GONDOLA FOR A WIND POWER PLANT

Description

[0001] The invention relates to a gondola for a wind turbine.

[0002] EP3783237A1 discloses a wind turbine with a nacelle comprising a nacelle housing, a rotor shaft, a rotor hub and a first and second rolling bearing for supporting the rotor shaft on the nacelle housing.

[0003] The wind turbine known from EP3783237A1 has the disadvantage that the rotor shaft bearing does not adequately meet the high requirements for wind turbines. Further bearings for rotor shafts of wind turbines are known from WO 2020 / 232495 A1, which discloses the features of the preamble of claim 1, EP 3 783 237 A1, WO 2018 / 071941 A1, WO 2018 / 095452 A1, and WO 2015 / 091407 A2. US 3,709,573 A discloses another bearing. The object of the present invention was to overcome the disadvantages of the prior art and to provide a nacelle for a wind turbine which has an improved bearing.

[0004] This problem is solved by a device and a method according to the claims. According to the invention, a nacelle for a wind turbine is designed. The nacelle comprises: a nacelle housing; a rotor shaft; a rotor hub arranged on the rotor shaft; a first rotor shaft bearing for supporting the rotor shaft on the nacelle housing, a second rotor shaft bearing for supporting the rotor shaft on the nacelle housing, wherein the first rotor shaft bearing and the second rotor shaft bearing are arranged at an axial distance from each other and wherein the first rotor shaft bearing is arranged closer to the rotor hub than the second rotor shaft bearing.

[0005] The first rotor shaft bearing has a first sliding surface which has an average first sliding surface diameter. The second rotor shaft bearing has a second sliding surface which has an average second sliding surface diameter, wherein the first sliding surface faces away from the rotor hub at least partially, and wherein the first sliding surface and the second sliding surface face each other at least partially.

[0006] In particular, it may be provided that the first rotor shaft bearing and the second rotor shaft bearing are designed as independent sliding bearings.

[0007] The nacelle according to the invention offers the advantage that the first and second rotor shaft bearings are designed as sliding bearings. Due to the arrangement of the first and second sliding surfaces relative to each other and to the rotor hub according to the invention, axial loads caused by wind force and tilting moments caused by the weight of the rotor hub can be absorbed and transmitted particularly efficiently. Thus, the arrangement according to the invention achieves surprisingly good suitability for use in a wind turbine nacelle. The fact that the first sliding surface is mostly partially oriented away from the rotor hub means that at least at a certain point, a tangent applied to the sliding surface is tilted away from the rotor hub.

[0008] Furthermore, it can be advantageous for the first sliding surface to have an average first sliding surface diameter, and for the axial distance between the first rotor shaft bearing and the second rotor shaft bearing to be measured from the innermost contact point of the first sliding surface to the innermost contact point of the second sliding surface, wherein the axial distance is between 20% and 1,000%, in particular between 50% and 500%, preferably between 90% and 300%, and specifically between 120% and 200% of the average first sliding surface diameter. The average first sliding surface diameter is the diameter that is in contact with the surface on average over the first sliding surface. The innermost contact point of the first sliding surface and the innermost contact point of the second sliding surface are those points at which the respective sliding surface still makes contact with the respective mating surface and which are located closest to each other.

[0009] Furthermore, it can be provided that the first sliding surface is conical and that the second sliding surface is also conical, with the first and second sliding surfaces arranged in a V-shape relative to each other. This has the advantage that sliding surfaces of this design are easy to manufacture.

[0010] In an alternative embodiment, the first sliding surface can be designed in the form of a first spherical cap, and the second sliding surface in the form of a second spherical cap. In longitudinal section, the first sliding surface forms a first arc of the spherical cap, and in longitudinal section, the second sliding surface forms a second arc of the spherical cap. A first tangent at the center of the first arc of the spherical cap and a second tangent at the center of the second arc of the spherical cap are arranged in a V-shape relative to each other. This design of the first and second sliding surfaces, in particular, provides good transmission of axial forces while simultaneously absorbing the radial forces and buckling moments applied by the rotor hub.

