Nacelle for wind turbine

Abstract

The present invention relates to a nacelle for a wind turbine generator, the nacelle comprising a nacelle housing (4), a rotor shaft (13), a rotor hub (6) arranged on the rotor shaft (13), a first rotor shaft bearing (8) and a second rotor shaft bearing (9) for supporting the rotor shaft (13) on the nacelle housing (4), the first rotor shaft bearing (8) and the second rotor shaft bearing (9) being arranged opposite each other with an axial distance (44) between them, and the first rotor shaft bearing (8) being arranged closer to the rotor hub (6) than the second rotor shaft bearing (9). The first rotor shaft bearing (8) includes a first sliding surface (22) having a first average sliding surface diameter (24), the second rotor shaft bearing (9) includes a second sliding surface (35) having a second average sliding surface diameter (37), the first sliding surface (22) at least partially facing away from the rotor hub (6), and the first sliding surface (22) and the second sliding surface (35) at least partially facing each other.

Description

[Technical field]

[0001] The present invention relates to a nacelle for a wind turbine generator. [Background technology]

[0002] Patent Document 1 discloses a wind turbine generator having a nacelle including a nacelle housing, a rotor shaft, a rotor hub, and first and second rolling bearings for supporting the rotor shaft in the nacelle housing.

[0003] The wind power generator known from DE 10 200 03 133 A1 has the drawback that the bearings of the rotor shaft do not adequately meet the high demands of a wind power generator. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] European Patent Application Publication No. 3783237(A1) Summary of the Invention [Problem to be solved by the invention]

[0005] SUMMARY OF THE PRESENT EMBODIMENT It is an object of the present invention to overcome the drawbacks of the prior art and to provide a nacelle for a wind turbine generator having an improved bearing. [Means for solving the problem]

[0006] The above problems are solved by an apparatus and method according to the claims.

[0007] According to the invention a nacelle for a wind turbine generator is designed, said nacelle comprising: A nacelle housing; A rotor shaft; A rotor hub disposed on the rotor shaft; a first rotor shaft bearing for supporting the rotor shaft in the nacelle housing; a second rotor shaft bearing for supporting the rotor shaft in the nacelle housing; The first rotor shaft bearing and the second rotor shaft bearing are disposed opposite each other with an axial distance therebetween, and the first rotor shaft bearing is disposed closer to the rotor hub than the second rotor shaft bearing.

[0008] The first rotor shaft bearing includes a first sliding surface having a first average sliding surface diameter, and the second rotor shaft bearing includes a second sliding surface having a second average sliding surface diameter, the first sliding surface at least partially facing away from the rotor hub and the first and second sliding surfaces at least partially facing one another.

[0009] In particular, the first rotor shaft bearing and the second rotor shaft bearing can be designed as independent plain bearings.

[0010] The nacelle according to the invention has the advantage that the first rotor shaft bearing and the second rotor shaft bearing are designed as plain bearings. The arrangement according to the invention of the first and second sliding surfaces relative to each other or relative to the rotor hub allows a particularly efficient absorption or transmission of axial loads caused by wind forces or tilting moments caused by the weight of the rotor hub. The arrangement according to the invention thus achieves a surprisingly good suitability for use in nacelles for wind power generators. The first sliding surface at least partially facing away from the rotor hub means that the tangent to the sliding surface at at least one specific point is inclined away from the rotor hub.

[0011] Furthermore, the first sliding surface has a first average sliding surface diameter, and the axial distance between the first and second rotor shaft bearings is measured from the innermost contact point of the first sliding surface to the innermost contact point of the second sliding surface, where said axial distance is advantageously 20% to 1000%, in particular 50% to 500%, preferably 90% to 300%, particularly preferably 120% to 200% of the first average sliding surface diameter. The first average sliding surface diameter is a diameter corresponding to the average of the areal areas on the first sliding surface. The innermost contact point of the first sliding surface and the innermost contact point of the second sliding surface are the points at which the respective sliding surfaces are still in contact with their respective counter surfaces and are located closest to each other.

[0012] Furthermore, the first sliding surface is formed conically and the second sliding surface is formed conically, where the first and second sliding surfaces are arranged in a V-shape relative to one another, which entails the advantage that sliding surfaces designed in this way are easy to manufacture.

