CN118103609A - Main bearing arrangement for a wind energy plant - Google Patents

Abstract

The invention relates to a main bearing arrangement for supporting a rotatable rotor (1) of a wind energy plant, wherein the rotor (1) is rotatably supported relative to a coupling structure via at least one rolling bearing (2), wherein the rolling bearing (2) has an outer ring (3) which is connected by means of a press fit to an annular receptacle (A) of the coupling structure by means of its radial outer circumferential surface (4), wherein the outer ring (3) has at least one first positive-locking element (7) at least one axial end face (6), wherein a counter element (8) which is non-rotatably connected to the coupling structure and has at least one second positive-locking element (9) is provided, and wherein a positive-locking connection (10) which acts in the circumferential direction of the outer ring (3) is formed between the first positive-locking element (7) and the second positive-locking element (9). In order to provide a main bearing arrangement in which damage due to a ring displacement of a rolling bearing outer ring arranged in an annular receptacle of a coupling structure by means of a press fit is avoided and which is flexible to use, it is proposed that at least one first form-fitting element (7) is configured as a projection (15) projecting in an axial direction relative to an end face (6) of the outer ring (3) and at least one second form-fitting element (9) is configured as a recess (16) retracting in an axial direction relative to an end face (14) of the component (11) or the flange (12), or that at least one first form-fitting element (7) is configured as a recess (17) retracting in an axial direction relative to an end face (6) of the outer ring (3) and that at least one second form-fitting element (9) is configured as a projection (18) projecting in an axial direction relative to an end face (14) of the component (11) or the flange (12), wherein the projections (15; 18) engage into the recess (16; 17) with form-fitting connection (10) acting in a circumferential direction.

Description

Main bearing arrangement for a wind energy plant

Technical Field

The invention relates to a main bearing arrangement for a wind energy plant. The rotor of a wind power plant (i.e. for example a rotor shaft, which connects the rotor hub of the wind power plant to a gear train or directly to a generator for generating electrical current) is supported by means of a main bearing.

Background

Document EP 2 947 b 339 discloses that in the case of a known main bearing device for supporting a rotatable rotor of a wind energy installation, the rotor is rotatably supported relative to a rotationally fixed coupling of the wind energy installation via at least one rolling bearing, wherein the rolling bearing has an inner ring, the radial inner circumferential surface of which is connected to the outer surface of the rotor by a press fit.

EP 2 947 339 B1 addresses the problem of so-called ring movements, which are important problems in particular in large bearings which serve as main bearings for the rotor/rotor shaft of a wind energy plant and have diameters which are several meters large. The problem of ring movements in the main bearing of a wind energy installation and the measures known from the prior art for preventing ring movements are described in detail in EP 2 947 339 B1 as follows:

the use of increasingly large rolling bearings, in particular reliable bearing blocks, has proven problematic. The main bearing of the rotor of a wind energy plant is usually positioned or fixed by means of a so-called press fit, i.e. the bearing rings of the rolling bearing, i.e. the inner ring and the outer ring, are pressed into corresponding annular receptacles on the rotor or on the coupling. In this case, a force-fitting connection (also referred to as a "press connection") is produced by means of a pair of interference fits.

When the bearing diameter is large, a very disadvantageous ratio of diameter/ring cross section is produced, so that sufficient force (connecting pressure) for a strong bearing seat can no longer be ensured. Further increases in the interference fit only result in a slight increase in the connection pressure, since the thin-walled bearing rings expand more easily, while the more solid rotor or the more solid coupling structure contracts only slightly. The excessively strong expansion of the bearing ring in turn leads to high tensile or compressive stresses in the bearing ring, which can lead to adverse effects on the raceway geometry due to shape deviations of the bearing ring. In addition, in many bearing designs, the bearing play, i.e. the positive bearing play, is thereby also changed, which can directly have a negative effect on the service life and the operational stability of the bearing.

