DE102012221255A1 - Bearing unit for rotor of wind power machine, has stator unit fastened with bearing unit at machine carrier of wind-power plant and rotor assembly, and rotor flange and stator flange fastened with rotor hub - Google Patents

Abstract

The bearing unit (2) has a stator unit (16) and a rotor assembly (14) supported over a rotor-side bearing (18A), a tower-side bearing (18B) and a bearing housing. The stator unit is fastened with the bearing unit at a machine carrier (12) of a wind-power plant and the rotor assembly. A rotor flange and a stator flange are fastened with a rotor hub (10). An inner ring and an outer ring are provided at the rotor assembly and the stator unit. A fixed stop part is formed in a case such that a front team circle (32) is formed over the bearings, the rotor assembly and the stator unit.

Description

The invention relates to a bearing unit for a wind turbine with the feature of the preamble of claim 1.

Such a storage unit is from the DE 10 2008 036 217 A1 refer to.

Wind turbines generally have a tower, at the head end of which a rotatable nacelle is arranged, which forms a machine carrier. On the nacelle a rotor hub is rotatably mounted about a rotation axis, are attached to the rotor blades.

In wind turbines there are both direct drive concepts in which the rotational movement of the rotor hub is transmitted directly and directly to a rotor of a generator. Alternatively, a transmission is interposed between the rotor hub and the generator.

A technical challenge in such wind turbines, which are designed for example for a power range of several megawatts of electrical power, is the provision of a storage that meets high technical requirements, such as a high flexural rigidity, a backlash-free storage, a low-wear kinematics and the simplest possible installation at the same time high economic efficiency.

The most different solution concepts for this bearing problem are already known from the prior art. For example, the so-called two-point storage from the DE 601 31 764 T2 and the so-called three-point storage from the DE 10 2006 037 890 A1 known. In these, a rotor shaft connected to the rotor hub is supported by a plurality of spaced-apart bearings. The bearings are mainly so-called spherical roller bearings. However, these concepts have in a hurry on a high axial play, which can lead to shocks, axial thrust and tilting at different wind loads, which subsequent components such as transmission or generator are charged so that their life and their efficiency due to larger required gap dimensions is adversely affected. Also, such a bearing assembly has a comparatively low rigidity due to the game. Furthermore, such bearings show no optimal rolling behavior, which leads to high friction and thus to increased wear and ultimately to a low life. Due to the different load distributions in the axial direction, the second row of bearings is regularly oversized in a double-row spherical roller bearing, which is disadvantageous from a cost point of view.

Alternatively, two-point bearings with a double-row tapered roller bearing and a cylindrical roller bearing are known. Compared to the spherical roller bearings, these have a lower axial clearance. They are also more tolerant to thermal expansion, since the cylindrical roller bearing is usually realized as a floating bearing. Again, however, the second row of tapered roller bearing is oversized and the cost of the entire storage are relatively high. In addition, there are high demands on an axis-parallel alignment of the rotor shaft with the rotor hub, since cylindrical roller bearings are critical in tilting.

For high-performance wind turbines in the multi-megawatt range, the so-called moment storage is known, as for example from the DE 10 2009 017 865 A1 can be seen. In this is completely dispensed with a second support point and the only one support point is designed as a double-row bearing, such as tapered roller bearings. However, this requires a much larger dimensions of the double row bearing to compensate for the lack of support of the second bearing and to support bending moments from the wind loads reliably.

Since only one bearing point is used, the axial clearance is low, and temperature-related length expansions are less critical. However, the required larger dimensioning of the bearing leads to a significantly higher bearing weight and also to higher costs. The entire dimensions are thereby significantly increased, so that due to the required high electrical power storage dimensions manufacturing limits, for example, at bearing diameters of about equal to 3 to 4 meters are achieved.

