DE102009058355A1 - Rolling bearing device with a ring piston sleeve, bearing assembly and method for adjusting the employment of a hydraulically adjustable bearing assembly - Google Patents

Abstract

The invention relates to a roller bearing device, comprising an inner ring (11) with an inner ring Laufbabn (13), an outer ring (15) with an outer raceway (17), between the inner ring raceway (13) and outer ring raceway (17) both rolling rings (11, 15) rolling rolling elements (19) and an annular piston sleeve (9) having a sliding bearing surface (25, 27) for their axially freely displaceable bearing and a ring piston pressure surface (29a) to its axially hydraulically movable bearing and a seat (31 ), to which one of the bearing rings (11, 15) is attached. The invention also relates to an associated bearing assembly (3), a method for adjusting a position of the hydraulically engageable bearing assembly (3) and a use of the bearing assembly (3).

Description

The invention relates to a rolling bearing device, comprising an inner ring with an inner ring raceway, an outer ring with an outer ring raceway, between rolling inner raceway and outer raceway of the two bearing rings rolling rolling elements. The invention also relates to a bearing assembly and a method for adjusting the employment of a hydraulically adjustable bearing assembly.

The JP 2006 177268 A describes a salaried rolling bearing assembly of a wind turbine with two tapered roller bearings in O arrangement, at the two facing inner ring end faces a respective front side adjacent hydraulic cylinder is interposed interspersed.

The US 3,222,991 describes an employed rolling bearing assembly in O arrangement of a spindle of a machine tool with five angular contact ball bearings, wherein a pair of angular contact ball bearings via an inner ring end face of a single angular contact ball bearing are hydraulically biased by means of a frontally abutting annular piston.

The US 4,611,934 describes an employed rolling bearing assembly in O arrangement of a spindle of a machine tool with four angular contact ball bearings, wherein two outer rings of a pair of angular contact ball bearings are screwed together by a bearing means form-fitting and the bearing means is connected via an axially plate-spring-like, flexible stiffener with an outer peripheral portion, the is fixed to a housing, wherein the plate spring-like, flexible stiffener is hydraulically bendable to bias the rolling bearing assembly.

The object of the invention is to provide a rolling bearing device with which the life of a bearing assembly is improved.

The object of the invention is achieved by a rolling bearing device, comprising an inner ring with an inner ring raceway, an outer ring with an outer ring raceway, between inner raceway and outer raceway of the two bearing rings rolling rolling elements and a ring piston sleeve having a sliding bearing surface to its axial having freely displaceable mounting and a ring piston pressure surface to its axially hydraulically movable mounting and a seat to which one of the bearing rings is attached.

A disadvantage of many roller bearings is the lack of adjustment options. Thus, the operating cycle, for example in cylindrical roller bearings, resulting from production bearing air, shaft and housing bore diameter and the related tolerances, as well as the temperature distribution in the storage environment during operation. These factors result in a comparatively large clearance. In many rolling bearing assemblies, such as tapered roller bearing assemblies can be adjusted by accurate measurement and appropriate adjustment of intermediate rings or similar adjustment means the mounting clearance or mounting bias of the rolling bearing assemblies relatively accurately.

If such a rolling bearing assemblies are put into operation, however, the set during assembly clearance changes to operating storage air. The amount of bias of the operating bearing air is dependent on the temperature distribution in the storage environment. However, this is not always known exactly. To avoid these disadvantages, hydraulically adjustable bearing arrangements can be used.

In order to improve the life of hydraulically adjustable bearing assemblies, a rolling bearing apparatus is proposed which comprises an annular piston sleeve comprising a sliding bearing surface for its axially freely displaceable mounting and a ring piston pressure surface to its axially hydraulically movable bearing and a seat to which one of the bearing rings is attached , The bearing ring fastened to the seat of the annular piston sleeve can, in particular, be the outer ring of the rolling bearing, in particular a tapered roller bearing or an angular contact ball bearing, for example in the case of an armed bearing of a shaft in an X arrangement. By an axially freely displaceable mounting of the annular piston sleeve and a particular rigid attachment of the bearing ring on the annular piston sleeve exact employment of the storage can be achieved with high vibration damping properties.

