinzipskizze zum Einsatzzweck beispielhafter Ausführungen erfindungsgemäßer elastischer Lager;
• 2 eine Vorderansicht einer beispielhaften Ausführung eines erfindungsgemäßen elastischen Lagers;
• 3 das elastische Lager aus 3 in Schnittansicht;
• 4 eine Schnittansicht einer weiteren beispielhaften Ausführung eines erfindungsgemäßen elastischen Lagers;
• 5 das elastische Lager aus den 2 bis 4 in einer weiteren Schnittansicht;
• 6 - 9 verschiedene Ansichten einer Lagereinrichtung einer beispielhaften Ausführung einer erfindungsgemäßen Elastomerbuchse in Halbschalenausführung;
• 10 eine weitere perspektivische Prinzipskizze zum Einsatzzweck beispielhafter Ausführungen erfindungsgemäßer elastischer Lager;
• 11 - 16 verschiedene Ansichten weiterer Lagereinrichtungen von beispielhaften Ausführungen einer erfindungsgemäßen Elastomerbuchse in Halbschalenausführung; und
• 17, 18 verschiedene Ansichten eines Festigkeitsträgers eines Wälzkörpers einer beispielhaften Elastomerbuchse.

In the following, further properties, features and advantages of the invention will become clear by describing preferred embodiments of the invention with reference to the accompanying exemplary drawings, in which:

• 1 a perspective schematic diagram of the intended use of exemplary embodiments of elastic bearings according to the invention;
• 2 a front view of an exemplary embodiment of an elastic bearing according to the invention;
• 3 the elastic bearing made of 3 in sectional view;
• 4 a sectional view of another exemplary embodiment of an elastic bearing according to the invention;
• 5 the elastic bearing from the 2 to 4 in another sectional view;
• 6 - 9 various views of a bearing device of an exemplary embodiment of an elastomer bushing according to the invention in half-shell design;
• 10 a further perspective schematic diagram of the intended use of exemplary embodiments of elastic bearings according to the invention;
• 11 - 16 various views of further bearing devices of exemplary embodiments of an elastomer bushing according to the invention in half-shell design; and
• 17 , 18 different views of a strength member of a rolling element of an exemplary elastomer bushing.

Based on the 1 to 18 Examples of embodiments of elastic bearings according to the invention, which are generally provided with the reference number 1, as well as of elastomer bushings according to the invention, which are generally provided with the reference number 3, of elastic bearings 1 are described. The elastic bearing 1 basically serves to elastically dampen 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 which act on the drive train component, the gearbox and/or the supporting structure. In 1 the gearbox 11 is indicated schematically and comprises a large-dimensioned main shaft 13, gearbox supports 15, 17, on each of which a gearbox bearing journal 19, 21 is arranged, which are mounted or supported on the support structure of the wind turbine via a pair of elastomer bushings 3 each assigned to an elastic bearing 1.

According to the embodiments, an elastic bearing 1 according to the invention comprises 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 one another; two bearing block parts 23, 25, in particular identically designed, for receiving the elastomer bushing 3 in a particularly clamping or floating manner, which are to be arranged or are arranged on the support structure side and are decoupled or dampened from one another by the elastic bearing 1 with respect to oscillation and/or vibration.

The gear center, indicated by a gear center axis G, is at the level of the bearing center, indicated by the longitudinal axis A. Alternatively, the gear center G can be arranged offset, in particular in the vertical direction, with respect to the longitudinal axis A.

Referring to the first embodiment of an elastic bearing 1 according to the invention according to the partially exploded view in 1 , on the right the individual components are shown in an exploded view for better clarity. The two clamping halves or bearing block parts 23, 25 delimit a cylindrical receiving space 27 for supporting the respective gear bearing journals 19, 21 and for receiving an elastomer bushing 3 for the oscillation and/or vibration-damping decoupling of the gear bearing journals 19, 21 from the supporting structure of the wind turbine. The two half-shells 5, 7 have a semicircular shape in cross-section and have a cross-section that varies in sections in the longitudinal direction, i.e. along the longitudinal axis A. The half-shells 5, 7 are concavely curved and have an open side that faces the other half-shell 7, 5, so that the half-shells 5, 7 delimit a semi-cylindrical, hollow interior, which is used for Serves to accommodate a connecting part of the drive train component, namely, for example, a transmission support 15, 17. An inner wall 29 of the half-shells 5, 7 delimiting the interior is uniformly curved along the longitudinal axis A.