In the DE 10 2008 036 217 A1 the rotor shaft is mounted via two axially spaced apart tapered roller bearings in O arrangement on a common bearing housing designed as a carrier unit. The inner rings and the outer rings of the two bearings are held by spacers at a defined distance from each other. To set a desired bearing preload, the sleeves are made in a defined desired length. For this purpose, the bearing unit is mounted during assembly in a complex assembly process, since the exact length required at least one of the sleeves must be measured and adjusted only during assembly of the bearing unit. As a result, the assembly is not least complex due to the high number of parts.

Proceeding from this, the present invention seeks to provide a storage unit for wind turbines, which meets high technical requirements with high efficiency.

The object is achieved according to the invention by a bearing unit having the features of claim 1. The bearing unit extends generally longitudinally along an axis of rotation from a front rotor side to a rear tower side and has a stator unit and a rotor unit, which has a rotor-side bearing and a tower-side Bearings are stored together. Rotor unit and stator form an outer bearing housing and a reaching into this journal. Depending on the configuration, both the rotor unit and the stator unit can form the bearing housing or the bearing journal. The rotor unit has a rotor flange for fastening the rotor hub of the wind turbine, and the stator unit has a stator flange for attachment to a machine carrier of the wind turbine. In the assembled end position in the wind turbine, therefore, the stator is rotatably mounted on the machine frame and thus attached to the tower of the wind turbine, whereas the rotor unit is rotatably mounted together with the rotor hub attached to it about the axis of rotation. The two bearings are arranged spaced from one another in each case in the opposite end regions of the stator or rotor unit, and in each case have two bearing rings, namely an inner ring and an outer ring. Thus, a total of four bearing rings are provided, wherein at least for three of the bearing rings on the rotor unit and the stator each having a fixed axial stop is formed, so that these three bearing rings are held at defined axial positions between the rotor and stator. In the mounted state of the bearing unit, a biasing circuit is thereby formed over the two bearings, as well as the rotor unit and the stator unit, via which a defined preload is generated on the bearings during assembly of the bearing unit.

The fourth bearing ring is preferably used as a bearing clamping ring without an associated stop and is preferably stretched in the longitudinal direction by means of a biasing ring.

The storage unit is therefore designed overall as a prefabricated structural unit, which completely pre-mounted allows the attachment of the rotor hub on the rotor flange and is fastened with its other side to the stator of the wind turbine with the stator. This configuration as a prefabricated unit allows a simple, reproducible and economical installation of this unit already in an assembly hall and avoids assembly steps on the site. For generators (> Ø 4m) for directly driven wind turbines, assembly of individual generator segments is particularly economical for logistical reasons. Here, the individual generator segments can be mounted particularly efficiently on the preassembled bearing unit.

Due to the integrated design with the bearing housing on the one hand and the bearing pin on the other hand, which are supported at their opposite ends by the bearings, a very stiff and backlash-free support of the wind loads is achieved at the same time low load bearing.

Decisive for this is, on the one hand, the largest possible distance between the two bearings. The bearings are each arranged in opposite end regions of the stator and / or the rotor unit and in particular of the bearing housing. This is understood to mean that the bearings are arranged in the outer 30%, preferably 20%, of the longitudinal extent of the respective unit. The bearings are preferably arranged directly on opposite front end sides of at least one of the units (rotor unit or stator unit), in particular of the bearing housing. At a different linear expansion of the two units, the bearings are preferably arranged on the front side of the one unit and the other unit, the one bearing preferably also frontally and the other bearing at least at the opposite end in the outer third. As a result of the resulting reduced bearing load, for example, compared to a momentary bearing with only one, possibly double row Lagerabstützstelle, the bearings can be significantly smaller dimensions, resulting in cost and weight savings.