[0013] In an alternative embodiment, the first sliding surface is formed in a first spherical crown shape and the second sliding surface is formed in a second spherical crown shape, the first sliding surface forms a first spherical crown arc in a longitudinal section and the second sliding surface forms a second spherical crown arc in a longitudinal section, and the first tangent to the center of the first spherical crown arc and the second tangent to the center of the second spherical crown arc are arranged in a V-shape with respect to each other. In particular, such a design of the first and second sliding surfaces allows a good transmission of axial forces while at the same time absorbing radial forces and tilting moments exerted by the rotor hub.

[0014] Also advantageous is an arrangement in which the first rotor shaft bearing has a first outer ring, the second rotor shaft bearing has a second outer ring, the first rotor shaft bearing has a first inner ring, the second rotor shaft bearing has a second inner ring, the first sliding surface is arranged between the first outer ring and the first inner ring, the second sliding surface is arranged between the second outer ring and the second inner ring, the first outer ring and the second outer ring are arranged in a fixed position relative to each other, the first inner ring is arranged in a fixed position relative to the rotor shaft, and the second inner ring or the second plain bearing element is preloaded axially towards the first inner ring by a tensioning means, which acts between the second inner ring and the rotor shaft. In particular, such a design of the first and second sliding surfaces allows a good transmission of axial forces while at the same time absorbing radial forces and tilting moments exerted by the rotor hub.

[0015] In an alternative embodiment, it is also conceivable that the two inner rings are arranged at a fixed distance from each other in their axial position. In order to preload the axial direction, the two outer rings or the two bearing blocks are movable relative to each other. In particular, it is also conceivable that the first bearing block is fixed and that the second bearing block is moved away from the first bearing block or clamped in order to preload the bearing.

[0016] According to another embodiment, the tensioning means is formed in the form of a shaft nut. This has the advantage that the two inner rings can be accurately positioned relative to each other by means of the shaft nut in order to achieve the required preload of the plain bearing. Furthermore, it is conceivable to tighten the shaft nut with a predefined tightening torque in order to achieve a predefined preload.

[0017] It is furthermore conceivable that a spring element is arranged between the tension means and the second inner ring or between the tension means and the second plain bearing pad, with the advantage that any thermal expansion and also to a certain extent wear can be compensated by the spring element.

[0018] It is furthermore advantageous if a transmission is formed torque-coupled to the rotor shaft, the weight of which is at least partially borne by the second rotor shaft bearing, which has the advantage that no separate bearing is required to support the transmission.

[0019] Furthermore, the first rotor shaft bearing and / or the second rotor shaft bearing can be designed to additionally bear the weight of the generator, which has the advantage that no separate bearing is required to support the generator.

[0020] Furthermore, the first sliding surface and / or the second sliding surface can be formed on the plain bearing pad. This has the advantage that the plain bearing pad is easily inserted into the plain bearing and can be easily replaced. Furthermore, the plain bearing pad has a precise sliding surface and can be easily manufactured in an industrial process.

[0021] Furthermore, it can be provided that the first mean sliding surface diameter is larger than the second mean sliding surface diameter, in particular that the second mean sliding surface diameter is 50% to 90%, preferably 70% to 80%, of the first mean sliding surface diameter. This has the advantage that the first rotor shaft bearing, which experiences increased axial forces and increased radial forces compared to the second rotor shaft bearing, is dimensioned larger in response to this uneven force distribution, whereby an optimal force absorption can be achieved.

[0022] According to a special configuration, the first outer ring can be accommodated in a first bearing block and the second outer ring can be accommodated in a second bearing block, which allows the first and second rotor shaft bearings to be designed separately and independently of each other.

[0023] The second bearing block can be designed to be integrated into the transmission.

[0024] It is also conceivable to design the first rotor shaft bearing and the second rotor shaft bearing as hydrodynamic plain bearings. Alternatively, it is conceivable to design the first rotor shaft bearing and the second rotor shaft bearing as hydrostatic plain bearings. A respective independent lubricating oil pump can be provided to supply lubricating oil to the first rotor shaft bearing and the second rotor shaft bearing. In an alternative embodiment, it is also conceivable to supply lubricating oil to the first rotor shaft bearing and the second rotor shaft bearing by a common lubricating oil pump.

[0025] For a better understanding of the invention, it will now be explained in more detail with the aid of the following figures.

