WO2010112229A1

WO2010112229A1 - Bearing assembly for rotatably supporting a machine element and method for fixing a tapered roller bearing to a machine element

Info

Publication number: WO2010112229A1
Application number: PCT/EP2010/002102
Authority: WO
Inventors: Hans-Jürgen Liesegang; Mathias Seuberling
Original assignee: Ab Skf
Priority date: 2009-04-01
Filing date: 2010-04-01
Publication date: 2010-10-07
Also published as: CN102449331A; DE102009015827B4; DE102009015827A1; CN102449331B; EP2414692A1

Abstract

The invention relates to a bearing assembly, having a two-rowed tapered roller bearing (1) for rotatably supporting a machine element (3) and having a clamping device (2) for fixing the tapered roller bearing (1) to the machine element (3). The tapered roller bearing (1) has an outer ring (5), the outer diameter of which is at least 1 meter, a first inner ring (7), a second inner ring (9), which is axially disposed next to the first inner ring (7), a set of conically designed first rolling elements (11), which roll between the outer ring (5) and the first inner ring (7), and a set of conically designed second rolling elements (12), which are axially disposed next to the first rolling elements (11) and which roll between the outer ring (5) and the second inner ring (9). The clamping device (2) has a rigid component (18) and an elastically deformable component (19, 23). The rigid component (18) of the clamping device (2) axially stops at the machine element (3). The elastically deformable component (19, 23) of the clamping device (2) is axially clamped and thus axially deformed compared to a relaxed state. The elastically deformable component (19, 23) of the clamping device (2) is connected to the first inner ring (7) of the tapered roller bearing (1), to the second inner ring (9) of the tapered roller bearing (1), to the rigid component (18) of the clamping device (2), or to the machine element (3).

Description

Bearing arrangement for the rotatable mounting of a machine part and method for fixing a tapered roller bearing on a machine part

The invention relates to a bearing assembly with a designed as a double-row tapered roller bearings large warehouse for rotatably supporting a machine part and with a clamping device for fixing the tapered roller bearing on the machine part. Furthermore, the invention relates to a wind turbine with such a bearing assembly and a method for fixing a tapered roller bearing on a machine part.

As a large bearing are referred to below bearing having an outer ring with a diameter of at least one meter. Other criteria and, in particular, other diameter values may also be used for the definition of large bearings. In any case, it is crucial that they are bearings that are significantly larger than those that are commonly used in everyday applications, such as cars, and have an outside diameter of a few centimeters.

In the construction of a large warehouse, a pure upscaling of the bearing geometry starting from a known "small" bearing usually makes no sense, as in large bearings often other criteria such as weight, the material required for the production, the installation effort, repair options, etc to come to the fore.

It is already known to fix a large warehouse by an axial bracing on a shaft. For this purpose, the large warehouse is supported on one axial side in a lenschulter. On the opposite side, a clamping ring is pressed axially against the large bearing, so that the large bearing is clamped axially between the shaft shoulder and the clamping ring. Since the axial tension of a large-scale bearing designed, for example, as a tapered roller bearing can influence the internal play or the internal prestressing of the large bearing, a precise adjustment of the axial forces acting on the large bearing is sometimes very important. In this context, it is known, for example, to compensate for tolerances to arrange an individually adapted intermediate ring axially between the large warehouse and the clamping ring. However, the individual production of the intermediate ring or the selection of a matching intermediate ring from an assortment of intermediate rings requires additional effort.

The invention has for its object to enable a mounting of a bearing assembly having a designed as a tapered roller bearing large stock, with a defined bias with little effort.

This object is achieved by a bearing arrangement with the feature combination of claim 1 and a method for fixing a tapered roller bearing according to claim 13.