[0011] An advantageous embodiment also includes the provision that 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, and the second rotor shaft bearing has a second inner ring, wherein the first sliding surface is arranged between the first outer ring and the first inner ring, and wherein the second sliding surface is arranged between the second outer ring and the second inner ring, wherein the first outer ring and the second outer ring are fixed in their respective positions, and wherein the first inner ring is fixed in its position relative to the rotor shaft, and wherein the second inner ring or a second sliding bearing element is axially preloaded towards the first inner ring by means of a clamping device, the clamping device acting between the second inner ring and the rotor shaft.In particular, such a design of the first sliding surface and the second sliding surface results in good transmission of axial forces while simultaneously absorbing the radial forces and tilting moments applied by the rotor hub.

[0012] In an alternative design, it is also conceivable that the two inner rings are arranged at a fixed distance from each other in their axial position. For axial preloading, the two outer rings or the two bearing blocks can be displaceable relative to each other. In particular, it is conceivable that the first bearing block is fixed and, to preload the bearing, the second bearing block is moved or tensioned away from the first bearing block.

[0013] According to further training, the clamping device can be designed in the form of a shaft nut. This offers the advantage that the two inner rings can be precisely positioned relative to each other using a shaft nut to achieve the necessary preload of the sliding bearing. Furthermore, it is conceivable that the shaft nut can be tightened with a predefined torque to achieve a defined preload.

[0014] Furthermore, it is conceivable that a spring element is arranged between the clamping device and the second inner ring, or between the clamping device and the second sliding bearing pads. This has the advantage that any thermal expansion and, to a lesser extent, wear can be compensated for by the spring element.

[0015] Furthermore, it can be advantageous to design a gearbox that is torque-coupled to the rotor shaft, with the weight of the gearbox being at least partially supported by the second rotor shaft bearing. This has the advantage that no separate bearing is required for the gearbox.

[0016] Furthermore, the first rotor shaft bearing and / or the second rotor shaft bearing may be designed to additionally support the weight of the generator. This has the advantage that no separate bearing is required for supporting the generator.

[0017] Furthermore, the first and / or second sliding surface can be designed as sliding bearing pads. This offers the advantage that sliding bearing pads are easy to insert into the sliding bearing and easy to replace. In addition, sliding bearing pads have a precise sliding surface and are easy to manufacture in an industrial process.

[0018] Furthermore, it can be provided that the average first sliding surface diameter is larger than the average second sliding surface diameter, in particular that the average second sliding surface diameter is between 50% and 90%, preferably between 70% and 80%, of the average first sliding surface diameter. This has the advantage that the first rotor shaft bearing, which experiences increased axial and radial forces compared to the second rotor shaft bearing, can be dimensioned larger to accommodate this uneven force distribution, thereby achieving optimal force absorption.

[0019] In a particular embodiment, it is possible for the first outer ring to be held in a first bearing block and the second outer ring to be held in a second bearing block. This allows the first rotor shaft bearing and the second rotor shaft bearing to be designed independently of each other.

[0020] Furthermore, it may be provided that the second bearing block is integrated into a gearbox.

[0021] Furthermore, it is conceivable that the first and second rotor shaft bearings are designed as hydrodynamic plain bearings. Alternatively, it is also conceivable that the first and second rotor shaft bearings are designed as hydrostatic plain bearings. A separate lubricating oil pump can be provided for each of the first and second rotor shaft bearings. In an alternative design, it is also conceivable that the first and second rotor shaft bearings are supplied with lubricating oil by a single lubricating oil pump.

[0022] To better understand the invention, it is explained in more detail with reference to the following figures.

[0023] They each show, in a highly simplified, schematic representation: Fig. 1 a schematic representation of a wind turbine; Fig. 2 a longitudinal section of a first embodiment of the sliding bearing; Fig. 3 a longitudinal section of a second embodiment of the sliding bearing.

[0024] It should be noted at the outset that in the differently described embodiments, identical parts are provided with the same reference numerals or component designations, and the disclosures contained in the entire description can be applied analogously to identical parts with the same reference numerals or component designations. Furthermore, the positional designations chosen in the description, such as top, bottom, side, etc., refer to the figure directly described and illustrated, and these positional designations must be applied analogously to the new position if the position changes.