Furthermore, such an integrated design shows a high dimensional accuracy with low bearing clearance preferably both in the axial and in the radial direction. Decisive for this is in particular the integral design of the bias circuit in the bearing assembly itself. Since the bias is generated and built during assembly of the bearing unit itself, a later adjustment on the site is no longer necessary. Due to the selected configuration with the fixed stops on the stator unit and on the rotor unit on which the bearing rings are supported for the formation of the clamping circuit is - in addition to an optimized force introduction to the formation of the bias circuit - in particular also allows a very simple installation, especially in comparison to the elaborate procedure, as it is from the DE 10 2008 036 217 A1 can be seen. Due to the stops fixedly formed on the rotor or stator unit, the rotor and stator units therefore serve as fixed spacers for the bearings. As a result, the application of the bearing preload is comparatively easy and is preferably carried out with the aid of the biasing ring, the expedient manner is screwed to the front side by means of clamping screws on the rotor unit or stator and applied with a ring flange portion of the bearing clamping ring in the axial direction with a biasing force.

In addition to the two mentioned bearings, the bearing unit preferably has no further bearing, so that overall a comparatively simple structure is achieved.

In an expedient embodiment, the bias in the mounted state of the bearing unit is adjustable. For this example, there is the possibility to adjust the clamping ring by tightening clamping screws in its axial position. By this configuration, even in the final assembled state, when mounted in the wind turbine storage unit, so if this is connected to the rotor hub and machine support, a readjustment of the bias allows. This can still be done, for example, after a few hours of operation after commissioning, or after several years of operation.

With regard to a design that is as rigid as possible, the rotor unit and the stator unit are expediently designed in each case as monolithic components, that is to say as one-piece components. These are in particular metal castings, in particular cast iron (GJS according to DIN EN 1563 , z. GJS 350). In addition to the attacks, in particular, the individual mounting flanges are integral components of these units. Another advantage of this embodiment is the fact that the bearing rings are expediently formed in comparison to these units hochwertigem material, in particular bearing steel.

With regard to the most favorable arrangement of the biasing ring of this total end face and preferably attached to a rotor-side end of the bearing unit.

The distance between the two bearings is chosen as large as possible in order to record the moments as well as possible. Conveniently, the distance between the bearings is at least 0.35 times the maximum bearing diameter. In a conical design of the journal, this is understood to mean the larger outer bearing diameter of the bearing outer ring at the thickened end.

The storage unit is designed for wind power plants with outputs in the multi-megawatt range. Basically, this design principle is also applicable to smaller plants. Generally, in such large-scale facilities, the bearing unit is dimensioned sufficiently large, so that the bearing pin / shaft is inside accessible. Typically, the journal has an (outer) diameter in the range of 2 to 3.5 meters. The assembly has a diameter approximately in the range of 2.5 to 4 meters with a length of about 2 to 3.5 meters. This means that the (largest) outer diameter of the bearing outer rings is approximately between 2 and 3.5 meters. As a result, the distance between the two storage units is at least - depending on the size - 0.7 to 1.2 meters. Preferably, the distance is chosen as large as possible. In particular, the two bearings are each arranged on opposite end sides of the position housing. The distance is then approximately in the range of 0.5 to 0.7 times the outer diameter of the bearing and is - depending on the size - between 1 and 1.75 meters.

The bearing pin, preferably the stator, is formed in an expedient embodiment of a hollow cone and tapers to the rotor side with a fixed journal ( 1 ) and to the machine carrier side with fixed bearing housings ( 2 ). In addition, it is furthermore expediently provided that the bearing housing surrounding the bearing journal, in particular the rotor unit, surrounds the bearing journal in the manner of a clamping arc. The wall of the bearing housing therefore extends in the longitudinal direction not parallel to the wall of the journal, but describes in the broadest sense an arc between the camps. For this purpose, the wall is arc-shaped, at least in some areas. In principle, the span-like configuration can also be formed by rectilinear portions. A particular convex curved course of the wall of the bearing housing in the longitudinal direction is, however, for the transmission of the biasing force to form the bias circuit and to avoid voltage spikes of particular advantage. By this special arcuate configuration, a particularly effective power transmission of the introduced biasing force is achieved by a bearing to the other camp.

Conveniently, in this case, stiffening ribs are arranged on the inside of the bearing housing in the curved arch area, which extend in particular in the longitudinal direction and preferably have a curved-segment-like surface.