The bearing ideally has the same preload in any operating condition, whether cold or warm, even with load reversal. The preload level can be set so that sliding of the rolling elements at high dynamic stress is largely avoided. By a targeted employment of rolling bearings, in particular tapered roller bearings calculative bearing life can be optimized. Another advantage is that during installation no adjustments are necessary, such. As measuring of bearing distances or grinding of intermediate sleeves.

The bearing ring, in particular the outer ring can be pressed into the annular piston sleeve or formed integrally with the annular piston sleeve. The annular piston sleeve forms an actuator which actuated by means of fluid pressure, in particular can be adjusted axially. The annular piston sleeve or the actuator has a sliding bearing surface for axially free slidable storage and a ring piston pressure surface for axially hydraulically movable storage. Through the sliding bearing surface and the annular piston pressure surface a trouble-free, in particular smooth and low-friction adjustment of the annular piston sleeve and the actuator is ensured. The annular piston sleeve can insofar damp vibrations or vibrations which act, for example, by a housing or a shaft on the bearing arrangement, ie prevent or at least reduce transmission to the seat ring firmly connected to the seat or reduce self-vibrations or natural vibrations of the bearing ring itself, ie damp. In order to transmit the highest possible damping properties of the annular piston sleeve on the bearing ring, the bearing ring may be pressed into the annular piston sleeve. The bearing ring can be pressed, for example in the case of an outer ring from the inside into the annular piston sleeve ie the annular piston sleeve thereby circumferentially surrounds the bearing ring from the outside. The bearing ring can be pressed, for example, in the case of an inner ring from the outside to the annular piston sleeve, ie, the bearing ring surrounds the annular piston sleeve circumferentially from the outside. Such an arrangement can be used for example in an external rotor with centrally fixed axis. Instead of a compression composite of annular piston sleeve and bearing ring, the annular piston sleeve with the bearing ring can also be made in one piece from a shell component. The seat is omitted or the seat is so far created by a material connection of ring piston sleeve and bearing ring. The bearing ring is integrated into the annular piston sleeve, so that a compact bearing arrangement is achieved.

The annular piston sleeve may be designed to form the annular piston pressure surface stepped outside circumference. The annular piston pressure surface is realized insofar by the radially extending step between two sleeve sections of different diameters. A sealing of the annular piston sleeve can be done with hydraulic seals, which may be in a simple configuration O-rings. The hydraulic seals can be integrated in a housing or in the annular piston sleeve. An axial preload force results from the hydraulic pressure and the annular piston pressure surface. The annular piston sleeve itself should have a sufficient length, so that, for example due to eccentric bearing loads to be feared terminals is avoided.

In all embodiments of the invention, the inner ring, the outer ring and the rolling elements can form a tapered roller bearing or an angular contact ball bearing.

Tapered roller bearings can preferably be used in wind turbines. Tapered roller bearings and cylindrical roller bearings are usually used there, since high loads can occur at low speeds. When installing, in particular the fits between the components should be observed, so that the preload between two tapered roller bearings is guaranteed. With the hydraulic pressure in the ring piston sleeve, the preload force of the tapered roller bearings can be adjusted easily and constantly. The preload force depends only on the set pressure and the attack surface in the ring piston sleeve d. H. the ring piston pressure surface from.

Angular contact ball bearings can preferably be used in the hydraulic adjustment of spindles in machine tools. In general, employed angular contact ball bearings are used when high speeds must be coped with. Due to a high speed, it can lead to a widening of the bearing rings due to the centrifugal force. As the speed increases, so does the preload between the angular contact ball bearings. The employment according to the invention hydraulic bearings, the employment can be actively set or regulated.

A bearing arrangement according to the invention has at least one hydraulically adjustable rolling bearing device, as described. In a further development of the invention, the bearing arrangement may comprise at least one hydraulically adjustable rolling bearing device, as described, and comprise a further rolling bearing, which is designed to receive a resulting axial force of a machine part carried by the bearing assembly, in particular gear wheel. In other words, the one bearing arrangement is hydraulically employed, which does not absorb the resulting axial force of the driven shaft or the toothing of a transmission having the bearing assembly.