The bearing assembly according to the invention comprises a double-row tapered roller bearing for rotatably supporting a machine part and a clamping device for fixing the KegehOllenlagers on the machine part. The tapered roller bearing has an outer ring whose outer diameter is at least 1 meter, a first inner ring, a second inner ring disposed axially adjacent to the first inner ring, a set of conically shaped first rolling elements rolling between the outer ring and the first inner ring and a set of conically shaped second rolling elements, which are arranged axially adjacent to the first Wälzkörpem and roll between the outer ring and the second inner ring, on. The tensioning device has a rigid component and an elastically deformable component. The rigid component of the clamping device strikes axially on Machine part on. The elastically deformable component of the tensioning device is axially clamped and thereby axially deformed relative to a relaxed state. The elastically deformable component of the tensioning device is connected to the first inner ring of the tapered roller bearing with the second inner ring of the tapered roller bearing, with the rigid component of the clamping device or with the machine part.

The invention has the advantage that it is ensured with relatively little effort that the axial preload of the tapered roller bearing is within a predetermined range. By using the elastically deformable component dimensional tolerances can be compensated for the components used. If the permitted dimensional tolerances are complied with for the components used, it is ensured that the axial preload of the tapered roller bearing is within the specified range. Individual adjustment or adjustment measures are not required. By connecting the elastically deformable component with an already existing component is also achieved that the number of components to be handled during assembly of the bearing assembly does not increase and accordingly the assembly can be performed quickly and efficiently.

The bearing assembly according to the invention may in particular be designed so that the first inner ring abuts axially on the machine part or in cooperation with the machine part axially clamps the elastically deformable component of the clamping device and the second inner ring abuts axially against the rigid component of the clamping device or in cooperation with the rigid component the clamping device axially clamps the elastically deformable component of the clamping device

The elastically deformable component of the clamping device can cohesively, in particular by vulcanization, with the first inner ring of the tapered roller bearing, with the second inner ring of the tapered roller bearing with the rigid component of Clamping device or is connected to the machine part. Such a compound can be produced with little effort and has sufficient strength.

Likewise, there is also the possibility that the elastically deformable component of the tensioning device is formed integrally with the first inner ring of the tapered roller bearing, with the second inner ring of the tapered roller bearing, with the rigid component of the tensioning device or with the machine part and is in particular made of the same material as the The first inner ring of the tapered roller bearing, the second inner ring of the tapered roller bearing, the rigid component of the clamping device or the machine part. This embodiment represents a particularly cost-effective implementation form with a long service life.

In particular, the elastically deformable component of the tensioning device may have a reduced material thickness compared to the rigid component. As a result, a lighter deformability is achieved in a very simple manner. For example, the elastically deformable component of the tensioning device may be formed as a flange-like extension of the rigid component.

The rigid component and / or the elastically deformable component of

Clamping device is designed as a circumferentially closed ring. As a result, the number of individual components can be kept low. Likewise, however, it is also possible for the rigid component and / or the elastically deformable component of the tensioning device to be segmented in the circumferential direction. As a result, the handling can be facilitated, especially in the case of very large bearing arrangements, and the installation effort can be reduced if accessibility is poor.

The elastically deformable component of the clamping device, for example, made of spring steel or plastic, in particular made of elastomeric material be. These materials are available inexpensively and elastically deformable over a sufficient deformation path.

The machine part can be designed, for example, as a shaft connection part or a shaft

In a preferred embodiment, the bearing assembly is formed as a component of a wind turbine. In wind turbines bearing arrangements are used with very large dimensions and it is a short assembly time desired. In particular, in off-shore systems, the assembly time can even be of paramount importance, since an assembly is possible only in favorable weather conditions.

The invention further relates to a wind energy plant with a rotor which is fastened to a rotor shaft which is rotatably mounted in a bearing arrangement according to the invention.