The bearings are conveniently tapered roller bearings inclined obliquely to the longitudinal direction, preferably in O-orientation, but alternatively also in X-orientation. Due to the inclination, a suitable force introduction and transmission for the bias circuit is achieved. The individual cones are with respect to the Longitudinal direction, for example, at an angle of 10 ° to 40 ° oriented

In an expedient development, the two spaced bearings are designed for different loads. By this is meant that the two bearings are designed specifically constructive according to the requirements of the respective storage position. Usually, therefore, the tower or machine carrier side bearing is designed for significantly lower loads and is thus usually sized smaller in terms of carrying capacity. This means that the bearing has a lower load rating (static or dynamic, C _o , C). This allows for an optimal adaptation of the entire bearing structure to the expected wind loads. This also allows the rolling behavior of the individual bearing parts to be optimized, as a result of which optimized frictional forces are achieved in order to achieve the least possible friction bearing. In addition, both the bearing weight and the material usage is kept low. This also reduces the manufacturing costs of the storage unit. Due to the different, load-specific design of the bearings, an optimized utilization of the service life reserves of the bearing unit is also achieved overall, since the expected service life are matched to one another, which is not possible with the concept of the moment bearing.

The bearing unit is preferably a total of a tightly sealed system, for which purpose preferably sealing rings are arranged on the outside of the two bearings for sealing purposes. Conveniently, annular bearing caps are also arranged to protect the bearings. This results in a total of a self-contained, sealed and preset unit that can be prepared ready for installation and delivered, for example, to the site of the wind turbine or a specialized operation. This reduces the risk of contamination and damage during assembly and during transport.

In an expedient embodiment, the rotor unit forms the outer bearing housing and the stator unit the inner bearing pin, which is fixedly connected to the machine frame.

Furthermore, the bearing unit is preferably designed for direct, direct attachment to a generator, for which purpose the rotor unit has at least one additional generator flange for attachment to a rotor of the generator. The stator of the generator is preferably attached directly to the stator unit of the bearing unit. The generator expediently surrounds the bearing unit approximately concentrically, which leads to a very space-saving arrangement as a whole. A particular advantage of a prefabricated assembly delivered to the construction site is the possible assembly of individual generator segments directly on the construction site of the wind power plant.

The generator flanges are in particular formed between the rotor flange and the stator flange in order to allow the greatest possible distance between these two flanges and thus between the two bearings.

An embodiment of the invention will be explained in more detail below with reference to FIGS. These show each in partially simplified representations:

1 a fragmentary, greatly simplified representation of a bearing unit in the final mounted position for a generator direct drive,

2 the bearing unit in final mounted position with gearbox connected between bearing unit and generator,

3 a simplified, partial and partial elevation view of a wind turbine with storage unit and directly driven generator,

4 a simplified, perspective partial elevation of the storage unit,

5 the storage unit in a longitudinal section, as well

6 an enlarged view of a portion of the storage unit according to 5 ,

In the figures, like-acting parts are provided with the same reference numerals.

1 and 2 show two highly simplified representations of two embodiments of the arrangement of a storage unit 2 inside a wind turbine. The storage unit 2 extends in the longitudinal direction 4 along a rotation axis R from a front rotor side 6 up to a rear side of the tower 8th , At the front rotor-side front end of the storage unit 2 is the rotor hub 10 attached and in its opposite, tower-side end, it is on a machine carrier 12 attached. The storage unit 2 generally has one with the rotor hub 10 connected rotor unit 14 as well as one with the machine carrier 12 connected stator unit 16 on. rotor unit 14 and stator unit 16 form a bearing housing or a bearing journal of the bearing unit 2 and are together over two Bearings, namely a rotor-side bearing 18A as well as a tower-side warehouse 18B stored together.

In the embodiment according to 1 forms the rotor unit 14 the outer bearing housing and the stator unit 16 the inner bearing pin. In the embodiment of 2 it is vice versa, here forms the rotor unit 14 the trunnion and the stator unit 16 the bearing housing.