In the bearing arrangement according to the invention, the further rolling bearing for forming two hydraulically adjustable rolling bearing devices can be designed as a hydraulically adjustable rolling bearing device, in particular as described, wherein the two hydraulically adjustable rolling bearing devices can form an employee storage, in particular in X-arrangement. For example, at high axial vibration problem, it may be useful to support both tapered roller bearings hydraulically. Due to the closed hydraulic circuit, the oil flows from one bearing side to the other bearing side when the load is reversed. By an adjustable throttle, as described later, the oil flow can be selectively throttled, whereby one achieves an attenuation of the axial vibration. The ring cross section in both pistons should be the same.

Due to a sufficient sleeve length and by the Ölbeaufschlagung a clamping of the annular piston sleeve can be avoided. The oil film and the hydraulic seals can provide damping properties, which can reduce a harmful influence of vibration. From these advantages, a reliable storage can result, which can significantly increase the operational safety, for example of wind turbines.

In the bearing assembly according to the invention, the hydraulically adjustable rolling bearing device or the hydraulically adjustable bearing assembly may form part of a fixed bearing and another rolling bearing a floating bearing.

In a further development, the bearing arrangement can have a stop for limiting a displacement path of the bearing arrangement in an axial direction and a further stop for limiting the displacement path of the bearing arrangement in the other axial direction. The annular piston sleeve according to the invention and optionally a housing can be constructed so that in each case the axial movement is limited by the stop in one direction. As a result, an axial displacement path can be realized in the opposite direction to the stop limit during load reversal. The necessary displacement results from the tolerance chain of all adjacent parts, as well as from the axial expansion, resulting from the different temperature level of shaft and housing.

To prevent rotation of the annular piston sleeve of the hydraulically adjustable rolling bearing device in a support member, the bearing assembly may have an anti-rotation.

For damping axial vibrations of the bearing assembly, the bearing assembly may comprise a damping device. The damping device can be formed by at least one axially damping seal, which seals the annular piston sleeve of the hydraulically adjustable rolling bearing device against a support member of the bearing assembly. The damping device may alternatively or additionally be formed by at least one damping throttle in a fluidic system which supplies the hydraulically adjustable rolling bearing device with hydraulic pressure.

In a hydraulic supply between the annular piston sleeve of two rolling bearing devices, two throttle valves may be used as damping elements. With appropriate design of the hydraulic connection, this can also be done with only a single throttle valve. Other components in the hydraulic connection can be check valve, pressure monitoring and pressure control valve. A pressure relief required for disassembly can be done via a vent on the respective annular piston sleeve. For mounting the bearing assembly or the rolling bearing of the vent closure is also required to allow the first existing air in the pressure chamber to escape as soon as the hydraulic oil flows. For example, at a high axial vibration level on a shaft, the shaft bearing system can oscillate in the axial direction. By installing the throttles according to the invention, these axial vibrations can be damped.

• – Öffnen eines Ventils in einer Verbindungsleitung von einem hydraulischen Druckerzeuger zu einer Ringkolbenhülse wenigstens einer hydraulisch verstellbaren Wälzlagervorrichtung;
• – Erhöhen des hydraulischen Druckes an der Ringkolbenhülse bis die Soll-Anstellung der Lageranordnung erreicht ist, insbesondere während des Betriebs der Lageranordnung,
• – Schließen des Ventils wenn ein die Soll-Anstellung der Lageranordnung entsprechender hydraulischer Druck erreicht ist.

A method according to the invention for adjusting an adjustment of a hydraulically adjustable bearing arrangement, in particular a bearing arrangement as described, may comprise the following steps:

• - Opening a valve in a connecting line from a hydraulic pressure generator to an annular piston sleeve at least one hydraulically adjustable rolling bearing device;
• Increasing the hydraulic pressure on the annular piston sleeve until the desired position of the bearing arrangement is reached, in particular during the operation of the bearing arrangement,
• - Closing the valve when the desired position of the bearing assembly corresponding hydraulic pressure is reached.

The pressure on the annular piston sleeve can be monitored by a pressure sensor. To set or regulate the pressure, a valve, in particular a 2/2-way valve can be switched to run. The valve is preferably connected to the pressure sensor and is automatically controlled according to the measured pressure. This can be done at constant operating condition. The actual setting or regulation can take only a short moment. Thereafter, the valve, in particular 2/2-way valve is switched back to passage lock. In the event of a jerky load reversal, the hydraulically supported bearing does not completely lose its position, since the pressure in the system can be maintained by a check valve. If the pressure rises, for example due to heating of the system, a pressure relief can be achieved by the valve and the setpoint pressure can be set again. For this, the valve is briefly switched to run until the pressure has reached its setpoint.