In addition, the invention relates to a method for fixing a tapered roller bearing, which has an outer diameter of at least 1 meter, by means of a clamping device comprising a rigid component and an elastically deformable

Component has, on a machine part. In the method according to the invention, the rigid component of the clamping device is axially approximated to the machine part until it abuts the machine part. In this case, the elastically deformable component of the tensioning device, which is connected to the tapered roller bearing, the rigid component of the tensioning device or the machine part, axially deformed about a deformation path which is so large that the tapered roller bearing with an axial force which is a value between a predetermined Minimum value and a predetermined maximum value, is clamped axially between the rigid component of the clamping device and the machine part or a machine connected to the machine part fastening element. Since the rigid component of the tensioning device is approached axially to the machine part until it stops against the machine part and thus the correct axial preload of the tapered roller bearing is already set without further adjustment, the method according to the invention can be carried out very simply and quickly.

In particular, in the method according to the invention, the elastically deformable component of the tensioning device with respect to their elastic constant and their tolerances tolerances and the rigid component of the tensioning device, the machine part and the tapered roller bearing with respect to their permitted dimensional tolerances can be coordinated so that the product from within the approved Dimensional tolerances resulting mimmal axial deformation path and the elastic constant of the elastically deformable component of the clamping device at least the predetermined minimum value of the axial force corresponds.

Furthermore, in the method according to the invention, the elastically deformable component of the tensioning device with respect to their elastic constant and their permitted dimensional tolerances and the rigid component of the tensioning device, the machine part and the tapered roller bearing with respect to their allowable dimensional tolerances can be coordinated so that the product from within the approved Dimensional tolerances resulting maximum axial deformation path and the elastic constant of the elastically deformable component of the clamping device corresponds to a maximum of the predetermined maximum value of the axial force.

The invention will be explained below with reference to the exemplary embodiments illustrated in the drawing. Show it

1 shows an embodiment of an inventively designed bearing assembly in a schematic sectional view,

Figure 2 shows another exemplary embodiment of the bearing assembly according to the invention in a schematic sectional view and

Figure 3 shows the exemplary embodiment shown in Figure 1 of the bearing assembly according to the invention during assembly in a sectional view.

Figure 1 shows an exemplary embodiment of an inventively designed bearing assembly in a schematic sectional view. The bearing assembly includes a double row Kegeh ^* olle bearing 1 and a tension apparatus 2 with which the Kegelκ is> llenlager 1 fixed to a shaft connecting part. 3 The shaft connection part 3 can be fastened, for example, to a rotor shaft (not shown in FIG. 1) that is driven by a rotor of a wind energy plant.

The tapered roller bearing 1 has a rotation axis 4. Unless stated otherwise below, directions are in each case based on this axis of rotation 4 of the tapered roller bearing 1. An axial direction is thus a direction parallel to the axis of rotation 4 of the tapered roller bearing 1. A radial direction is a direction perpendicular to the axis of rotation 4 of the Kegerrollenlagers first

The tapered roller bearing 1 has an outer ring 5 with two axially adjacent conical raceways, which together form a V-shaped profile. The outer ring 5 has an outer diameter of at least 1 meter and has axial holes 6, with the aid of the outer ring 5 can be attached to a non-figured housing. Furthermore, the tapered roller bearing 1 has two axially juxtaposed inner rings 7 and 8, each with a conical raceway. The inner ring 7 has an outer axial end surface 8 and the inner ring 9 has an outer axial end surface 10. The outer ring 5 and the two inner rings 7, 9 are formed in the illustrated embodiment as closed in the circumferential direction rings. In principle, it is also possible to use segmented rings.

On the raceway of the inner ring 7 and the adjacent raceway of the outer ring 5 tapered rolling elements 11 roll off. On the raceway of the inner ring 9 and the adjacent raceway of the outer ring 5 taper conical rolling elements 12 from. The rolling elements 11 are arranged in a cage 13, the rolling elements 12 in a cage 14. The cages 13, 14 may be segmented or formed closed in the circumferential direction. For example, the individual cage segments can be lined up in the circumferential direction, as disclosed in DE 102 46 825 A1 and be made of plastic.

The two inner rings 7, 9 are arranged on the shaft connection part 3 and rotatably connected to the shaft connection part 3. For this purpose, the shaft connecting part 3 has a shoulder 15 with an axial stop surface 16 against which the inner ring 7 axially abuts with its outer axial end surface 8. Furthermore, the shaft connection part 3 has an axial abutment surface 17 at its axial end opposite to the shoulder 15.

