Sliding bearing, nacelle for wind turbine equipped with sliding bearing, and wind turbine

Abstract

The invention relates to a plain bearing (9) comprising: an inner ring element (13); an outer ring element (14); at least one sliding bearing element (15), which is arranged between the inner ring element (13) and the outer ring element (14), by means of which the outer ring element (14) and the inner ring element (13) are supported so as to be rotatable relative to one another about an axis of rotation (16), the sliding bearing element (15) comprising a plurality of sliding bearing pads (22), each individual sliding bearing pad (22) having a curved bearing surface (27). The curved bearing surface (27) has a first radius (34) in a longitudinal section along the axis of rotation (16) and a second radius (35) in a cross section orthogonal to the axis of rotation (16). In particular, the second radius (35) is larger than the first radius (34).

Description

Technical Field

[0001] The invention relates to a sliding bearing, a nacelle for a wind power plant equipped with the sliding bearing, and a wind power plant. Background Art

[0002] DE650737C discloses a sliding bearing, which comprises an inner ring element and an outer ring element, and a plurality of sliding bearing pads are arranged on the inner ring element. Each sliding bearing pad has a sliding surface in the shape of a spherical cap, and the sliding surface cooperates with a sliding surface corresponding to the sliding surface on the outer ring element. This spherical bearing is used to receive radial force and axial force between the inner ring element and the outer ring element.

[0003] The spherical bearing according to DE 650 737 C needs to have a certain width for a predetermined axial load-bearing capacity, so that a certain projected axial area is achieved. Since the radial load-bearing capacity in the case of a spherical bearing is also dependent on the width, an unnecessarily high radial load-bearing capacity is often achieved here. This results in the spherical bearing being frequently oversized in terms of its radial load-bearing capacity and therefore having a high weight. Summary of the invention

[0004] The object of the present invention is to provide an improved plain bearing. In particular, the object of the present invention is to provide a plain bearing which, at a predetermined diameter, has a plain bearing pad width which is as small as possible, while the radial and axial load carrying capacities are adapted to a predetermined load curve.

[0005] This object is achieved by a device according to the claims.

[0006] According to the present invention, a sliding bearing is provided. The sliding bearing comprises:

[0007] - Inner ring element;

[0008] - outer ring element;

[0009] - at least one sliding bearing element, which is arranged between the inner ring element and the outer ring element, by means of which the outer ring element and the inner ring element are supported so as to be rotatable relative to each other around the rotation axis, and the sliding bearing element comprises a plurality of sliding bearing pads, each of which has a curved bearing surface.

[0010] The curved support surface has a first radius in a longitudinal section along the axis of rotation and a second radius in a cross section orthogonal to the axis of rotation. In particular, it can be provided that the second radius is greater than the first radius.

[0011] The sliding bearing according to the invention has the unexpected advantage that the axial load-bearing capacity and the radial load-bearing capacity of the sliding bearing can be adapted to one another by means of different radii at a predetermined diameter of the inner ring element. As a result, the weight of the individual sliding bearing pads can be reduced. In addition, the efficiency of the sliding bearing can be improved by optimizing the axial load-bearing capacity and the radial load-bearing capacity of the sliding bearing.

[0012] Corresponding to the support surface, a counter surface may be formed. The support surface and the counter surface may together form a sliding support pair.

[0013] The longitudinal section along the axis of rotation has a section guide extending in the axial direction of the sliding bearing. The axis of rotation is now in the section plane of the section guide. In other words, the section plane of the longitudinal section is arranged exactly in the center and therefore on the axis of rotation of the sliding bearing.

[0014] The axial position of the cross section orthogonal to the axis of rotation is selected at the position of the axial apex of the bearing surface.

[0015] In particular, it can be provided that the first radius extends in the axial direction and the second radius extends in the circumferential direction. It can also be provided that the first radius has a constant value over the entire axial extension of the bearing surface. The first radius can have a center point which is radially spaced apart from the axis of rotation.

[0016] It can also be suitable that the bearing surface of the sliding bearing pad is correspondingly configured as a torus surface segment of a torus surface with a circular cross section. In particular, the bearing surface in the form of a torus surface segment can be manufactured with sufficiently high precision. In addition, the bearing surface shape can have good functionality.

[0017] The toroidal surface section can be formed in such a way that a circular cross section with a first radius is arranged at a distance from the axis of rotation and rotates about the axis of rotation. The distance from the axis of rotation can be selected so that the axial vertex, that is to say the radially outermost point, is arranged at a distance from the axis of rotation at a second radius.