The thus insufficient press fit between the bearing ring and the rotor/coupling structure conceals the risk of fretting corrosion and ring movement, which leads to failure of the rolling bearing arrangement and/or the rotor (rotor shaft) or the coupling structure (also referred to as the "housing" of the wind energy plant nacelle). The damage mechanism usually starts with a small relative movement in the bearing housing between the bearing housing and the bearing ring, which is made possible by too little stress or force (connection pressure). Thereby causing the mating surfaces to slidingly rotate (circumferentially) and move (axially) relative to each other. As a result, the edge layer particles are mostly sheared by the softer components, thereby creating holes and scaly material particles. This mechanism of wear is known as adhesive wear. This process is superimposed and accelerated by oxidation in the mating connection. Due to the relative movement, water, oxygen and other media can reach into the contact area, which in turn leads to chemical reactions, which in combination with the movement of the component are called tribo-oxidation.

In this damage progression, the softer parts in the wear chain are often fatigued, which is usually the shaft or the housing/coupling structure. Typically, a large area of material shedding occurs first under the bearing and finally a shaft breakage occurs directly at the bearing seat due to notch stress concentration effects and high forces. This problem is exacerbated by the lightweight construction required in wind power. Due to limited overhead mass, high required transportation and expensive crane capacity, attempts are made to design the mechanical structure lighter. The machine support, the shaft and the housing are therefore not (any more) regarded as highly rigid structural components. In basic design, however, rolling bearing manufacturers require a very rigid environment for each rolling bearing. The structural components of modern wind power installations deform under high wind loads so severely that the rolling bearing housing is also subjected to large-area deformations. These global deformations also contribute to the development of tribological and adhesive wear problems.

As the bearing size increases, the tolerance of the bearing housing surface increases also problematic. The fit for a bearing ring with a diameter of 2.5m has a very high tolerance range. In combination with the equally high tolerance ranges for the bearing seats on the shaft or housing, high fluctuations in the press fit result. If these high tolerances disadvantageously coincide, only a very small proportion of the connecting pressure remains in the press fit. Thus, such press-fitting is particularly susceptible to relative movement that causes fretting corrosion and adhesive wear. This also accounts for the different failure rates in the event of damage due to fretting corrosion and wear in the press connection.

In particular for the main bearings of wind energy installations, no adequate technical solution exists for this problem. Special plastic coatings such as PTFE (polytetrafluoroethylene) on the bearing ring and/or on the shaft or on the bearing seat on the housing can slightly reduce the problems of chemical reactions between the two metallic mating bearings. However, the problem of low connection pressure cannot be eliminated with such a coating. Hard coatings such as DLC (diamond like carbon) or hard chrome coatings for bearing rings and/or shafts or housings can reduce adhesive wear, however there are still problems with chemical reactions and thus with tribo-corrosion. Because these two alternatives reduce only one of the two wear mechanisms and are furthermore associated with very high costs, they are not used in the main bearing arrangement.

Instead, single bearing solutions have been used in the past few years with an outer ring of a screwed main bearing arrangement and later also an inner ring. However, the focus here is not a press connection, but rather a pre-adjustable bearing arrangement is provided.

However, the threaded connection of the bearing rings has a number of disadvantages as known. This includes high ring cross-section (weight and cost), limited screw connection rigidity, and difficult assembly of such rolling bearing systems.

In order to reduce or even suppress the problems described with respect to fretting corrosion, adhesive wear and ring movement, EP 2 947 339 B1 suggests that the rolling bodies of the main bearing are supported directly on the rotor shaft or housing/coupling structure without separate bearing rings, which are integral parts of the rotor shaft or housing/coupling structure. However, this measure has several serious drawbacks. On the one hand, the rolling body raceways integrated in the rotor shaft or the housing have to be hardened in order to be able to achieve the required service life of the main bearing. However, this is technically very difficult, complex and expensive in the case of raceways formed integrally with the rotor shaft and the housing component, since, for example, only the integral raceways have to be heated and quenched selectively for hardening over the entire rotor shaft, in which case, however, the entire rotor shaft has to be handled. On the other hand, in the event of a bearing failure, the bearing or the individual bearing rings cannot be replaced, but rather the entire component with the integrated rolling element raceways needs to be replaced, which results in a far greater outlay and a far greater cost.