The tensioning device 2 has a clamping ring 18 and an elastic ring 19. The clamping ring 18 is made, for example, of metal, in particular of steel, and has axial bores 20 and in the region of the axial bores 20 an axial stop surface 21 which abuts against the axial stop surface 17 of the shaft connection part 3. The elastic ring 19 is fixed to the axial side of the clamping ring 18, which faces the outer axial end surface 10 of the inner ring 9 of the tapered roller bearing 1 and has an axial end surface 22 which rests against the outer axial end surface 10 of the inner ring 9. In the illustrated embodiment, the elastic ring 19 is made of an elastomer material and connected by vulcanization with the clamping ring 18. For the attachment of the elastic ring 19 on the clamping ring 18, however, other cohesive connections come into question. Likewise, a positive connection is possible. Furthermore, in the illustrated embodiment, the clamping ring 18 and the elastic ring 19 are each closed in the circumferential direction. Alternatively, the clamping ring 18 and / or the elastic ring 19 may also be formed segmented.

The elastic ring 19 is clamped axially between the inner ring 9 of the tapered roller bearing 1 and the clamping ring 18, since the inner ring 7 is prevented by the shoulder 15 of the shaft connection part 3 at a deflection in the axial direction and the clamping ring 18 is screwed by means of clamping screws 24 with the shaft connection part 3 , Compared to an undeformed state, the elastic ring is compressed in the axial direction by an axial deformation path x. On the inner ring 7, 9 of the tapered roller bearing 1 accordingly acts an axial force F, which is the greater, the stronger the elastic ring 19 is compressed axially, d. H. the larger the axial deformation path x is. Thus, the tapered roller bearing 1 is under an axial bias whose size corresponds to the axial force F. When the elastic ring 19 has an elastic constant k, the axial force F results:

F = k * x.

The axial deformation path x of the elastic ring 19 is limited by the fact that the clamping ring 18 abuts axially with its axial stop surface 21 against the axial stop surface 17 of the shaft connection part 3. An axial displacement of the clamping ring 18 up to this stop state can take place with the aid of the clamping screws 24, which are threaded axially through the axial bores 20 and screwed into the shaft connection part 3. In the assembled state of the tapered roller bearing 1, the clamping screws 24 are fully tightened, so that the clamping ring 18 abuts axially against the shaft connection part 3. As a result, the axial deformation path x of the elastic ring 19 and thus the axial force F on the inner rings 7, 9 defined in principle exactly and accordingly the axial preload of the tapered roller bearing 1 exactly specified.

Due to tolerances in the axial dimensions of the elastic ring 19, the clamping ring 18, the shaft connection part 3 and the inner rings 7, 9, the deformation path x of the elastic ring 19 in the assembled state is not always exactly the same value, but may within a range vary between a minimum value x min and a maximum value x max. Accordingly, the axial force F exerted on the inner rings 7, 9 can also vary between a minimum value F min and a maximum value F max.

The minimum value x min for the axial deformation path x and thus the minimum value F_min for the axial force result for a first combination of maximum exhausted tolerances in the axial dimensions. In a second combination of maximum exhausted tolerances, the maximum value x max of the axial deformation path x and thus also the maximum value F max of the axial force F results.

Specifically, the axial deformation amount x increases with increasing axial distance a1 between the axial end surface 22 of the elastic ring 19 and the axial abutment surface 21 of the clamping ring 18 in the undeformed state of the elastic ring 19, with increasing axial distance a2 between the two axial abutments 16, 17 of the shaft connection part 3 from and with increasing axial distance a3 between the outer axial end surfaces 8, 10 of the inner rings 7, 9 to. The minimum value F min of the axial force results for a combination of the smallest permissible values for a 1 and a 3 and the largest permissible value for a 2. The maximum value F max of the axial force results for a combination of the largest permissible values for a 1 and a3 and the smallest permissible value for a2. In order to ensure that the axial force F on the inner ring 7, 9 and thus the axial preload of the tapered roller bearing 1, even with an unfavorable combination of tolerances for the axial distances al, a2 and a3 in an allowable range, the tolerances for the axial distances al, a2 and a3 and the elastic constant k of the elastic ring 19 are matched to one another such that the minimum value F min and the maximum value F max of the axial force F are just within the permissible range.