[0025] Fig. 1Figure 1 shows a schematic representation of a first embodiment of a wind turbine 1 for generating electrical energy from wind power. The wind turbine 1 comprises a nacelle 2, which is rotatably mounted on a tower 3. The nacelle 2 includes a nacelle housing 4, which forms the main structure of the nacelle 2. The electrotechnical components, such as a generator of the wind turbine 1, are arranged in the nacelle housing 4 of the nacelle 2.

[0026] Furthermore, a rotor 5 is formed, which has a rotor hub 6 with rotor blades 7 arranged on it. The rotor hub 6 is considered part of the nacelle 2. The rotor hub 6 can be rotatably mounted on the nacelle housing 4 by means of a first rotor shaft bearing 8 and a second rotor shaft bearing 9. In particular, it can be provided that the rotor hub 6 is arranged on a rotor shaft 13, wherein the rotor shaft 13 is supported by means of the first rotor shaft bearing 8 and the second rotor shaft bearing 9.

[0027] The first rotor shaft bearing 8 and the second rotor shaft bearing 9 can be designed to absorb a radial force 10 and an axial force 11. The axial force 11 is caused by the force of the wind. The radial force 10 is caused by the weight of the rotor 5 and acts at the center of gravity of the rotor 5. Since the center of gravity of the rotor 5 lies outside the first rotor shaft bearing 8, the radial force 10 induces a tilting moment 12 in the rotor shaft 13, 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 an uneven load on the rotor blades 7.

[0028] Furthermore, a gearbox 14 may be provided which is coupled to the rotor shaft 13. The gearbox 14 may be coupled to the rotor shaft 13 in such a way that it is also supported by the first rotor shaft bearing 8 and the second rotor shaft bearing 9.

[0029] Furthermore, it may be provided that a generator 15 is designed which is coupled to the gearbox 14.

[0030] As from Fig. 1 It can also be seen that the first rotor shaft bearing 8 is arranged closer to the rotor hub 6 than the second rotor shaft bearing 9.

[0031] Furthermore, it may be provided that the second rotor shaft bearing 9 is arranged closer to the generator 15 than the first rotor shaft bearing 8. It may also be provided that the first rotor shaft bearing 8 and / or the second rotor shaft bearing 9 are designed to additionally support the weight of the generator 15.

[0032] Fig. 2 Figure 1 shows a first embodiment of the first rotor shaft bearing 8 and second rotor shaft bearing 9 installed in the nacelle 2 in a longitudinal section view.

[0033] As from Fig. 2 As can be seen, the first rotor shaft bearing 8 may have a first inner ring 16 and a first outer ring 17. A first sliding bearing element 18 may be arranged between the first inner ring 16 and the first outer ring 17, which serves for the rotational sliding support of the first inner ring 16 relative to the first outer ring 17.

[0034] In the exemplary embodiment which in Fig. 2 As shown, the first inner ring 16 can be formed directly on the rotor shaft 13. Alternatively, it is also conceivable that the first inner ring 16 is designed as an independent component that is mounted on the rotor shaft 13.

[0035] Furthermore, it can be provided that the first outer ring 17 is received in a first bearing block 19. In particular, it can be provided that the first bearing block 19 is coupled to the nacelle housing 4 or alternatively is formed directly in the nacelle housing 4. In this embodiment, it can thus be provided that the first outer ring 17 is rigidly coupled to the nacelle housing 4 and that the first inner ring 16 is rotatable relative to the first outer ring 17 with respect to an axis of rotation 20 by means of the first sliding bearing element 18.

[0036] Furthermore, it can be provided that the first bearing block 19 serves directly as the first outer ring 17.

[0037] Furthermore, it can be provided that the first sliding bearing element 18 comprises several individual first sliding bearing pads 21, which are arranged distributed around the circumference between the first inner ring 16 and the first outer ring 17.

[0038] The individual first sliding bearing pads 21 can be rigidly coupled to the first inner ring 16 in the operating state and thus rotate with it relative to the first outer ring 17. To enable the rotational movement between the first inner ring 16 and the first outer ring 17, each of the individual first sliding bearing pads 21 has a first sliding surface 22 which bears against a first counter surface 23 of the first outer ring 17. The first counter surface 23 can be located on an inner side of the first outer ring 17.