In DE 10 2017 109 148 A1, an anti-rotation device for a rolling bearing is described, which serves to prevent a ring from moving and at the same time to achieve a desired bearing preload in the housing shaft device. The shaft is rotatably supported relative to the housing by a rolling bearing. The inner ring of the rolling bearing is connected to the shaft in a rotationally fixed manner. The outer ring of the rolling bearing is preloaded in the axial direction relative to the housing by the fixing element and is prevented from rotating. The fixing element is configured as a wave spring. The wave spring engages with a first spring bending region protruding in the axial direction into at least one recess of the outer ring of the rolling bearing. At the same time, the wave spring has at least one second spring bending region which engages into a recess of the housing-fixed component.

The anti-rotation device described in DE 10 2017 109 148 A1 appears to be provided for use in smaller housing-shaft devices, for example in motor vehicles. The anti-rotation device is not suitable for use in the main bearing arrangement of a wind energy plant, because for this purpose very large wave springs with a diameter of several meters are required. Such additional fixation elements will substantially increase the total weight of the main bearing arrangement. The installation of such wave springs is very difficult and expensive. Furthermore, by the method according to DE 10 2017

109 148A1, it is not possible to apply the required large forces in order to axially pretension the large rolling bearings of the main bearing arrangement of the wind energy plant.

DE 10 2021 203 603 A1 describes a transmission device (101) for a wind power installation, comprising a housing part (103), a bearing (105), a shaft (107), a counter element (113) and a cover (111). The shaft (107) is rotatably supported in the housing part (103) by means of a bearing (105). The cover (111) is fixed at least in a rotationally fixed manner in the housing part (103) and covers at least partially a gap running between the housing part (103) and the shaft (107). The mating element (113) engages in a form-fitting manner into a ring (105 a) of the bearing (105) and into the cover (111). A disadvantage of this solution is that a housing part, a cover connected to the housing part, and a separate mating element are required in order to achieve the described solution. Thus, assembly of the transmission device is costly. Furthermore, this solution is applicable only in wind power installations with a gear mechanism, but not in installations without a gear mechanism.

Disclosure of Invention

The object of the present invention is to provide a main bearing arrangement for rotatably supporting a rotor of a wind energy plant, wherein the above-mentioned damage and disadvantages are avoided. In particular, damage occurring as a result of a ring displacement of the outer ring of the rolling bearing, which is arranged in the annular receptacle of the coupling structure by means of a press fit, should be avoided. Furthermore, the main bearing arrangement should be able to be used not only in gearless wind energy installations, but also in wind energy installations with gearings.

This object is achieved by a main bearing arrangement having the features specified in the independent claims. Advantageous refinements emerge from the dependent claims, the following description and the figures.

The invention relates to a main bearing arrangement for supporting a rotatable rotor of a wind energy plant, wherein the rotor is rotatably supported relative to a coupling structure by means of at least one rolling bearing, wherein the rolling bearing has an outer ring which is connected by means of a press fit to an annular receptacle of the coupling structure by means of its radial outer circumferential surface, wherein the outer ring has at least one first positive-locking element at least one axial end face, wherein a counter element which is non-rotatably connected to the coupling structure is provided and has at least one second positive-locking element, and wherein a positive-locking connection which acts in the circumferential direction of the outer ring is formed between the first and second positive-locking elements. .

According to the invention, the at least one first positive-locking element is configured as a projection projecting in the axial direction relative to the end face of the outer ring and the at least one second positive-locking element is configured as a recess which is retracted in the axial direction relative to the end face of the component or flange, or the at least one first positive-locking element is configured as a recess which is retracted in the axial direction relative to the end face of the outer ring and the at least one second positive-locking element is configured as a projection projecting in the axial direction relative to the end face of the component or flange, wherein the projection engages into the recess with a positive-locking connection which is configured to act in the circumferential direction. .

The mating element can be formed by a radial flange formed on the coupling structure. Alternatively, the ring which is connected to the coupling structure in a rotationally fixed manner can also form a mating element. Such a ring can be connected to the coupling structure in a rotationally fixed manner in different ways, for example by means of a screw connection, by welding, adhesive bonding or soldering, etc.