[0026] The figure is a highly simplified schematic diagram. [Brief description of the drawings]

[0027] [Figure 1] FIG. 1 is a schematic diagram of a wind turbine generator. [Diagram 2] FIG. 2 is a longitudinal section of a first embodiment of a sliding bearing. [Diagram 3] FIG. 3 is a longitudinal section of a second embodiment of the sliding bearing. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0028] It should be noted at the outset that the same elements in the different embodiments described are given the same reference numbers or names. In this case, the disclosure contained in the entire description applies mutatis mutandis to the same elements having the same reference numbers or names. Positional terms selected in the description, such as top, bottom, side, etc., also refer directly to the described and displayed figures, and these positional terms apply mutatis mutandis to the new positions when the positions are changed.

[0029] 1 shows a schematic diagram of a first embodiment of a wind turbine 1 for generating electrical energy from wind energy. The wind turbine 1 comprises a nacelle 2 which is rotatably held on a tower 3. The nacelle 2 comprises a nacelle housing 4 which constitutes the main structure of the nacelle 2. In the nacelle housing 4 of the nacelle 2, electrical components, such as for example a generator, of the wind turbine 1 are arranged.

[0030] Further, a rotor 5 is formed having a rotor hub 6 and rotor blades 7 attached thereto. The rotor hub 6 is considered to be part of the nacelle. The rotor hub 6 is rotatably held in the nacelle housing 4 by a first rotor shaft bearing 8 and a second rotor shaft bearing 9. In particular, the rotor hub 6 is disposed on a rotor shaft 13, which is supported by the first rotor shaft bearing 8 and the second rotor shaft bearing 9.

[0031] The first rotor shaft bearing 8 and the second rotor shaft bearing 9 are designed to absorb radial forces 10 and axial forces 11. The axial forces 11 arise due to wind forces. The radial forces 10 arise due to the gravity of the rotor and act on the centre of gravity of the rotor 5. As the centre of gravity of the rotor 5 is located outside the first rotor shaft bearing 8, the radial forces 10 induce a tilting moment 12 in the rotor shaft bearing 8, which can be absorbed by the first rotor shaft bearing 8 and the second rotor shaft bearing 9. The tilting moment 12 can also be caused by uneven loading of the rotor blades 7.

[0032] Further, there is provided a transmission 14 coupled to the rotor shaft 13. The transmission 14 can be coupled to the rotor shaft 13 such that it is also supported by the first rotor shaft bearing 8 and the second rotor shaft bearing 9.

[0033] Additionally, a generator 15 coupled to the transmission 14 may be provided.

[0034] As is further apparent from FIG. 1, the first rotor shaft bearing 8 may be located closer to the rotor hub 6 than the second rotor shaft bearing 9 .

[0035] Furthermore, the second rotor shaft bearing 9 is arranged closer to the generator 15 than the first rotor shaft bearing 8. Furthermore, the first rotor shaft bearing 8 and / or the second rotor shaft bearing 9 are designed to additionally absorb the weight of the generator 15.

[0036] FIG. 2 shows a first embodiment of a first rotor shaft bearing 8 and a second rotor shaft bearing 9 mounted in a nacelle 2 in a longitudinal section.

[0037] As can be seen from Figure 2, the first rotor shaft bearing 8 can have a first inner ring 16 and a first outer ring 17. A first plain bearing element 18 can be arranged between the first inner ring 16 and the first outer ring 17, which first plain bearing element 18 is used for the rotational plain bearing of the first inner ring 16 relative to the first outer ring 17.

[0038] 2, the first inner ring 16 can be formed directly on the rotor shaft 13. It is further contemplated that the first inner ring 16 can be formed as a separate member carried by the rotor shaft 13.

[0039] Furthermore, the first outer ring 17 can be accommodated in a first bearing block 19. In particular, the first bearing block 19 can be connected to the nacelle housing 4 or, alternatively, directly molded into the nacelle housing 4. Thus, in this embodiment, the first outer ring 17 is rigidly connected to the nacelle housing 4, and the first inner ring 16 can be rotatable relative to the first outer ring 17 about the rotation axis 20 by means of the first plain bearing element 18.

[0040] Furthermore, the first bearing block 19 can directly function as the first outer ring 17 .

[0041] Furthermore, the first plain bearing element 18 comprises a plurality of individual first plain bearing pads 21 arranged circumferentially distributed between the first inner ring 16 and the first outer ring 17 .

[0042] In the operating state, each first plain bearing pad 21 can be rigidly connected to the first inner ring 16 and can thus rotate together with this first inner ring 16 relative to the first outer ring 17. To enable a rotational movement between the first inner ring 16 and the first outer ring 17, each first plain bearing pad 21 is formed with a first sliding surface 22 which rests against a first counter surface 23 of the first outer ring 17. This first counter surface 23 can be arranged on the inside of the first outer ring 17.