[0039] The first sliding surface 22 of the first sliding bearing pad 21 and the first counter surface 23 of the first outer ring 17 are designed as sliding surfaces which slide against each other during operation of the wind turbine 1.

[0040] In particular, the first mating surface 23 of the first outer ring 17 may be designed as a hard, wear-resistant surface, which could, for example, be made of hardened steel. The first sliding surface 22 of the first sliding bearing pad 21 may be made of a sliding bearing material that is softer than the first mating surface 23. Of course, it is also conceivable that the first sliding surface 22 has a sliding coating.

[0041] As from Fig. 2 It can be particularly evident that the individual first sliding bearing pads 21 each have a first sliding surface 22 that is curved in the axial direction.

[0042] Furthermore, it can be provided that the first sliding surface 22 has an average first sliding surface diameter 24. The average first sliding surface diameter 24 is the mean value of the diameters of the first sliding surface 22 over the entire length of the sliding surface 22.

[0043] The first sliding surface 22 has an innermost contact point 25. The innermost contact point 25 of the first sliding surface 22 is that point of the first sliding surface 22 at which the first counter surface 23 still contacts the first sliding surface 22 and which is located closest to the second rotor shaft bearing 9.

[0044] As from Fig. 2 It can further be seen that the first sliding surface 22 of the first sliding bearing pad 21 is designed in the form of a spherical cap. In particular, it can be provided that the first sliding surface 22 forms a first spherical cap arc 26 in longitudinal section.

[0045] A first tangent 27 to the first sliding surface 22 in a first spherical cap arc center 28 can be arranged at a first angle 29 to the axis of rotation 20.

[0046] As from Fig. 2As can be seen, the second rotor shaft bearing 9 may have a second inner ring 30 and a second outer ring 31. A second sliding bearing element 32 may be arranged between the second inner ring 30 and the second outer ring 31, which serves for the rotational sliding support of the second inner ring 30 relative to the second outer ring 31.

[0047] In the exemplary embodiment which in Fig. 2 As shown, the second inner ring 30 can be formed directly on the rotor shaft 13. Alternatively, it is also conceivable that the second inner ring 30 is designed as an independent component that is mounted on the rotor shaft 13.

[0048] Furthermore, it can be provided that the second outer ring 31 is received in a second bearing block 33. In particular, it can be provided that the second bearing block 33 is coupled to the nacelle housing 4 or alternatively is formed directly in the nacelle housing 4. In this embodiment, it can thus be provided that the second outer ring 31 is rigidly coupled to the nacelle housing 4 and that the second inner ring 30 is rotatable relative to the second outer ring 31 with respect to the axis of rotation 20 by means of the second sliding bearing element 32.

[0049] Furthermore, it can be provided that the second bearing block 33 serves directly as the second outer ring 31.

[0050] Furthermore, it can be provided that the second sliding bearing element 32 comprises several individual second sliding bearing pads 34, which are arranged distributed around the circumference between the second inner ring 30 and the second outer ring 31.

[0051] The individual second sliding bearing pads 34 can be rigidly coupled to the second inner ring 30 in the operating state and thus rotate with it relative to the second outer ring 31. To enable the rotational movement between the second inner ring 30 and the second outer ring 31, each of the individual second sliding bearing pads 34 has a second sliding surface 35 which bears against a second counter surface 36 of the second outer ring 31. The second counter surface 36 can be located on an inner side of the second outer ring 31.

[0052] The second sliding surface 35 of the second sliding bearing pad 34 and the second counter surface 36 of the second outer ring 31 are designed as sliding surfaces which slide against each other during operation of the wind turbine 1.

[0053] In particular, the second mating surface 36 of the second outer ring 31 may be designed as a hard, wear-resistant surface, which may, for example, be made of hardened steel. The second sliding surface 35 of the second sliding bearing pad 34 may be made of a sliding bearing material that is softer than the second mating surface 36. Of course, it is also conceivable that the second sliding surface 35 has a sliding coating.

[0054] As from Fig. 2 It can be particularly evident that the individual second sliding bearing pads 34 each have a second sliding surface 35 that is curved in the axial direction.

[0055] Furthermore, it can be provided that the second sliding surface 35 has an average second sliding surface diameter 37. The average second sliding surface diameter 37 is the mean value of the diameters of the second sliding surface 35 over the entire length of the second sliding surface 35.