By the solution according to the invention, the advantage is achieved that the axial end faces (grooves and noses) do not need to be produced with high precision. The increase in the bearing capacity and rigidity of the circumferential side of the connection is achieved by the sedimentation of the positive-locking connection between the bearing ring and the counter element, which occurs on the circumferential side during operation of the bearing, and the consequent increase in the bearing circumferential side area of the connection. With each sedimentation phenomenon, the relative movement of the bearing ring and the circumferential side of the coupling structure becomes smaller and eventually stops. The sedimentation phenomenon is generated by forces occurring between the outer ring and the counter element, which forces act in the circumferential direction. The at least one positive-locking element can be said to be embedded in the component that participates in the positive-locking connection. Thus eventually preventing the ring from moving and slipping completely.

By means of the invention, the damage caused by the movement of the ring described above is reliably prevented.

The form-fitting connection embodied in the manner according to the invention has form-fitting elements which are embodied integrally with the respective component (outer ring or counter element). Thus, no separate connecting element, which is configured separately from the outer ring or the counter element, is required to form a form fit. Thereby minimizing the number of components required. Assembly costs are also relatively small.

The solution according to the invention can be used very flexibly. It can be used not only in gearless wind power installations, but also in wind power installations with gearings. In gearless wind energy installations, the coupling structure can be, for example, a nacelle of the wind energy installation or a part of a nacelle of the wind energy installation.

An embodiment of the main bearing arrangement according to the invention provides that a plurality of first and second form-fitting elements are arranged distributed in the circumferential direction, wherein preferably the circumferential portions between adjacent form-fitting elements are of equal length. As a result, there is a large surface area available for the form-fitting connection in the circumferential direction as a whole. Thus, each individual positive connection is only subjected to a relatively small face pressure. The service life of a bearing arrangement having a plurality of form-fitting connections can be significantly increased compared to an embodiment having only a single form-fitting connection. If the individual positive-locking connections are arranged uniformly distributed in the circumferential direction, that is to say if the circumferential part lengths between adjacent positive-locking connections are identical, the force in the circumferential direction is introduced very uniformly from the outer ring into the counter element and undesired deformation of the outer ring due to the circumferential force introduced unevenly into the counter element is avoided.

According to one embodiment of the main bearing arrangement according to the invention, it is provided that the counter element is a component which is connected to the coupling structure in a rotationally fixed manner or is a flange which is formed integrally on the coupling structure, wherein the at least one second positive-locking element is formed on an axial end face of the component or of the flange, which axial end face faces the axial end face of the outer ring having the at least one first positive-locking element. By arranging the form-fitting elements on the end faces of the respective structural elements, the form-fitting elements can be configured such that they have a large length in the radial direction. In this way, a large force transmission surface in the circumferential direction is provided, which in turn contributes to a relatively small surface pressure in the sole form-fitting connection or in the individual form-fitting connections. The form-fitting element arranged on the end face of the component can also be produced in a simple manner in terms of production technology, which contributes to low production costs.

In order to also resist ring movements in the axial direction of the coupling structure and to inhibit such axial ring movements, an embodiment of the main bearing arrangement according to the invention is arranged such that the outer ring is coupled by at least one detachable connection, e.g. a bolt, preventing relative movement in the axial direction with respect to the coupling structure. The detachable connection may be configured, for example, between the outer ring and the counter element. The detachable connection may be arranged between the first and second form-fitting element, for example in the circumferential region. One or more detachable connections may be provided.

According to one embodiment of the main bearing arrangement according to the invention, the outer ring is a bearing ring made of hardened and tempered steel, which has one or more induction-hardened rolling-element raceways. In this embodiment, the first positive-locking element can be introduced into the outer ring simply and without great effort in terms of manufacturing technology, since the outer ring region which does not belong to the surface-hardened raceway region is not hardened and can therefore be easily machined, for example cut, to introduce the first positive-locking element. In principle, the invention can also be implemented on fully hardened or carburized outer rings, which are made of the material 100Cr6 or carburized steel, for example, but the subsequent introduction of form-fitting elements into the hardened outer ring is considerably more complicated.