[0043] The first sliding surface 22 of the first plain bearing pad 21 and the first mating surface 23 of the first outer ring 17 are formed as sliding surfaces that slide against each other while the wind power generator 1 is in operation.

[0044] In particular, it can be provided that the first counter surface 23 of the first outer ring 17 is formed as a hard, wear-resistant surface, which can be produced, for example, from hardened steel. The first sliding surface 22 of the first plain bearing pad 21 can be formed of a softer plain bearing material compared to the first counter surface 23. Of course, it is also conceivable that the first sliding surface 22 has a sliding coating layer.

[0045] As is particularly clear from FIG. 2, each of the first plain bearing pads 21 can have a first sliding surface 22 that is curved when viewed in the axial direction.

[0046] Additionally, first sliding surface 22 can have a first average sliding surface diameter 24. First average sliding surface diameter 24 is the average of the diameters of first sliding surface 22 over the entire length of sliding surface 22.

[0047] The first sliding surface 22 has an innermost contact point 25. The innermost contact point 25 of the first sliding surface 22 is the point of the first sliding surface 22 where the first mating surface 23 is still in contact with the first sliding surface 22 and is located closest to the second rotor shaft bearing 9.

[0048] As can be further seen from Figure 2, the first sliding surface 22 of the first plain bearing pad 21 can be formed in a spherical crown shape. In particular, the first sliding surface 22 can be formed in a longitudinal section as a first spherical crown arc 26.

[0049] A first tangent 27 to the first sliding surface 22 at the center 28 of the first spherical crown arc may be disposed at a first angle 29 relative to the axis of rotation 20 .

[0050] As is apparent from Figure 2, the second rotor shaft bearing 9 may have a second inner ring 30 and a second outer ring 31. Between the second inner ring 30 and the second outer ring 31, a second plain bearing element 32 may be arranged, which acts as a plain bearing to rotate the second inner ring 30 relative to the second outer ring 31.

[0051] 2, the second inner ring 30 can be formed directly on the rotor shaft 13. It is further contemplated that the second inner ring 30 can be formed as a separate member carried by the rotor shaft 13.

[0052] Furthermore, the second outer ring 31 can be accommodated in a second bearing block 33. In particular, the second bearing block 33 can be connected to the nacelle housing 4 or, alternatively, directly molded into the nacelle housing 4. Thus, in this embodiment, the second outer ring 31 is rigidly connected to the nacelle housing 4, and the second inner ring 30 can be rotatable relative to the second outer ring 31 about the rotation axis 20 by means of the second plain bearing element 32.

[0053] Furthermore, the second bearing block 33 can directly function as the second outer ring 31 .

[0054] Furthermore, the second plain bearing element 32 includes a plurality of individual second plain bearing pads 34 arranged circumferentially distributed between the second inner ring 30 and the second outer ring 31 .

[0055] Each second plain bearing pad 34 can be rigidly connected to the second inner ring 30 in the operating state and can thus rotate together with this second inner ring 30 relative to the second outer ring 31. To enable a rotational movement between the second inner ring 30 and the second outer ring 31, each second plain bearing pad 34 is formed with a second sliding surface 35 which rests against a second counter surface 36 of the second outer ring 31. This second counter surface 36 can be arranged on the inside of the second outer ring 31.

[0056] The second sliding surface 35 of the second plain bearing pad 34 and the second mating surface 36 of the second outer ring 31 are formed as sliding surfaces that slide against each other while the wind power generator 1 is in operation.

[0057] In particular, the second counter surface 36 of the second outer ring 31 can be formed as a hard, wear-resistant surface, which can be produced, for example, from hardened steel. The second sliding surface 35 of the second plain bearing pad 34 can be formed of a softer plain bearing material compared to the second counter surface 36. Of course, it is also conceivable for the second sliding surface 35 to have a sliding coating layer.

[0058] As is particularly clear from FIG. 2, each of the second plain bearing pads 34 can have a second sliding surface 35 that is curved when viewed in the axial direction.

[0059] Additionally, the second sliding surface 35 can have a second average sliding surface diameter 37. The second average sliding surface diameter 37 is the average of the diameters of the second sliding surface 35 over the entire length of the second sliding surface 35.