• – Drosseln eines Fluidflusses in einer Verbindungsleitung zwischen der hydraulisch verstellbaren Wälzlagervorrichtung und einer weiteren hydraulisch verstellbaren Wälzlagervorrichtung, insbesondere während des Betriebs der Lageranordnung.

A development of the method according to the invention can have the further step:

• - throttling a fluid flow in a connecting line between the hydraulically adjustable rolling bearing device and another hydraulically adjustable rolling bearing device, in particular during operation of the bearing assembly.

An inventive use of a bearing assembly as described provides for use in a gearbox of a wind turbine or on a spindle of a machine tool.

Various embodiments of the invention are illustrated by way of example in the accompanying schematic drawings. Show it:

1 a sectional view of a first embodiment of a rolling bearing assembly with a circuit diagram of a fluid power system,

2 a sectional view of a second embodiment of a rolling bearing assembly with a circuit diagram of a fluid power system,

3 a sectional view of a third embodiment of a rolling bearing assembly with a circuit diagram of a fluid power system,

4 a sectional view of a fourth embodiment of a rolling bearing assembly with a circuit diagram of a fluid power system and

5 a sectional view of an alternative embodiment of a rolling bearing assembly.

In the 1 is a rolling bearing device according to the invention 1 in a bearing arrangement 2 shown. The bearing arrangement 3 The first embodiment is exemplary as an employee storage in X-arrangement with two tapered roller bearings 5 and 7 executed. The first tapered roller bearing 5 forms together with a ring piston sleeve 9 the rolling bearing device according to the invention 1 , The second tapered roller bearing 7 is designed as a known standard tapered roller bearing. Each rolling bearing device 1 has an inner ring 11 with an inner ring track 13 , an outer ring 15 with an outer raceway 17 and interposed rolling elements 19 on. The two employed tapered roller bearings 5 and 7 exemplify a wave 21 comprising a transmission gear 23 ,

The annular piston sleeve 9 is formed in the manner of a hollow cylindrical socket. The annular piston sleeve 9 has a first sliding bearing surface 25 and a second slide bearing surface 27 on. The first sliding bearing surface 25 is through a portion of the outwardly facing lateral surface of the annular piston sleeve 9 formed with a smaller diameter. The second sliding bearing surface 27 is through a portion of the outwardly facing lateral surface of the annular piston sleeve 9 formed with a larger diameter. In a radially extending annular disk-shaped transition section between the sliding bearing surface 25 and plain bearing surface 27 becomes a step due to the difference in diameter 29 educated. The circular ring surface of the step 29 forms a ring piston pressure surface 29a , To limit a displacement of the bearing assembly 3 or the annular piston sleeve 9 has in the embodiment, the annular piston sleeve 9 a stop 37 in the form of a further step, with a shoulder of a supporting component 39 how a housing cooperates. ??

The annular piston sleeve 9 has a seat 31 on. The seat 31 serves for the rigid connection of one of the bearing rings 11 . 15 , in illustrated example, the connection of the outer ring 15 with the annular piston sleeve 9 , The outer ring 15 can either, as in 1 left above the midline 33 shown in the annular piston sleeve 9 be pressed in or, as in 1 left below the midline 33 shown as a one-piece rolling bearing component 35 be educated.

The in 1 illustrated circuit diagram of a fluid power system 41 shows a valve 43 for opening and closing a connection line 45 , The valve 43 can, as shown in the embodiment be a 2/2-way valve. The connection line 45 runs from a hydraulic pressure generator 47 to the annular piston sleeve 9 , In the connection line 45 is a throttle 49 inserted. By means of a check valve 51 the hydraulic pressure is kept in the system. The check valve 51 is in the direction of the pressure generator 47 to the bearing arrangement 1 always permeable, but blocking in the opposite direction. For example, when mounting the bearing assembly after switching on the pressure generator 47 Pressurized oil into the cavity of the annular piston sleeve 9 pumped, the air contained escapes through a vent valve. As soon as the pressure generator 47 set pressure and thus the desired preload is reached in the bearing assembly prevents the check valve 51 in that pressure increases occurring in the annular piston sleeve due to the operation of the bearing arrangement 9 to the pressure generator 47 be passed on and the total pressure in the system decreases accordingly. About a pressure sensor 53 the pressure in the system can be monitored. If the pressure rises above the set value, it can be opened by briefly opening the valve 43 the pressure is reduced back to the setpoint.