Generally, the rotor unit rotates 14 in operation about the axis of rotation R, whereas the stator 16 stationary with the machine carrier 12 connected is. In the embodiment of the 1 is the rotor unit 14 directly with a rotor 20 as well as the stator unit 16 with a stator 22 a generator 24 (see. 3 ) for a direct drive of the generator 24 connected.

In contrast to this is the stator unit 16 in the embodiment according to 2 with a gear unit 26 connected and via an output shaft 28 indirectly via an in 2 not shown generator.

Like from the 1 and 2 shows, the bearing pin has a substantially hollow cone-shaped geometry. In the embodiment of the 1 this is the stator unit 16 extending to the rotor side 6 rejuvenated. Conversely, in the embodiment of the 2 the rotor unit 14 as a bearing journal to the tower side 8th out.

In both cases is at the respective camp 18A . 18B at the tapered end of the journal as a biasing ring 30 formed trained biasing element, which is the respective bearing 18A . 18B longitudinal 4 subjected to a biasing force, so that the entire storage unit 2 is biased and thus mounted without clearance in both the axial direction and in the radial direction. The from the preload ring 30 generated clamping force is on the respective first bearing 18A . 18B on the bearing housing, from there over the opposite second bearing 18B . 18A on the bearing journal and over this again on the first bearing 18A . 18B transferred, leaving a bias circuit 32 is formed by these components, which are exemplified in the 1 and 2 is shown.

At the storage unit 2 with the components rotor unit 14 , Stator unit 16 , Camp 18A . 18B as well as preload ring 30 it is a preassembled unit, so delivered in the assembled state to the site of the wind turbine and there only with the rotor hub 10 and the machine carrier 12 is mounted. In a direct drive variant as in 1 In addition, there is basically the possibility, even the generator already together with the storage unit 2 to deliver pre-assembled.

The entire storage unit 2 has a length L and a maximum diameter D. Furthermore, by the storage unit 2 a _maximum bearing diameter d _max defined by the largest outer diameter of one of the bearings 18A . 18B is defined. The two camps 18A . 18B are spaced apart by a distance A, which is chosen as large as possible and at least 0.35 times the bearing diameter d _max . Preferably, the distance A is between 0.6 and 1 times the bearing diameter d _max

Further details of the embodiment with the direct drive are from the 3 to 6 refer to. 3 shows here a partial cutout from a wind turbine, in which at an upper head of a tower 34 a rotatable and the machine carrier 12 forming nacelle is attached. At this is the storage unit 2 with her stator unit 16 via a stator flange 36 attached. This is an annular end flange encircling the end face. At the opposite end is at the storage unit 2 the rotor hub 10 via a rotor flange 38 attached. At the rotor hub 10 itself rotor blades are attached here in a manner not shown.

Between the stator flange 36 and the rotor flange 38 is still a generator flange 40 on the peripheral side of the rotor unit 14 formed. This is about in the front third of the rotor unit 14 educated. About the generator flange 40 is the rotor 20 of the generator 24 attached. About the stator flange 36 is still the stator 22 , So the generator housing attached.

As in particular from the enlarged view according to 4 it can be seen, it concerns with the two units 14 . 16 in each case by monolithic, one-piece units, preferably cast metal units, in which the individual flanges 36 . 38 . 40 and continue several attacks 42 are formed, in which the bearings 18A . 18B longitudinal 4 support, as will be explained in more detail below. Due to this monolithic configuration, the entire, preloaded storage unit 2 a high rigidity with only minimal bearing clearance. Due to the comparatively large distance A between the two bearings 18A . 18B In addition, the forces are reliably absorbed even in different wind loads both in the axial direction and tilting moments. Due to the non-existent bearing clearance this allows at the same time a mounting of the generator 24 with extremely low generator gap between stator 22 and rotor 20 , so that the efficiency of the generator 24 compared to the use of other warehouse concepts is increased. Decisive for this is the design of the storage unit 2 as a prestressed assembly with the widely spaced bearings 18A . 18B , In addition, for the preload and the generation of high desired stiffness is essential that the attacks 42 at the rotor unit 14 or the stator unit 16 are formed to transfer the biasing forces.