According to the invention, the bearing device 9 is designed to roll on the drive train component and/or the support structure in the longitudinal direction. According to the exemplary figures, the bearing device 9 is formed by the pair of half shells 5, 7, which according to the preferred embodiments form a rolling bearing. The bearing device 9 ensures a reduction in the axial resistance force or the ability to absorb axial forces, but at the same time ensures the necessary radial deformability for the desired radial rigidity. The half shells 5, 7 can have contact projections or contact webs on their outer surfaces facing the respective bearing block parts 23, 25, which extend in the longitudinal axis direction A of the elastomer bushing and protrude in the radial direction from the outer surface of the half shells 5, 7. The assembly state of the elastic bearing 1 is in 2 and in the sectional views according to the 3 to 5 visible.

In particular from 2 the positive and/or non-positive connection between the half-shells 5, 7 and the bearing block parts 23, 25 is also visible, which according to the exemplary embodiment is designed as a dovetail connection 37. The dovetail connection 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 matching of the shapes and in particular the design as a dovetail connection 37, the projections are designed in relation to the grooves in such a way that they engage behind them in the radial direction in order to be received therein in a particularly secure position. In the assembled state, the fastening projections 39, 41 are mounted floating within the receiving grooves 43, 45 in order to keep the axial rigidity as low as possible. In an alternative embodiment, if a higher axial rigidity is desired, the fastening projections 39, 41 can be clamped within the receiving grooves 43, 45. In 3 is a sectional view along the line III-III of 2 shown.

For example, the bearing device 9, as in the preferred embodiments in particular according to the 3 to 16 as a rolling bearing with a plurality of rolling elements 47 arranged at a distance from one another in the longitudinal axis direction A in order to produce the desired low axial stiffness through the rolling ability of the rolling elements 47 on the components to be supported. In 3 It can also be seen that the bearing pin 19, 21 is provided with a support device 53 which, according to the 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 4 a preferred embodiment of the rolling elements 47 is shown in that the rolling elements 47 consisting of a particularly elastically deformable material are provided with a particularly embedded strength carrier 57, for example made of plastic, such as polyamide, or metal.

The 4 and 5 show schematic views of another elastic bearing 1, wherein the 4 and a sectional view looking in the direction of the longitudinal axis A and the 5 a sectional view looking perpendicular to it. 4 shows an exemplary embodiment according to which the rolling elements 47 can be segmented in the circumferential direction.

Referring to the 6 , 7 and 8, 9 exemplary designs of bearing devices 9 of elastomer bushings 3 according to the invention are described in more detail. The two 6 and 7 The half shells 5, 7 shown form the bearing device 9, which in the assembled state ( 2 ) completely surround the bearing journal 19,21 and rest on each other with their front surfaces along the cutting direction in the longitudinal axis direction A. In structural terms, the two half shells 5, 7 are constructed identically and each have several rolling or roller elements 47 and a base 59 holding the roller elements 47 and firmly connected thereto, made of two identically formed flat plate sections 61 which extend in the longitudinal axis direction A beyond the longitudinal extent of the roller elements 47 and which in the assembled state ( 2 ) with the fastening projections 39, 41 arranged thereon are positively received in the bearing blocks 23, 25, in particular in a clamping or floating manner. In other words, the base 59 is held in position in the assembled state and remains essentially undeformed during operation of the wind turbine in the event of any force influences on the elastic bearing 1 or on the bearing device 9. The rolling elements 9 are in accordance with the 6 and 7 formed as circular, cylindrical rolling sections in cross section, which are shaped according to the curvature of the bearing pin 19,21 and are designed to roll in the longitudinal axis direction A on the components to be supported. Because the rolling elements 47, in particular the rolling sections 63, are firmly connected to the rigid base 59 at both ends, when the Rolling elements 47 or the rolling sections 63 in the longitudinal axis direction A are accompanied by a twisting or torsion of the rolling sections 63, in particular relative to the base 59, around their own axis, whereby a particularly elastic deformation restoring force is built up, which represents a resistance force against further relative movement or rolling movement of the rolling elements 47 relative to the components to be supported. On the respective outer rolling elements 47, the front and rear ones viewed in the longitudinal axis direction, there is a stop projection 69, 71, which is shaped according to the curvature of the half-shell, but can be designed as desired in cross-section. The stop projections 69, 71 can be supported on a projection assigned to them on one of the bearing block parts or the gear bolt. In the circumferential direction, stop projections 69, 71 extend less far than the rolling elements. The rolling movement of the rolling elements is in 7 schematically indicated by the arrow with the reference symbol a, which leads to the twisting of the same indicated by the arrow with the reference symbol b.