[0056] 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 at which the second counter surface 36 still contacts the second sliding surface 35 and which is located closest to the first rotor shaft bearing 8.

[0057] As from Fig. 2 As further shown, it can be provided that the second sliding surface 35 of the second sliding bearing pad 34 is designed in the form of a spherical cap. In particular, it can be provided that the second sliding surface 35 forms a second spherical cap arc 39 in longitudinal section.

[0058] A second tangent 41 to the second sliding surface 35 in a second spherical cap arc center 40 can be arranged at a second angle 42 to the axis of rotation 20.

[0059] As from Fig. 2 As can be further seen, it may be provided that the first tangent 27 and the second tangent 41 are arranged in a V-shape relative to each other. In other words, it may be provided that the first angle 29 is measured on the side of the rotor hub 6.

[0060] The second angle 42 can be measured on the side facing away from the rotor hub. Furthermore, it is conceivable that the first angle 29 and the second angle 42 are equal in size, with the V-shaped arrangement resulting from the different sides of the measurement.

[0061] Furthermore, it can be provided that the second sliding bearing pads 34 are pre-tensioned axially towards the first rotor shaft bearing 8 by means of a clamping device 43. The described design and the pre-tensioning by means of the clamping device 43 result in an O-shaped arrangement of the first rotor shaft bearing 8 and the second rotor shaft bearing 9, which allows radial forces, axial forces and tilting moments to be absorbed.

[0062] As from Fig. 2 It can further be seen that the innermost contact point 25 of the first sliding surface 22 and the innermost contact point 38 of the second sliding surface 35 are arranged at an axial distance 44 from each other.

[0063] In another embodiment, not shown, the first inner ring 16 and the second inner ring 30 can of course be designed as independent components. In such an embodiment, the clamping device 43 can act directly on the second inner ring 30.

[0064] Fig. 3 Figure 1 shows a further embodiment of the first rotor shaft bearing 8 and the second rotor shaft bearing 9 of the wind turbine 1. As shown from Fig. 3 As can be seen, the first sliding surface 22 and the second sliding surface 35 may be conical. In the longitudinal section view, the first sliding surface 22 and the second sliding surface 35 are thus represented as straight lines. As can be seen from Fig. 3As further shown, it can be provided that the first sliding surface 22 and the second sliding surface 35 are V-shaped relative to each other. In particular, it can be provided that the first sliding surface 22 and the second sliding surface 35 face each other.

[0065] As from Fig. 3 It can also be seen that the clamping device 43 is pressed directly against the second inner ring 30 or acts on the second inner ring 30.

[0066] The exemplary embodiments show possible embodiment variants, whereby it should be noted at this point that the invention is not limited to the specifically illustrated embodiment variants, but rather various combinations of the individual embodiment variants are also possible and this possibility of variation lies within the skill of the person skilled in this technical field due to the teaching on technical action by the present invention.

[0067] The scope of protection is defined by the claims. However, the description and drawings must be consulted for the interpretation of the claims. Individual features or combinations of features from the different embodiments shown and described can, in themselves, represent independent inventive solutions. The problem underlying these independent inventive solutions can be found in the description.

[0068] All references to value ranges in this description are to be understood as encompassing any and all sub-ranges thereof, e.g., the reference 1 to 10 is to be understood as including all sub-ranges, starting from the lower limit 1 and the upper limit 10, i.e., all sub-ranges begin with a lower limit of 1 or greater and end with an upper limit of 10 or less, e.g., 1 to 1.7, or 3.2 to 8.1, or 5.5 to 10.