Another significant advantage is to be seen in the small number of parts, whereby the installation is relatively easy.

Like from the 3 and 4 and in greater clarity still from the 5 and 6 it can be seen, the bearing housing (rotor unit 14 ) viewed in cross-section formed slightly arcuate, so that the inner wall of the rotor unit 14 not exactly parallel to the outer wall of the stator unit 16 runs. About arcuate portions of the bearing housing is in each case in the oriented in the radial direction stops 42 above. The bow-shaped design efficiently transfers the preload forces without generating voltage peaks.

For stiffening the bearing housing has this on its inner wall preferably stiffening ribs 44 on ( 5 . 6 ).

As in particular from 6 it is to be understood that these are the camps 18A . 18B Tapered tapered roller bearings, each with an inner ring 46 , an outer ring 48 and have a plurality of tapered rollers as rolling elements. In the embodiment, the bearings 18A . 18B oriented in O-arrangement to each other. Additional bearings are between the rotor unit 14 and the stator unit 16 not arranged. At the tower side warehouse 18B is both the outer ring 48 as well as the inner ring 46 each on one side in the longitudinal direction 4 at a stop 42 supported. At the same time a radial support is achieved. In the area of the stop 42 is both the rotor unit 14 as well as the stator unit 16 Viewed in cross-section each formed approximately L-shaped. In contrast, the rotor-side bearing 18A only the outer ring 48 longitudinal 4 about a stop 42 supported. The inner ring 46 is in contrast in the longitudinal direction 4 easily displaceable and with the help of the preload ring 30 against the tapered rollers 50 for the formation of the bias and the bias circuit 32 braced. This inner ring 46 is therefore designed as a bearing clamping ring. The preload ring 30 This is about a variety of bolts on the stator 16 attached and has an edge over the front side of the stator 16 protruding collar on the ring against the inner ring 46 is pressed. The over the preload ring 30 generated bias is preferably even after the assembly of the storage unit 2 adjustable and adjustable, for example, after a certain number of operating hours to readjust the bias, without any re-assembly or disassembly of the storage unit 2 would be required.

The two camps 18A . 18B are further sealed from the environment, so that even during assembly, a defined amount of bearing lubricant can be introduced, which is tuned, for example, to a certain period of operation or on the life of the bearing. Due to the sealed version is the storage unit 2 Also not susceptible to dirt, for example, during transport or during assembly. For this seal, each bearing has 18A . 18B in the exemplary embodiment, an annular bearing cap 52 on, which in the embodiment of the rotor unit 14 is attached. Furthermore, at least one outer sealing ring 54 in the area of the bearing cap 42 as well as an inner sealing ring 56 provided on the opposite inner side. The inner sealing ring 56 seals the ring contact surface of the respective stop 42 the rotor unit 14 to the outer wall of the stator 16 down. The inner seal is for this purpose in an annular groove.

LIST OF REFERENCE NUMBERS

2

storage unit

4

longitudinal direction

6

rotor side

8th

tower page

10

rotor hub

12

machine support

14

rotor unit

16

stator

18A

rotor-side bearing

18B

tower side bearing

20

Rotor of the generator

22

Stator of the generator

24

generator

26

gear unit

28

output shaft

30

preloading ring

32

biasing circuitry

34

tower

36

stator flange

38

rotor flange

40

generator flange

42

attack

44

stiffening rib

46

inner ring

48

outer ring

50

tapered rollers

52

bearing cap

54

outer seal

56

inner seal

R

axis of rotation

A

distance

L

camp

D

diameter

d _max

Bearing diameter

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

• DE 102008036217 A1 [0002, 0010, 0017]
• DE 60131764 T2 [0006]
• DE 102006037890 A1 [0006]
• DE 102009017865 A1 [0008]

Cited non-patent literature

• DIN EN 1563 [0020]