According to one embodiment of the main bearing arrangement according to the invention, it is provided that the rolling bearing is provided for absorbing forces acting in the axial direction during operation of the bearing, wherein the outer ring is pressed in the direction of the counter element by forces acting in the axial direction on the outer ring such that the at least one first positive-locking element is pressed in the direction of the at least one second positive-locking element. The advantage achieved thereby is that the force flow through the rolling bearing supports a positive-locking connection. The outer ring is always pressed against the counter element by the axial forces acting on it during operation of the rolling bearing, i.e. always in the direction of the positive-locking connection. Thereby, the form fit is not lost even when no mechanical safety measures are taken to avoid the loss of the form fit. The forces acting on the rolling bearing during operation thus ensure in this embodiment a positive fit acting in the circumferential direction between the outer ring and the counter element. According to one embodiment of the main bearing arrangement according to the invention, the rolling bearing may be configured as a combined (ANGESTEL LT) tapered roller bearing.

According to one embodiment of the main bearing arrangement according to the invention, the inner ring of the rolling bearing has at least one third positive-locking element on at least one axial end face, wherein a second counter element is provided which is connected to the rotor in a rotationally fixed manner and has at least one fourth positive-locking element, and wherein a positive-locking connection which acts in the circumferential direction of the inner ring is formed between the third and fourth positive-locking elements. In this embodiment, therefore, a positive connection acting in the circumferential direction is provided on both the outer ring and the inner ring of the rolling bearing, by means of which positive connection the ring movement of the outer ring and the inner ring is effectively prevented. According to the invention, the damage mechanism described at the beginning, which can occur by a ring movement, is prevented for both bearing rings in this way.

Drawings

The invention is explained in detail below with the aid of the drawing. Which are respectively schematically shown:

fig. 1: according to the outer race with the first positive-fit element of the first embodiment of the present invention,

Fig. 2: one embodiment of the invention has a rolling bearing outer ring fitted in an annular receptacle of the coupling,

Fig. 3: in one embodiment of the invention, not only the outer ring but also the inner ring of the rolling bearing is fixed in the circumferential direction, in order to prevent the ring from moving,

Fig. 4: according to one embodiment of the form-fitting connection of the invention,

Fig. 5: alternative to the embodiment of fig. 4, a form-fitting connection according to the invention.

Detailed Description

Fig. 1 shows an outer ring 3 of a large rolling bearing in a three-dimensional view. The remaining components of the rolling bearing 2, i.e. in particular the inner ring and the rolling bodies arranged between the outer ring 3 and the inner ring, are not shown in fig. 1.

The outer ring 3 has an axial end face 6 and a radial outer circumferential face 4. Furthermore, the outer ring 3 has a first positive-locking element 7, which first positive-locking element 7 protrudes relative to the axial end face 6. The outer ring 3 is accommodated in the annular accommodation a in the assembled state with its radially outer circumferential surface 4 by means of a press fit (see fig. 2). The receptacle a, which is not shown in fig. 1, is fixedly connected to the coupling structure.

Fig. 2 shows an embodiment of the invention with an outer ring 3 which is accommodated in an annular receptacle a in a rotationally fixed manner via a press fit. The receptacle a is connected in a rotationally fixed manner to a coupling structure, not shown. The receptacle a has a counter element 8, which in the exemplary embodiment shown is designed as a flange 12. The flange 12 is in the embodiment shown an integral, unitary component of the receptacle a.

The outer ring 3 has an axial end face 6 which faces a counter element 8. The counter element 8 or the flange 12 has an axial end face 14 facing the end face 6. On the axial end face 6 of the outer ring 3, a first positive-locking element 7 is formed, which forms a positive-locking connection 10 with a second positive-locking element 9 formed on the end face 14 of the counter element 8, which positive-locking connection acts in the circumferential direction.