The exemplary embodiment of the bearing arrangement according to the invention shown in FIG. 1 can be modified in many different ways, in particular with regard to the design of the tensioning device 2. For example, instead of the clamping ring 18, the elastic ring 19 may be attached to the outer axial end surface 10 of the inner ring 9 of the tapered roller bearing 1. In principle, it is even possible to attach the elastic ring 19 on the outer axial end surface 8 of the inner ring 7 of the tapered roller bearing 1 or on the stop surface 16 of the shoulder 15 of the shaft connection part 3.

Furthermore, it is possible to replace the elastic ring 19 by a different type of elastic member. Such a modified embodiment is shown in FIG.

Figure 2 shows another embodiment of the inventive bearing arrangement in a schematic sectional view. In this embodiment, the configuration of the tapered roller bearing 1 and the shaft connection part 3 completely coincide with the embodiment shown in Figure 1.

However, in the tensioning device 2, the elastic ring 19 shown in FIG. 1 is omitted. Instead, the clamping ring 18 has a flange-like extension 23 which extends obliquely radially outwardly. In particular, the orientation of the flange-like extension 23 is selected such that it extends toward the inner ring 9 and bears against the outer axial end face 10 of the inner ring 9 under tension. For this purpose, the flange-like extension 23 is made of an elastic material, in particular of a spring steel. In the illustrated embodiment, the flange-like extension 23 is formed integrally with the clamping ring 18 and has a smaller material thickness than the other areas of the clamping ring 18. Accordingly, the entire clamping ring 18 including the flange-like extension 23 can be made of the same material. However, it is possible, for example, by means of a suitable heat treatment to vary the hardness location-dependent. In particular, the clamping ring 18 in the region of the flange-like extension 23 may have increased hardness and elasticity. Furthermore, it is possible to form segmented the entire clamping ring 18 including the flange-like extension 23.

The axial clamping of the tapered roller bearing 1 and the generation of a bias in the tapered roller bearing 1 takes place in an analogous manner, as described with reference to FIG. The statements there on the component tolerances and the axial deformation path x apply analogously, wherein the flange-like extension 23 analogous to the elastic ring 19 also has an elastic constant k and enters into the determination of the axial distance al an axial position, the maximum axial projection of the flange Extension 23 of the clamping ring 18 corresponds in the relaxed state.

The assembly and fixation of the tapered roller bearing 1 on the shaft connecting part 3 is considerably facilitated by the erfϊndungsgemäße training of the clamping device 2 and can be carried out in the manner described below the. The description will be the illustrated in Figure 1 embodiment of

Bearing arrangement based. In the exemplary embodiment or other variants shown in FIG. 2, it is possible to proceed in an analogous manner.

First, the tapered roller bearing 1 is axially pushed onto the shaft connection part 3 from the side axially opposite to the shoulder 15 until the outer axial end surface 8 of the inner ring 7 of the tapered roller bearing 1 abuts against the axial stop surface 16 of the shoulder 15 of the shaft connection part 3 strikes. Depending on whether there is a radial overlap between the shaft connecting part 3 and the inner rings 7, 9 of the tapered roller bearing 1, it may be necessary for the ball bearing roller 1 to be pressed onto the shaft connecting part 3 and / or for the inner rings 7, 9 to be heated be widened or the shaft connection part 3 is cooled.

When the tapered roller bearing 1 has reached its end position on the shaft connection part 3, the tensioning device 2 is pushed from the same side as the tapered roller bearing 1 axially onto the shaft connection part 3 until the axial end face 22 of the elastic ring 19 of the tensioning device 2 becomes the outer axial one End face 10 of the inner ring 9 touched. This situation is shown in FIG.