Claims (13)

Storage unit ( 2 ) for a rotor of a wind turbine projecting in a longitudinal direction ( 4 ) along a rotation axis (R) from a front rotor side ( 6 ) to a rear tower side ( 8th ), with a stator unit ( 16 ) and a rotor unit ( 14 ), which via a rotor-side bearing ( 18A ) and a tower-side bearing ( 18B ) are mounted on each other and form a bearing housing and a journal, wherein the stator ( 16 ) a stator flange ( 36 ) for securing the storage unit ( 2 ) on a machine carrier ( 12 ) of the wind turbine and the rotor unit ( 14 ) a rotor flange ( 38 ) for fastening a rotor hub ( 10 ) at the storage unit ( 2 ) on the wind turbine and the two bearings ( 18A . 18B ) spaced from each other in each case in the opposite end regions of the stator or rotor unit ( 14 . 16 ) are arranged and in each case two bearing rings, namely an inner ring ( 46 ) and an outer ring ( 48 ), characterized in that for three of the bearing rings ( 46 . 48 ) on the rotor unit ( 14 ) and at the stator unit ( 16 ) one fixed stop each ( 42 ) is formed so that over the two camps ( 18A . 18B ), the rotor unit ( 14 ) and the stator unit ( 16 ) a bias circuit ( 32 ) is formed over the during assembly of the storage unit ( 2 ) a defined bias voltage is generated. Storage unit ( 2 ) according to claim 1, characterized in that one of the bearing rings ( 46 . 48 ) without assigned stop ( 42 ) is designed as a bearing clamping ring which in the longitudinal direction ( 4 ) by means of a preload ring ( 30 ) is biased, for which purpose the biasing ring ( 30 ) on the rotor unit ( 14 ) or the stator unit ( 16 ) is attached. Storage unit ( 2 ) according to one of the preceding claims, characterized in that the bias voltage in the mounted state of the bearing unit ( 2 ) is adjustable. Storage unit ( 2 ) according to one of the preceding claims, characterized in that the rotor unit ( 14 ) and the stator unit ( 16 ) are each monolithic components, in which the stops ( 42 ) are formed. Storage unit ( 2 ) according to one of the preceding claims, characterized in that the bearings ( 18A . 18B ) one through the outer diameter of the outer ring ( 46 ) have defined bearing diameter and the distance (A) in the longitudinal direction ( 4 ) between the camps ( 18A . 18B ) equals at least 0.35 times the largest bearing diameter (d _max ). Storage unit ( 2 ) according to one of the preceding claims, characterized in that the bearing pin is formed in a hollow cone shape. Storage unit ( 2 ) according to one of the preceding claims, characterized in that viewed in a longitudinal cross section, the bearing housing is formed in relation to the bearing pin in the manner of a clamping arc. Storage unit ( 2 ) according to any one of the preceding claims, characterized in that the bearings ( 18A . 18B ) at an angle to the longitudinal direction ( 4 ) is tapered roller bearings. Storage unit ( 2 ) according to one of the preceding claims, characterized in that the two bearings ( 18A . 18B ) are designed for different loads. Storage unit ( 2 ) according to one of the preceding claims, characterized in that it has an outwardly sealed sealing system and at the two bearings ( 18A . 18B ) to the rotor side ( 6 ) and to the tower side ( 8th ) Seals ( 54 . 56 ) are arranged. Storage unit ( 2 ) according to one of the preceding claims, characterized in that the rotor unit ( 14 ) forms the outer bearing housing. Storage unit ( 2 ) according to one of the preceding claims, characterized in that it can be attached directly to a generator ( 24 ) is formed and for this purpose the rotor unit ( 14 ) an additional generator flange ( 40 ) for attachment to a rotor ( 20 ) of the generator ( 24 ) having. Storage unit ( 2 ) according to claim 12, characterized in that preferably a plurality of generator flanges ( 40 ) between the rotor flange ( 38 ) and the stator flange ( 36 ) are arranged.

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