In the 2 is a second embodiment of a rolling bearing device according to the invention 1 in a bearing arrangement 2 shown. In this second embodiment, the bearing assembly 3 of two hydraulically adjustable rolling bearing devices according to the invention 1 educated. Both Rolling bearings are called tapered roller bearings 5a and 5b ausgerführt. Each tapered roller bearings 5a . 5b is with its own ring piston sleeve 9a respectively. 9b connected. To form a damping device is the annular piston sleeve 9a hydraulically via a coupling line 56 with the annular piston sleeve 9b connected and with an inserted damping throttle 59 Mistake. Alternatively or, as shown in the illustrated second embodiment, in addition to the damping throttle 59 can as further damping devices axially damping seals 57a . 57b be provided. The seals 57a and 57b contribute to the damping of the system and also seal the pressure chamber of the rotary piston sleeves 9a and 9b so that no oil can escape. The seals 57a and 57b lie in correspondingly dimensioned recesses in the support member. Also in the second embodiment, the outer ring 15 either, as in 2 left above the midline 33 shown in the annular piston sleeve 9 be pressed in or, as in 2 left below the midline 33 shown as a one-piece rolling bearing component 35 be educated.

In the 3 is a third embodiment of a rolling bearing device according to the invention 1 in a bearing arrangement 2 shown. In this third embodiment, the bearing assembly 3 from a camp 61 and a floating warehouse 63 educated. The floating bearing 63 may be a standard rolling bearing, for example, as shown, a cylindrical roller bearing. The camp 61 is formed by an inventively designed hydraulically adjustable rolling bearing device 1 in conjunction with a standard rolling bearing, such as the tapered roller bearing shown or in conjunction with another inventively designed hydraulically adjustable rolling bearing. The camp 61 is formed here by way of example of an employed storage of two tapered roller bearings.

In the 4 is a fourth embodiment of a rolling bearing device according to the invention 1 in a bearing arrangement 2 shown. In this fourth embodiment, the bearing assembly 3 of two inventively designed hydraulically adjustable rolling bearing devices 1 educated. The rolling bearing devices 1 form an employed storage. By means of the throttle 49 the hydraulic pressure in the system is adjusted and the amount of adjustment that is set the axial contact force. About the damping throttle 59 becomes the axial mobility of the bearing assembly 3 or the shaft 21 set. By means of the damping throttle 59 can thus axial vibrations of the shaft exemplified 21 are variably attenuated ie the amount of attenuation can be adjusted.

In the 5 is a fragmentary an alternative embodiment of the rolling bearing device according to the invention shown. Here are the seals 57a and 57b in recesses of the annular piston sleeve 9 inserted. The annular piston sleeve 9 is integrally formed with the outer ring. The annular piston sleeve 9 is analogous to the previous embodiments in a support member 39 held and has a recess 70 on. In the recess 70 grab a sapwood 71 one on the supporting component 39 is attached. This ensures that the annular piston sleeve 9 is not radially rotatable.

LIST OF REFERENCE NUMBERS

1

Rolling device

3

bearing arrangement

5

Tapered roller bearings

7

Tapered roller bearings

9

Ring piston sleeve

11

inner ring

13

Inner ring raceway

15

outer ring

17

Outer ring raceway

19

rolling elements

21

wave

23

transmission gear

25

friction bearing surface

27

friction bearing surface

29

step

29a

Ring piston pressure surface

31

Seat

33

center line

35

rolling bearing component

37a, 37b

attack

39

support member

41

fluidic system

43

Valve

45

connecting line

47

pressure generator

49

throttle

51

check valve

53

pressure gauge

55

attenuator

56

coupling line

57a, 57b

seals

59

Damping throttle

61

fixed bearing

63

movable bearing

70

recess

71

cotter

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been 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 assumes no liability for any errors or omissions.