The axial forces occurring during bearing operation support the positive fit of the positive fit connection 10. The rolling bearing 2 is provided for absorbing forces acting in the axial direction during operation of the bearing. The force 25 exerted by the rolling bodies 23 on the outer ring 3 has a force component 26 acting in the axial direction, by means of which the outer ring 3 is pressed in the direction of the counter element 8. Thereby, the end face 6 of the outer ring 3 is pressed against the end face 14 of the flange 12 by a force acting on the outer ring 3 when the main bearing arrangement is in operation. This is indicated in fig. 2 by arrow 27 showing the reaction force. The form-fitting elements 7, 9 can in this way not lose their form-fitting engagement. The forces occurring during operation and acting on the outer ring 3 are prevented in this way, the connection partners of the positive-locking connection 10 are moved away from one another in the axial direction and the positive-locking is eliminated, without a separate prestressing force having to be applied for this purpose. In particular, no separate pretensioning element is required, by means of which the outer ring 3 is pretensioned onto the flange 12.

Fig. 3 shows an embodiment of the invention in which not only the outer ring 3 but also the inner ring 22 of the rolling bearing 2 are prevented from ring movement in the circumferential direction. The inner ring 22 has a plurality of third positive locking elements 29 distributed in the circumferential direction on at least its axial end face 28. The second counter element 30, which is connected to the rotor 1 in a rotationally fixed manner, has a plurality of fourth positive-locking elements 31 distributed in the circumferential direction. A positive-locking connection 32, which acts in the circumferential direction of the outer ring 22, is formed between the third positive-locking element 29 and the fourth positive-locking element 31.

The forces occurring during operation and acting on the inner ring 22 support the positive fit of the positive fit connection 32. The rolling bearing 2 is provided for absorbing forces acting in the axial direction during operation of the bearing. The force 33 exerted by the rolling bodies 23 on the inner ring 22 has a force component 34 acting in the axial direction, by means of which force component 34 the outer ring 22 is pressed in the direction of the second counter element 30. Thus, during operation of the main bearing arrangement, the end face 28 of the inner ring 22 is pressed against the end face 35 of the second counter element 30 facing the end face 28 by a force acting on the inner ring 22. This is indicated in fig. 3 by arrow 36. The form-fitting elements 29, 31 can in this way not lose their form-fitting engagement. The forces occurring during operation and acting on the inner ring 22 prevent the connection partners of the positive-locking connection 32 from being moved away from one another in the axial direction and the positive-locking is lost, without a separate prestressing force having to be applied for this purpose. In particular, no separate pretensioning element is required, by means of which the inner ring 22 is pretensioned onto the second mating element 30.

In the exemplary embodiment shown in fig. 3, the second mating element 30 is embodied as a flange 38 embodied integrally with the rotor 1.

The outer ring 3 and the housing a housing the outer ring 3 are implemented similarly to the embodiment shown in fig. 2 in the embodiment shown in fig. 3. The receptacle a is configured, like the embodiment shown in fig. 2, as an annular component which is connected in a rotationally fixed manner to an element of the coupling structure, which is not shown in fig. 3. The coupling structure may be, for example, a component of the housing of the nacelle of the wind power plant.

It goes without saying that all form-fitting elements 7, 9, 29, 31 can be embodied as projections and/or recesses within the scope of the conceivable embodiment of the invention.

Fig. 4 shows an embodiment of the invention in which the first form-fitting element 7 on the outer ring 3 is designed as a recess and the second form-fitting element 9 on the counter element 8/flange 12 is designed as a projection. The positive-fit connection is established by engaging the male part into the female part.

Fig. 5 shows an embodiment of the invention, in which the first form-fitting element 7 on the outer ring 3 is configured as a male part and the second form-fitting element 9 on the counter element 8/flange 12 is configured as a female part. The positive-fit connection is established by engaging the male part into the female part.