FIG. 3 shows the exemplary embodiment of the bearing assembly according to the invention shown in FIG. 1 during assembly in a sectional view.

In a next step, the clamping screws 24 are inserted into the axial bores 20 of the clamping ring 18 and tightened. As a result, the tensioning device 2 is brought closer to the tapered roller bearing 1 until the axial abutment surface 21 of the clamping ring 18 of the tensioning device 2 abuts axially against the axial abutment surface 17 of the shaft connection part 3. In this case, the elastic ring 19 of the clamping device 2 between the inner ring 9 of the tapered roller bearing 1 and the clamping ring 18 of the clamping device 2 is axially clamped and compressed to the axial deformation path x.

With the insertion and tightening of the clamping screws 24 can be started immediately after the attachment of the tensioning device 2 to the shaft connector part 3, if for the postponement of the tensioning device 2 on the shaft connector part 3, a force application is required. After striking the KJemmrings 18 of the tensioning device 2 on the shaft connecting part 3, the clamping screws 24 are still tightened until each of a predetermined torque is reached. Then the assembly and the fixation of the tapered roller bearing 1 are completed. This situation is shown in FIG.

By the axial clamping between the shoulder 15 of the shaft connection part 3 on the one side and the tensioning device 2 on the other side, the tapered roller bearing 1 is rotatably connected to the shaft connection part 3 and has an axial bias within a desired range.

LIST OF REFERENCE NUMBERS

1 tapered roller bearing

2 clamping device

3 shaft connection part

4 rotation axis

5 outer ring

6 Axial bore

7 inner ring

8 External axial end surface

9 inner ring

10 External axial end surface

11 rolling elements

12 rolling elements

13 cage

14 cage

15 shoulder

16 Axial stop surface

17 Axial stop surface

18 clamping ring

19 Elastic ring

20 Axial bore

21 Axial stop surface

22 Axial end surface

23 Flange-like extension

24 clamping screw

Claims

P atentanspr ch e bearing arrangement for rotatably supporting a machine part and method for fixing a tapered roller bearing on a machine part

1. Bearing arrangement with a double row tapered roller bearing (1) for rotatably supporting a machine part (3) and with a clamping device (2) for fixing the tapered roller bearing (1) on the machine part (3), wherein

- the tapered roller bearing (1)

- an outer ring (5) whose outer diameter is at least 1 meter, «a first inner ring (7),

a second inner ring (9) arranged axially next to the first inner ring (7),

a set of conically shaped first rolling elements (11) which roll between the outer ring (5) and the first inner ring (7) and - a set of conically shaped second rolling elements (12) which are axially adjacent to the first rolling elements (11) are arranged and roll between the outer ring (5) and the second inner ring (9) has

- The clamping device (2) has a rigid component (18) and an elastically deformable component (19, 23), - the rigid component (18) of the clamping device (2) axially on the machine part

(3) strikes,

- The elastically deformable component (19, 23) of the clamping device (2) axially clamped and thereby axially deformed against a relaxed state and - the elastically deformable component (19, 23) of the clamping device (2) with the first inner ring (7) of the Tapered roller bearing (1), with the second NEN ring (9) of the tapered roller bearing (1), with the rigid component (18) of the clamping device (2) or with the machine part (3) is connected.

2. Bearing arrangement according to claim 1, characterized in that the first inner ring (7) abuts axially on the machine part (3) or in cooperation with the machine part (3), the elastically deformable component (19, 23) of the clamping device (2) axially clamped and the second inner ring (9) axially abuts the rigid component (18) of the tensioning device (2) or, in cooperation with the rigid component (18) of the tensioning device (2), the elastically deformable component (19, 23) of the tensioning device (2) a - xial clamps

3. Bearing arrangement according to one of the preceding claims, characterized in that the elastically deformable component (19) of the clamping device (2) cohesively, in particular by vulcanization, with the first inner ring (7) of the tapered roller bearing (1), with the second inner ring (9) of the tapered roller bearing (1), with the rigid component (18) of the clamping device (2) or with the machine part (3) is connected.