[0018] Furthermore, it can be provided that the first radius is between 5% and 99%, in particular between 10% and 50%, preferably between 15% and 30% of the second radius. This has the advantage that this measure allows a particularly good distribution between radial load carrying capacity and axial load carrying capacity to be achieved.

[0019] Furthermore, it can be provided that the second radius is measured at an axial apex.

[0020] A variant is also advantageous, according to which it can be provided that the plain bearing pad has a first axial extension in a first axial direction and a second axial extension in a second axial direction, starting from the axial vertex, the first axial extension being greater than the second axial extension. This has the following advantages: With this measure, the plain bearing pad has good properties with a design that is as small as possible: axial forces directed in the main load direction can be absorbed. In the axial secondary load direction, smaller axial forces can be absorbed as required. By different values ​​for the first axial extension and the second axial extension, the plain bearing can be specifically adapted to the requirements.

[0021] According to one embodiment, it is possible that the second axial extension is between 5% and 99%, in particular between 20% and 95%, preferably between 50% and 80%, of the first axial extension. This has the advantage that, with this measure, the plain bearing has good properties with the smallest possible construction: axial forces directed in the main load direction can be absorbed. In the axial secondary load direction, smaller axial forces can be absorbed as required. Overall, the construction extension of the plain bearing is kept as small as possible.

[0022] In an alternative embodiment, it can be provided that the plain bearing pad has, starting from the axial vertex, a first axial extension in a first axial direction and a second axial extension in a second axial extension, the first axial extension being equal to the second axial extension. A plain bearing pad designed in this way can have a structure that is as simple as possible. Furthermore, a plain bearing pad designed in this way can be loaded equally in both axial directions.

[0023] According to an advantageous embodiment, it can be provided that the sliding bearing pad has a sliding bearing pad width which is between 20% and 170%, in particular between 60% and 140%, preferably between 90% and 120% of the first radius. In particular, sliding bearing pads having such a ratio of sliding bearing pad width to first radius have unexpectedly low wear.

[0024] In another embodiment, it can be provided that the second radius has a value different from the first radius, and the first radius has a constant value over the entire axial extension of the bearing surface. In other words, the first radius can have a constant radius over the entire axial extension of the bearing surface, and the resulting surface is not a spherical cap. When the second radius is greater than the first radius or the second radius is less than the first radius, the resulting bearing surface is different from the shape of the spherical cap. For the sake of simplicity, the technician selects the first radius and the second radius to be of the same size so that the bearing surface can be manufactured as simply as possible. At this time, the bearing surface has the shape of a spherical cap. By the measures according to the present invention, it can be achieved that the bearing surface can be simply manufactured due to the constant value over the entire axial extension, and at the same time, the ratio of the radial load-bearing capacity to the axial load-bearing capacity can be adjusted by the different values ​​of the second radius and the first radius. Therefore, the sliding bearing element can have a width as small as possible in general, and the width is selected so that the radial load-bearing capacity can be achieved under the condition of a predetermined second radius. By adapting the first radius, the axial load-bearing capacity can be adjusted.

[0025] Therefore, in the first embodiment, it can be provided that the second radius is greater than the first radius. In this case, a high axial load-bearing capacity can be achieved under a given radial load-bearing capacity.

[0026] In other exemplary embodiments, it may be provided that the second radius is smaller than the first radius. Such an embodiment may be advantageous in cases where only small demands are made on the axial load-bearing capacity for a given radial load-bearing capacity.

[0027] According to the invention, a nacelle for a wind power installation is provided, comprising:

[0028] - Nacelle shell;

[0029] - rotor hub;

[0030] - A rotor bearing for supporting the rotor hub on the nacelle housing. The rotor bearing comprises a sliding bearing according to one of the above-mentioned solutions.

[0031] In particular in the nacelle according to the invention, the plain bearing according to the invention leads to simple maintainability of the plain bearing.

[0032] Furthermore, it can be provided that the plain bearing pad of the plain bearing has, starting from the axial apex, a first axial extension in a first axial direction and a second axial extension in a second axial direction, the first axial extension being greater than the second axial extension, the plain bearing pad being received in the nacelle housing in such a way that the first axial extension is formed on the side of the axial apex facing away from the rotor hub. This has the advantage that by this measure, increased axial forces can be particularly well absorbed at the plain bearing pad. The increased axial forces at the plain bearing pad are generated by wind forces at the rotor hub.