Description of the reference numerals

1 Rotor

2 Rolling bearing

3 Outer ring

4 Outer peripheral surface

5 Shell noodles

6 End face

7 Form-fitting element

8 Mating element

9 Form-fitting element

10 Form-fitting connection

11 Component

12 Flange

14 End face

15 Convex portions

16 Concave parts

17 Recess portion

18 Convex portions

19 Recess portion

20 Concave part

22 Outer ring

23 Rolling element

24 Holder

25 Force

26 Force component

27 Arrow

28 End face

29 Form-fitting element

30 Mating element

31 Form-fitting element

32 Form-fit connection

33 Force

34 Force component

35 End face

36 Arrow

37 Component

38 Flange

Claims (8)

1. A main bearing arrangement for supporting a rotatable rotor (1) of a wind energy plant, wherein the rotor (1) is rotatably supported relative to a coupling structure by means of at least one rolling bearing (2), wherein the rolling bearing (2) has an outer ring (3) which is connected by means of a press fit by its radial outer circumferential surface (4) to an annular receptacle (A) of the coupling structure, wherein the outer ring (3) has at least one first form-fitting element (7) at least one axial end face (6), wherein a counter element (8) which is non-rotatably connected to the coupling structure and has at least one second form-fitting element (9) is provided, and wherein a form-fitting connection (10) which acts in the circumferential direction of the outer ring (3) is formed between the first form-fitting element (7) and the second form-fitting element (9),

It is characterized in that the method comprises the steps of,

The at least one first positive-locking element (7) is configured as a projection (15) projecting in the axial direction relative to the end face (6) of the outer ring (3), and the at least one second positive-locking element (9) is configured as a recess (16) that is retracted in the axial direction relative to the end face (14) of the component (11) or the flange (12), or the at least one first positive-locking element (7) is configured as a recess (17) that is retracted in the axial direction relative to the end face (6) of the outer ring (3), and the at least one second positive-locking element (9) is configured as a projection (18) projecting in the axial direction relative to the end face (14) of the component (11) or the flange (12), wherein the projections (15; 18) engage into the recesses (16; 17) with the positive-locking connection (10) that is configured to function in the circumferential direction.

2. The main bearing arrangement of claim 1,

It is characterized in that the method comprises the steps of,

A plurality of first and second form-fitting elements (7, 9) are arranged distributed in the circumferential direction, wherein preferably the circumferential portions between adjacent form-fitting elements (7, 9) are of equal length.

3. The main bearing arrangement according to claim 1 or 2,

It is characterized in that the method comprises the steps of,

The counter element (8) is a component (11) which is connected to the coupling structure in a rotationally fixed manner or is a flange (12) which is formed integrally on the coupling structure, wherein the at least one second positive-locking element (9) is formed on an axial end face (14) of the component (11) or the flange (12), which axial end face (14) faces the axial end face (6) of the outer ring (3) having the at least one first positive-locking element (7).

4. The main bearing arrangement according to any of the preceding claims,

It is characterized in that the method comprises the steps of,

The outer ring (3) is prevented from relative movement with respect to the coupling structure in the axial direction by at least one detachable connection, for example a threaded connection.

5. The main bearing arrangement according to any of the preceding claims,

It is characterized in that the method comprises the steps of,

The outer ring (3) is a bearing ring made of hardened and tempered steel, having one or more induction-hardened rolling element raceways.

6. The main bearing arrangement according to any of the preceding claims,

It is characterized in that the method comprises the steps of,

The rolling bearing (2) is provided for receiving forces acting in the axial direction during operation of the bearing, wherein the outer ring (3) is pushed in the direction of the counter element (8) by forces acting in the axial direction on the outer ring in such a way that the at least one first positive-locking element (7) is pushed in the direction of the at least one second positive-locking element (9).

7. The main bearing assembly of claim 6,

It is characterized in that the method comprises the steps of,

The rolling bearing (2) is designed as a combined tapered roller bearing.

8. The main bearing arrangement according to any of the preceding claims,

It is characterized in that the method comprises the steps of,

The inner ring (22) of the rolling bearing (2) has at least one third positive-locking element (29) on at least one axial end face (28), wherein a second counter element (30) which is non-rotatably connected to the rotor (1) is provided, said second counter element having at least one fourth positive-locking element (31), and wherein a positive-locking connection (32) which acts in the circumferential direction of the inner ring (22) is formed between the third positive-locking element (29) and the fourth positive-locking element (31).