[0060] The second sliding surface 35 has an innermost contact point 38. The innermost contact point 38 of the second sliding surface 35 is the point of the second sliding surface 35 where the second mating surface 36 is still in contact with the second sliding surface 35 and is located closest to the first rotor shaft bearing 8.

[0061] As can be seen further from Figure 2, the second sliding surface 35 of the second plain bearing pad 34 can be formed in a spherical crown shape. In particular, the second sliding surface 35 can be formed in a longitudinal section as a second spherical crown arc 39.

[0062] A second tangent 41 to the second sliding surface 35 at the second crown arc center 40 may be disposed at a second angle 42 relative to the axis of rotation 20 .

[0063] As further apparent from Fig. 2, the first tangent 27 and the second tangent 41 can be arranged in a V-shape with respect to one another. In other words, the first angle 29 can be measured on the side of the rotor hub 6. The second angle 42 can be measured on the side opposite the rotor hub. It is furthermore conceivable that the first angle 29 and the second angle 42 are of the same magnitude, in which case the V-shape arises due to the difference in the measuring sides.

[0064] Furthermore, it can be provided that the second plain bearing pad 34 is preloaded axially towards the first rotor shaft bearing 8 by tensioning means 43. The above-mentioned structure or preloading by tensioning means 43 results in an O-shaped arrangement of the first rotor shaft bearing 8 and the second rotor shaft bearing 9, which can absorb radial forces, axial forces and tilting moments.

[0065] As can be further seen in FIG. 2, the innermost contact point 25 of the first sliding surface 22 and the innermost contact point 38 of the second sliding surface 35 are disposed an axial distance 44 from each other.

[0066] In an alternative embodiment, not shown, it is of course also possible to design the first inner ring 16 and the second inner ring 30 as separate components. In such an embodiment, the tensioning means 43 can act directly on the second inner ring 30.

[0067] Fig. 3 shows another embodiment of the first rotor shaft bearing 8 or the second rotor shaft bearing 9 of the wind power generator 1. As is evident from Fig. 3, the first sliding surface 22 or the second sliding surface 35 can be conically shaped. In the longitudinal section, the first sliding surface 22 and the second sliding surface 35 are shown as straight lines. Thus, as is further evident from Fig. 3, the first sliding surface 22 and the second sliding surface 35 can be V-shaped relative to one another. In particular, the first sliding surface 22 and the second sliding surface 35 can be facing one another.

[0068] As is further apparent from FIG. 3, the tensioning means 43 can be pressed directly against or act on the second inner ring 30 .

[0069] The examples show possible embodiments, and it is to be noted here that the invention is not limited to the specifically shown embodiments, but on the contrary, the individual embodiments can also be combined with one another in various ways, this variation being within the capabilities of a person skilled in the art based on the teachings of the technical practice of the invention.

[0070] The scope of protection is defined by the claims. However, in order to interpret the claims, the detailed description and the drawings must be taken into account. Individual features or combinations of features described in the different embodiments shown and described may constitute independent inventive solutions in themselves. The problems underlying these independent inventive solutions can be read off from this description.

[0071] In the description of the invention, all references to ranges of values ​​should be understood to include any and all subranges within that range, for example, a reference of 1 to 10 should be understood to include all subranges from a lower limit of 1 to an upper limit of 10, i.e. all subranges beginning at a lower limit of 1 or more and ending at an upper limit of 10 or less, such as, for example, 1 to 1.7 or 3.2 to 8.1 or 5.5 to 10.

[0072] Finally, as a matter of formality, some elements have been represented not to scale and / or enlarged and / or reduced in size in order to make the structure easier to understand. [Explanation of symbols]

[0073] 1. Wind turbine 2. Nacelle 3. Tower 4 Nacelle housing 5 Rotor 6 Rotor hub 7 Rotor Blades 8 First rotor shaft bearing 9 Second rotor shaft bearing 10 Radial force 11 Axial force 12 Tilting moment 13 Rotor shaft 14. Transmission 15. Generator 16 The First Inner Circle 17 First outer wheel 18 First plain bearing element 19 First bearing block 20 Rotation axis 21 First plain bearing pad 22 First sliding surface 23 First Counterface 24 First average sliding surface diameter 25 Innermost contact point of the first sliding surface 26 First crown arc 27 First Tangent 28 Center of the first crown arc 29 First Angle 30 The second inner circle 31 Second outer wheel 32 Second plain bearing element 33 Second bearing block 34 Second plain bearing pad 35 Second sliding surface 36 Second mating surface 37 Second mean sliding surface diameter 38 Innermost contact point of the second sliding surface 39 Second crown arc 40 Center of the second crown arc 41 Second Tangent 42 Second Angle 43 Tension means 44 Axial distance