[0033] According to a particular embodiment, it is possible to form a first rotor shaft bearing and a second rotor shaft bearing, the first rotor shaft bearing being arranged closer to the rotor hub than the second rotor shaft bearing, the second rotor shaft bearing being designed as a plain bearing according to the above-described embodiment. Such an arrangement has an unexpectedly simple construction, wherein the forces occurring in the rotor shaft can be well absorbed by the described embodiment.

[0034] According to an advantageous development, it can be provided that the plain bearing pads are fastened to the rotor shaft.

[0035] Furthermore, it can be expedient if each of the plurality of plain bearing pads has a respective fastening contour lying opposite the bearing surface.

[0036] In particular, it can be provided that the inner ring element has at least one receptacle on its radial outer side, which serves to connect the plain bearing pad to the inner ring element in a form-fitting manner. This measure allows for simple replaceability of the plain bearing pad and, at the same time, for a secure seating of the plain bearing pad in the ready-to-operate state of the plain bearing.

[0037] According to a special embodiment, it is possible to form an axial stop for the plain bearing pad on the inner ring element in the region of the receptacle. This has the advantage that the plain bearing pad can be positioned precisely in the axial direction.

[0038] According to an advantageous embodiment, a fixing element can be provided, by means of which the sliding bearing pad is pressed against the axial stop in the axial direction. This has the advantage that the sliding bearing pad can be fixed or positioned correctly in the axial direction in order to achieve the functionality of the sliding bearing.

[0039] In addition, it can be provided that at least one anti-torsion element is formed, which acts between the axial stop ring and at least one of the sliding bearing pads. By this measure, it can be achieved that at least one of the sliding bearing pads is locked to prevent rotation relative to the shaft.

[0040] Furthermore, it can be provided that the axial stop is formed on a stop ring which is received on the shaft. In particular, it can be provided that the axial stop ring is shrink-fitted on the shaft.

[0041] In an alternative embodiment, it can be provided that the axial stop is formed directly on the shaft. It can also be provided that a positioning projection is formed on the sliding bearing pad, which positioning projection corresponds to the axial stop.

[0042] In an alternative embodiment, it can be provided that the sliding bearing pad is fixed to the nacelle housing. This can be achieved directly or with the interposition of a bearing bracket.

[0043] In such an embodiment, the bearing surface can be formed on the inner side of the sliding bearing pad.

[0044] The counter surface for the bearing surface can be formed on the inner ring element. In particular, it can be provided that the counter surface is formed directly on the shaft, wherein the shaft forms the inner ring element. In an alternative embodiment, it can also be provided that the counter surface is arranged on a structurally independently formed inner ring element, wherein the inner ring element is coupled to the shaft. In particular, it can be provided that the inner ring element is shrink-fitted onto the shaft.

[0045] In particular, it can be provided that the outer ring element has at least one receptacle on its radial inner side, which serves to connect the sliding bearing pad to the outer ring element in a form-fitting manner. This measure allows for simple replaceability of the sliding bearing pad and, at the same time, for a secure seating of the sliding bearing pad in the ready-to-operate state of the sliding bearing.

[0046] According to a particular embodiment, it is possible to form an axial stop for the plain bearing pad on the outer ring element in the region of the receptacle. This has the advantage that the plain bearing pad can be positioned precisely in the axial direction.

[0047] According to an advantageous embodiment, it can be provided that a fixing element is provided, by means of which the sliding bearing pad is pressed in the axial direction against an axial stop on the outer ring element. This has the advantage that the sliding bearing pad can be fixed or positioned correctly in the axial direction in order to achieve the functionality of the sliding bearing.

[0048] The invention further relates to a wind power installation having a nacelle, the nacelle comprising:

[0049] - Nacelle shell;

[0050] - a rotor hub having rotor blades arranged thereon;

[0051] - A rotor bearing for supporting the rotor hub on the nacelle housing. The rotor bearing comprises a sliding bearing according to one of the above-mentioned solutions.

[0052] According to a particular embodiment, it is possible for the rotor bearing to comprise a bearing bracket in which the outer ring element is accommodated.

[0053] In an alternative embodiment, it can be provided that the bearing bracket is designed directly as an outer ring element.

[0054] The bearing bracket can be fastened to the nacelle housing.

[0055] In an alternative embodiment, it is also conceivable that the bearing bracket is formed directly in the nacelle housing. Therefore, it can also be provided that the outer ring element is formed directly in the nacelle housing.

[0056] According to an extended solution, it is possible to form an extraction opening in the outer ring element, which interrupts the corresponding surface of the outer ring element starting from the first end side of the outer ring element. This brings the following advantages: through this measure, each individual sliding bearing pad can be easily replaced without having to disassemble the entire sliding bearing into its parts for this purpose. In particular, it is conceivable that through this measure, each individual sliding bearing pad can be replaced in the installed state of the sliding bearing without having to completely disassemble the sliding bearing. In addition, it can be provided that the extraction opening extends from the first end side of the outer ring element to the top of the sliding bearing element.