Cited patent literature

• JP 2006177268 A [0002]
• US 3222991 [0003]
• US 4611934 [0004]

Claims (15)

Rolling bearing device comprising an inner ring ( 11 ) with an inner raceway ( 13 ), an outer ring ( 15 ) with an outer raceway ( 17 ), between inner raceway ( 13 ) and outer raceway ( 17 ) of the two bearing rings ( 11 . 15 ) rolling rolling elements ( 19 ) and an annular piston sleeve ( 9 ), which has a plain bearing surface ( 25 . 27 ) to its axially freely displaceable storage and a ring piston pressure surface ( 29a ) to its axially hydraulically movable bearing and a seat ( 31 ), on which one of the bearing rings ( 11 . 15 ) is attached. Rolling bearing device according to claim 1, wherein the bearing ring ( 11 . 15 ), in particular the outer ring ( 15 ) in the annular piston sleeve ( 9 ) or integrally with the annular piston sleeve ( 9 ) is trained. Rolling bearing device according to claim 1 or 2, wherein the annular piston sleeve ( 9 ) to form the annular piston pressure surface ( 29a ) is formed stepped outside circumference. Rolling bearing device according to one of claims 1 to 3, wherein the inner ring ( 11 ), the outer ring ( 15 ) and the rolling elements ( 19 ) form a tapered roller bearing. Bearing arrangement with a hydraulically adjustable rolling bearing device ( 1 ) according to one of claims 1 to 4 and a further rolling bearing ( 7 ) for receiving a resulting axial force of one of the bearing assembly ( 3 ) carried machine part, in particular transmission gear ( 23 ). Bearing assembly according to claim 5, wherein the further rolling bearing ( 7 ) to form two hydraulically adjustable rolling bearing devices ( 1 ) as a hydraulically adjustable rolling bearing device ( 1 ) is designed according to one of claims 1 to 4, and the two hydraulically adjustable rolling bearing devices ( 1 ) together form a salaried storage, especially in X-arrangement. Bearing assembly according to claim 5 or 6, wherein the hydraulically adjustable rolling bearing device ( 1 ) or the hydraulically adjustable bearing arrangement ( 3 ) a part of a permanent camp ( 61 ) and another rolling bearing a floating bearing ( 63 ). Bearing arrangement according to one of claims 5 to 7, comprising a stop ( 37a ) for limiting a displacement of the bearing assembly in an axial direction and another stop ( 37b ) for limiting the displacement of the bearing assembly ( 3 ) in the other axial direction. Bearing arrangement according to one of claims 5 to 8, comprising an anti-rotation device for preventing rotation of the annular piston sleeve ( 9 ) of the hydraulically adjustable rolling bearing device ( 1 ) in a supporting component ( 39 ) of the bearing assembly ( 3 ). Bearing arrangement according to one of claims 5 to 9, comprising a damping device ( 55 ) for damping axial vibrations of the bearing assembly ( 3 ). Bearing assembly according to claim 10, wherein the damping device ( 55 ) of at least one axially damping seal ( 57a . 57b ) is formed, the ring piston sleeve ( 9 ) of the hydraulically adjustable rolling bearing device ( 1 ) against a supporting component ( 39 ) of the bearing assembly ( 3 ) seals. Bearing assembly according to claim 10 or 11, wherein the damping device ( 55 ) of at least one throttle ( 59 ) in a fluid power system ( 41 ) is formed, the hydraulically adjustable rolling bearing device ( 1 ) supplied with hydraulic pressure. Method for adjusting a setting of a hydraulically adjustable bearing arrangement ( 3 ), in particular according to one of claims 5 to 12, with the steps: - opening a valve ( 43 ) in a connection line ( 45 ) from a hydraulic pressure generator ( 47 ) to an annular piston sleeve ( 9 ) at least one hydraulically adjustable rolling bearing device ( 1 ); - increase the hydraulic pressure on the annular piston sleeve ( 9 ) until the desired position of the bearing assembly ( 3 ) is reached, in particular during operation of the bearing assembly ( 3 ), - closing the valve ( 43 ) if a the desired position of the bearing assembly ( 3 ) corresponding hydraulic pressure is reached. Method according to Claim 13, with the further step of: - throttling a fluid flow in a connecting line ( 45 ) between the hydraulically adjustable rolling bearing device ( 1 ) and a further hydraulically adjustable rolling bearing device ( 1 ), in particular during operation of the bearing assembly ( 3 ). Use of a bearing arrangement ( 3 ) according to one of claims 5 to 12 in a transmission of a wind turbine.

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