In the 8 and 9 Another exemplary embodiment of the storage device 9 is shown in two different views. From the 8 and 9 a further bearing device 9 according to the invention emerges. The figures schematically show an extreme load event which occurs, for example, when there is 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 essentially oval (reference number 65) indicates that the rolling elements 47 come into mutual contact with one another, so that further deformability is excluded.

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 occurring forces can be transmitted to the supporting structure of the wind turbine without damage. As in 8 and 9 As can be seen, the rolling elements 47 come into contact on mutually facing outer circumferential surfaces and form a circumferentially oriented press line contact 67.

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

In the execution according to 11 the half-shell 5, 7 has connecting means 75 instead of the intermediate segments 73 in order to couple the rolling elements 47 spaced apart in the longitudinal axis direction A to one another, whereby a rolling element unit is formed from a plurality of rolling elements 47.

The execution according to 12 differs from the previous designs 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, for example, 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 drive rod component and yield structure that are supported relative to one another.

In 13 another exemplary embodiment of a half-shell 5, 7 is shown. This differs from the previous embodiments essentially in that the rolling elements 47 are designed in several parts. The rolling elements 47 comprise a plug-in strip 85 connecting the base 59 to one another and three rolling element segments 87 each plugged onto the plug-in strip, which are arranged in the direction of extension of the plug-in strip 85 at a distance from one another, which can in particular be uniform.

The design of the exemplary half shell 5, 7 according to 14 differs from the design of the half-shell 5, 7 from the previous figures essentially in that on the plates 61 forming the base 59 there are several stiffening projections or stiffening ribs 89 arranged at a distance from one another in the longitudinal axis direction A, which are each oriented in the direction of the opposite plate 61.

In the 15 and 17 another exemplary embodiment of a half-shell 5, 7 is shown, 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 or six o'clock position, the rolling elements 47 have a thickening, which can be star-shaped, for example, in order to ensure contact with the bearing block halves and the gear bolt.

The 17 and 18 show an exemplary embodiment of a strength member 57, which can be embedded in the rolling element 47. We from a summary of the 17 and 18 As can be seen, the rolling element 47 of the reinforcement 57 has a thin cross-section compared to its Longitudinal extension and is curved according to the curvature of the rolling elements 47. A large number of holes 93 are provided in the strength member 57 in order to reinforce the embedding or the interlocking within the material of the rolling element. The strength member 57 can be manufactured for the operating state at 1400 kN so that it is as stress-free as possible in this state. In the casting tool during the manufacture of the half-shells 5, 7, the strength members 57 to be embedded are therefore pre-stressed in order to avoid any possible breakage of the strength member in the event of extreme loads due to overloading.

As an alternative to the illustrated rectangular profile contour of the strength member 57, concave and convex profiles are also possible. Furthermore, if required, several strength members 57 can be combined in one rolling element 47, in particular cast.

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

List of reference symbols

1

elastic bearing

3

Elastomer bushing

5.7

Half shell

9

Storage facility

11

Gearbox

13

Main shaft

15, 17

Gearbox support

19, 21

Bearing journal

23, 25

Bearing block part

27

Interior

29

Inner wall

37

Dovetail joint

39, 41

Mounting projection

43, 45

Receiving groove

47

Rolling elements

53

Support device

55

Radial projection

57

Strengthening elements

59

base

61

plate

63

Roll-off section

65

oval rolling element section

67

Press line contact

69, 71

Stop projection

73

Intermediate segment

75

Connecting elements

77, 79, 81, 83

Star point

85

Slide bar

87

Rolling element segment

89

Stiffening rib

91

thickening

93

Hole

A

Longitudinal axis direction

R

Radial direction

G

Gearbox center axis

a

Rolling movement

b

Twisting

QUOTES INCLUDED IN THE DESCRIPTION

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

Cited patent literature

• DE 102020119832 A1 [0003]
• US 20130202232 A1 [0004]
• EP2516883 [0007, 0028]