Claims

1. A nacelle (2) for a wind turbine generator (1), the nacelle (2) comprising: A nacelle housing (4); A rotor shaft (13); a rotor hub (6) disposed on the rotor shaft (13); a first rotor shaft bearing (8) for supporting the rotor shaft (13) in the nacelle housing (4); a second rotor shaft bearing (9) for supporting the rotor shaft (13) in the nacelle housing (4); A nacelle (2), wherein the first rotor shaft bearing (8) and the second rotor shaft bearing (9) are disposed at an axial distance (44) from each other, and the first rotor shaft bearing (8) is disposed closer to the rotor hub (6) than the second rotor shaft bearing (9), nacelle (2), characterized in that the first rotor shaft bearing (8) has a first sliding surface (22) having a first average sliding surface diameter (24), and the second rotor shaft bearing (9) has a second sliding surface (35) having a second average sliding surface diameter (37), the first sliding surface (22) at least partially facing away from the rotor hub (6), and the first sliding surface (22) and the second sliding surface (35) at least partially facing each other.

2. 2. A nacelle (2) according to claim 1, characterized in that the first sliding surface (22) has a first average sliding surface diameter (24), the axial distance (44) between the first rotor shaft bearing (8) and the second rotor shaft bearing (9) is measured from an innermost contact point (25) of the first sliding surface (22) to an innermost contact point (38) of the second sliding surface (35), and the axial distance (44) is 20% to 1000%, in particular 50% to 500%, preferably 90% to 300%, particularly preferably 120% to 200% of the first average sliding surface diameter (24).

3. 3. The nacelle (2) according to claim 1 or 2, characterized in that the first sliding surface (22) is formed in a conical shape, the second sliding surface (35) is formed in a conical shape, and the first sliding surface (22) and the second sliding surface (35) are arranged to form a V-shape with respect to each other.

4. 3. The nacelle (2) according to claim 1 or 2, characterized in that the first sliding surface (22) is formed in the shape of a first spherical crown, the second sliding surface (35) is formed in the shape of a second spherical crown, the first sliding surface (22) forms a first spherical crown arc (26) in a longitudinal section, the second sliding surface (35) forms a second spherical crown arc (39) in a longitudinal section, and a first tangent (27) at a center (28) of the first spherical crown arc and a second tangent (41) at a center (40) of the second spherical crown arc are arranged to mutually form a V-shape.

5. The first rotor shaft bearing (8) has a first outer ring (17), the second rotor shaft bearing (9) has a second outer ring (31), the first rotor shaft bearing (8) has a first inner ring (16), the second rotor shaft bearing (9) has a second inner ring (30), the first sliding surface (22) is disposed between the first outer ring (17) and the first inner ring (16), and the second sliding surface (35) is disposed between the second outer ring (31) and the second inner ring (30).

2. A nacelle (2) according to claim 1, characterized in that the first outer ring (17) and the second outer ring (31) are arranged in a fixed position relative to each other, the first inner ring (16) is arranged in a fixed position relative to the rotor shaft (13), and the second inner ring (30) or the second plain bearing element (32) is axially prestressed towards the first inner ring (16) by tensioning means (43), the tensioning means (43) acting between the second inner ring (30) and the rotor shaft (13).

6. The nacelle (2) according to claim 5, characterized in that the tensioning means (43) are made in the form of a shaft nut.

7. 2. The nacelle (2) according to claim 1, further comprising a transmission (14) torque-coupled to the rotor shaft (13), the weight of which is at least partially borne by the second rotor shaft bearing (9).

8. 2. The nacelle (2) according to claim 1, characterized in that the first sliding surface (22) and / or the second sliding surface (35) are formed on a plain bearing pad (21).

9. The nacelle (2) according to claim 1, characterized in that the first average sliding surface diameter (24) is larger than the second average sliding surface diameter (37), in particular the second average sliding surface diameter (37) is 50% to 90%, preferably 70% to 80% of the first average sliding surface diameter (24).

10. 7. The nacelle (2) according to claim 5 or 6, characterized in that the first outer ring (17) is housed in a first bearing block (19) and the second outer ring (31) is housed in a second bearing block (33).

Images