[0069] Finally, for the sake of clarity, it should be noted that, for a better understanding of the structure, some elements have been shown not to scale and / or enlarged and / or reduced in size. Reference numeral list

[0070] 1 Wind turbine 28 first spherical cap arc center 29 first angle 2 gondola 30 second inner ring 3 Tower 31 second outer ring 4 nacelle housing 32 second sliding bearing element 5 rotor 33 second bearing block 6 Rotor hub 34 second sliding bearing pad 7 Rotor blade 35 second sliding surface 8 first rotor shaft bearing 36 second opposite surface 9 second rotor shaft bearing 37 average second sliding surface diameter 10 Radial force 11 Axial force 38 innermost contact point, second sliding surface 12 Tilting moment 13 Rotor shaft 39 second spherical cap arch 14 transmission 40 second spherical cap arc center 15 generator 41 second tangent 16 first inner ring 42 second angle 17 first outer ring 43 Clamping device 18 first sliding bearing element 44 Axial distance 19 first bearing block 20 axis of rotation 21 first sliding bearing pad 22 first sliding surface 23 first opposite surface 24 average first sliding surface diameter 25 innermost contact point, first sliding surface 26 first spherical cap arch 27 first tangent

Claims

1. A nacelle (2) for a wind turbine (1), the nacelle (2) comprising: - a nacelle housing (4); - a rotor shaft (13); - a rotor hub (6), which is arranged on the rotor shaft (13); - a first rotor shaft bearing (8) for bearing the rotor shaft (13) on the nacelle housing (4), characterized in that - the nacelle (2) comprises a second rotor shaft bearing (9) for bearing the rotor shaft (13) on the nacelle housing (4), wherein the first rotor shaft bearing (8) and the second rotor shaft bearing (9) are arranged at an axial distance (44) to one another and wherein the first rotor shaft bearing (8) is arranged closer to the rotor hub (6) than the second rotor shaft bearing (9); wherein the first rotor shaft bearing (8) has a first sliding surface (22), which has an averaged first sliding surface diameter (24), and that the second rotor shaft bearing (9) has a second sliding surface (35), which has an averaged second sliding surface diameter (37), wherein the first sliding surface (22) faces away from the rotor hub (6) at least in some sections, wherein the first sliding surface (22) and the second sliding surface (35) face one another at least in a partial section, wherein the first sliding surface (22) has an averaged first sliding surface diameter (24), wherein the axial distance (44) between the first rotor shaft bearing (8) and the second rotor shaft bearing (9) is measured from the innermost contact point (25) of the first sliding surface (22) to the innermost contact point (38) of the second sliding surface (35), wherein the axial distance (44) is between 20% and 1,000%, in particular between 50% and 500%, preferably between 90% and 300%, especially between 120% and 200% of the averaged first sliding surface diameter (24).

2. The nacelle (2) according to claim 1, characterized in that the axial distance (44) is between 90% and 1,000% of the averaged first sliding surface diameter (24).

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

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

5. The nacelle (2) according to one of the preceding claims, characterized in that the first rotor shaft bearing (8) has a first outer ring (17) and that the second rotor shaft bearing (9) has a second outer ring (31), and that the first rotor shaft bearing (8) has a first inner ring (16) and that the second rotor shaft bearing (9) has a second inner ring (30), wherein the first sliding surface (22) is arranged between the first outer ring (17) and the first inner ring (16) and wherein the second sliding surface (35) is arranged between the second outer ring (31) and the second inner ring (30), wherein the first outer ring (17) and the second outer ring (31) are arranged fixed to one another in their position and wherein the first inner ring (16) is arranged fixed to the rotor shaft (13) in its position and wherein the second inner ring (30) or a second sliding bearing element (32) is pretensioned in the axial direction towards the first inner ring (16) by means of a tensioning means (43), wherein the tensioning means (43) acts between the second inner ring (30) and the rotor shaft.

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

7. The nacelle (2) according to one of the preceding claims, characterized in that a gearbox (14) is formed which is torque-coupled to the rotor shaft (13), wherein the weight of the gearbox (14) is at least partially absorbed by the second rotor shaft bearing (9).

8. The nacelle (2) according to one of the preceding claims, characterized in that the first sliding surface (22) and / or the second sliding surface (35) are formed on sliding bearing pads (21).

9. The nacelle (2) according to one of the preceding claims, characterized in that the averaged first sliding surface diameter (24) is larger than the averaged second sliding surface diameter (37), in particular in that the averaged second sliding surface diameter (37) amounts to between 50% and 90%, preferably between 70% and 80%, of the averaged first sliding surface diameter (24).

10. The nacelle (2) according to one of claims 5 to 9, characterized in that the first outer ring (17) is accommodated in a first bearing block (19) and the second outer ring (31) is accommodated in a second bearing block (33).