4. Bearing arrangement according to one of claims 1 or 2, characterized in that the elastically deformable component (23) of the clamping device (2) integrally with the first mnenring (7) of the tapered roller bearing (1), with the second inner ring (9) of the tapered roller bearing (1), with the rigid component (18) of the clamping device (2) or with the machine part (3) is formed and in particular made of the same material as the first mnenring (7) of the tapered roller bearing (1), the second inner ring ( 9) of the tapered roller bearing (1), the rigid component (18) of the clamping device (2) or the machine part (3).

5. Bearing arrangement according to claim 4, characterized in that the elastically deformable component (23) of the tensioning device (2) has a relation to the rigid component (18) reduced material thickness.

6. Bearing arrangement according to one of claims 4 or 5, characterized in that the elastically deformable component (23) of the clamping device (2) is designed as a flange-like extension of the rigid component (18).

7. Bearing arrangement according to one of the preceding claims, character- ized in that the rigid component (18) and / or the elastically deformable component (19, 23) of the clamping device (2) is designed as a ring closed in the circumferential direction.

8. Bearing arrangement according to one of claims 1 to 6, characterized marked, that the rigid component (18) and / or the elastically deformable

Component (19, 23) of the clamping device (2) is formed segmented in the circumferential direction.

9. Bearing arrangement according to one of the preceding claims, character- ized in that the elastically deformable component (19, 23) of the

Clamping device (2) made of spring steel or plastic, in particular from E lastomermaterial made.

10. Bearing arrangement according to one of the preceding claims, character- ized in that the machine part (3) is designed as a shaft connection part or a shaft

11. Bearing arrangement according to one of the preceding claims, characterized in that the bearing arrangement is designed as a component of a wind energy plant.

12 wind turbine with a rotor which is fixed to a rotor shaft, characterized in that the rotor shaft is rotatably mounted in a bearing assembly according to one of the preceding claims.

13. A method for fixing a tapered roller bearing (1), which has an outer diameter of at least 1 meter, by means of a clamping device (2) having a rigid component (18) and an elastically deformable component (19, 23) on a machine part ( 3), wherein the rigid component (18) of the clamping device (2) is axially approximated to the machine part (3) until it abuts on the machine part (3) and thereby the elastically deformable

Component (19, 23) of the tensioning device (2) connected to the tapered roller bearing (1), the rigid component (18) of the tensioning device (2) or the machine part (3) is axially deformed about a deformation path (x), which is so large that the tapered roller bearing (1) with an axial force (F) having a value between a predetermined minimum value (F min) and a predetermined maximum value (F max), axially between the rigid component (18) of the clamping device (2) and the machine part (3) or a fastener connected to the machine part (3) is clamped.

14. The method according to claim 13, characterized in that the elastically deformable component (19, 23) of the clamping device (2) in terms of their elastic constant (k) and their tolerances tolerances and the rigid component (18) of the clamping device (2), the Machine part (3) and the tapered roller bearing (1) are matched with respect to their tolerances tolerances that the product of the resulting within the tolerances allowed minimum axial deformation path (x) and the elastic constant (k) of the elastically deformable component (19 , 23) of the tensioning device (2) corresponds to at least the predetermined minimum value (F_min) of the axial force (F).

15. The method according to any one of claims 13 or 14, characterized in that the elastically deformable component (19, 23) of the tensioning device (2) in terms of their elastic constant (k) and their tolerances tolerances and the rigid component (18) of the tensioning device ( 2), the machine part (3) and the taper roller bearing (1) with regard to their approved

Dimensional tolerances are coordinated so that the product of the within the tolerances allowed maximum axial deformation path (x) and the elastic constant (k) of the elastically deformable component (19, 23) of the clamping device (2) maximum the predetermined maximum value ( F max) corresponds to the axial force (F).