Claims (15)

Elastomer 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 support, of a wind turbine, comprising a bearing device (9) which decouples the drive train component and the support structure from one another and which in particular comprises two half shells (5, 7), wherein the bearing device (9) is designed to roll on the drive train component and/or the support structure. Elastomer bushing (3) after Claim 1 , wherein the bearing device (9) is designed as a rolling bearing. Elastomer bushing (3) after Claim 2 , wherein the rolling bearing comprises at least one in particular elastically deformable, preferably twistable, rolling body (47), in particular made of an elastomer material. Elastomer bushing (3) according to one of the preceding claims, wherein the bearing device, in particular the rolling body (47) of the rolling bearing, is further configured to twist at least in sections when rolling on the drive train component and/or the support structure and/or to build up a restoring force oriented counter to the rolling movement. 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 body (47) with a particularly semi-annular rolling section (63) and a base (59), wherein the rolling body (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). Elastomer bushing (3) according to one of the Claims 2 until 5 , wherein the rolling bearing comprises at least one in particular elastically deformable rolling body (47) with a in particular embedded strength carrier (57), for example made of plastic, such as polyamide, glass fiber, carbon fiber, or metal. 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 next to one another in the longitudinal axis direction, which are arranged and/or coordinated with one another in such a way that when the elastomer bushing (3) is loaded in the radial direction above a limit load, in particular of greater than 1500 kN, in particular of greater than 1600 kN, 1700 kN or of greater than 1800 kN, the at least two rolling elements (47) are pressed against one another to suddenly increase the radial rigidity in the longitudinal axis direction. Elastomer bushing (3) according to one of the Claims 5 until 7 , wherein the rolling bearing further comprises a base (59) which holds the rolling elements (47) and remains substantially undeformed when the elastomer bushing (3) is loaded in the radial direction. Elastomer bushing (3) according to one of the preceding claims, wherein the elastomer bushing (3) has an axial stiffness in the longitudinal axis direction in the range from 4 kN/mm to 14 kN/mm, in particular in the range from 5 kN/mm to 13 kN/mm or in the range from 5 kN/mm to 12 kN/mm, and/or wherein the radial stiffness has a sudden increase when the elastomer bushing (3) is loaded in the radial direction above a limit load, in particular of greater than 1,500 kN, in particular of greater than 1,600 kN, of greater than 1,700 kN or of greater than 1,800 kN. 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 has at least one contact projection (69, 71) extending in the direction of the longitudinal axis of the half-shell, such as a contact web, 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 one another in the circumferential direction such that the bearing device (9) rests against both contact projections. Elastomer bushing (3) according to one of the preceding claims, wherein the bearing device (9) comprises two half-shells (5, 7) and two circumferential ends of the half-shells (5, 7) facing one another are designed to form a tongue and groove and/or dovetail connection with two bearing block parts on the wind turbine side, in particular on the machine support side, for receiving the elastomer bushing (3) in a particularly clamping or floating manner. Elastomer bushing (3) after 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. Elastic bearing (1), in particular decoupling bearing, for supporting a drive train component, in particular a gearbox, of a wind turbine, in particular on its supporting structure, such as a machine carrier, comprising an elastomer bushing (3) designed according to one of the preceding claims and two bearing block parts for receiving the elastomer bushing, in particular in a clamping or floating manner. Elastic bearing (1) according to Claim 13 , wherein the bearing block parts have mutually facing, in particular identically formed grooves and radial projections are formed on two mutually facing circumferential ends of the half-shells (5, 7), wherein the grooves and the radial projections are coordinated with one another in terms of shape, wherein in particular the radial projections are shaped to engage behind the grooves in the radial direction, in particular are formed in the manner of a tongue and groove and/or dovetail connection. Elastic bearing (1) according to Claim 13 or 14 , further comprising a bearing pin supported by the elastomer bushing (3) and provided with a device for supporting the bearing device (9) in the longitudinal axis direction under a predetermined load condition, in particular under a predetermined radial load on the elastomer bushing, wherein in particular the bearing pin has a radial projection which is arranged in relation to the bearing device (9) such that under the predetermined load condition the bearing device (9) is pressed against the radial projection.

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