[0057] In addition, it is conceivable that in the running state of the sliding bearing, an open-pored material such as a sponge is provided in the extraction opening, and this open-pored material is used to temporarily receive lubricating oil. By this measure, it can be realized that the sliding surface of each single sliding bearing pad is evenly covered with a lubricating oil film.

[0058] The individual plain bearing pads can be removed from their operating position simply through the removal opening.

[0059] Furthermore, it can be provided that the removal opening is designed to expand radially toward the first end side. This has the advantage that the outer ring element can have the highest possible stability and at the same time the sliding bearing pad can be removed as easily as possible through the removal opening.

[0060] Furthermore, it can be provided that a plain bearing receiving ring is formed for fixing the plain bearing, which is received on the inner ring element. This has the advantage that the plain bearing can be firmly coupled to the inner ring element by this measure.

[0061] Furthermore, it can be provided that the plain bearing pad receiving ring is shrink-fitted onto the inner ring element. This results in an extremely durable and practical connection, in particular for the rotor shaft. During shrink-fitting, the plain bearing pad receiving ring is heated and / or the inner ring element is cooled in order to facilitate axial press-fitting. After temperature equilibration and thus after thermal expansion equilibration, a firm fit of the plain bearing pad receiving ring on the inner ring element can be achieved.

[0062] In an alternative embodiment or as a supplement, it can be provided that the plain bearing pad receiving ring is coupled to the inner ring element by means of a materially bonded connection, for example welding.

[0063] In yet another embodiment, it can be provided that the plain bearing pad receiving ring is coupled to the inner ring element by means of a form-fitting connection, for example a screw connection.

[0064] Furthermore, it can be provided that a plurality of threaded holes are formed in the sliding bearing pad receiving ring, which are arranged in the axial direction of the sliding bearing pad receiving ring and are used to receive fastening screws, through-holes are formed in the sliding bearing pads, and the fastening screws are inserted through these through-holes in order to clamp the sliding bearing pad on the sliding bearing pad receiving ring by means of the fastening screws. Such a connection between the sliding bearing pad and the sliding bearing pad receiving ring can be easily produced.

[0065] In an extension, it can be provided that the sliding bearing pad has a step on its inner side, the step abutting against the end side of the sliding bearing pad receiving ring, the through hole being arranged in the region of the step. By this measure, a connection that can be sufficiently loaded between the sliding bearing pad and the inner ring is achieved.

[0066] In a first embodiment it can be provided that the sliding bearing is designed as a hydrodynamic bearing.

[0067] In a further embodiment it can be provided that the sliding bearing is designed as a hydrostatic bearing.

[0068] In yet another embodiment, it can be provided that the sliding bearing is designed as a self-lubricating bearing element. BRIEF DESCRIPTION OF THE DRAWINGS

[0069] For a better understanding of the invention, the invention is explained in more detail with the aid of the following drawings.

[0070] The accompanying drawings are greatly simplified schematic diagrams, as follows:

[0071] Figure 1 A schematic diagram showing a wind power plant;

[0072] Figure 2 A longitudinal sectional view showing a first embodiment of a sliding bearing;

[0073] Figure 3 A perspective view showing a plain bearing;

[0074] Figure 4 A perspective view showing a sliding bearing pad;

[0075] Figure 5 Display Press Figure 2 A cross-sectional view of section line VV;

[0076] Figure 6 A perspective view showing a torus with a depicted slip surface;

[0077] Figure 7 show Figure 2 Detail of the longitudinal section view;

[0078] Figure 8 A longitudinal sectional view showing a second embodiment of a sliding bearing;

[0079] Fig. 9 A longitudinal section through a third exemplary embodiment of a sliding bearing is shown. DETAILED DESCRIPTION

[0080] First of all, it should be pointed out that in the various embodiments described, the same components are provided with the same reference numerals or the same component names, and the disclosure contained in the entire description can be applied to the same components with the same reference numerals or the same component names in a meaningful manner. The orientation descriptions selected in the description, such as top, bottom, side, etc., also refer to the directly described and described drawings, and these orientation descriptions can be applied to the new orientation in a meaningful manner when the orientation changes.

[0081] Figure 1 In the schematic diagram, a first embodiment of a wind power installation 1 for generating electrical energy from wind energy is shown. The wind power installation 1 comprises a nacelle 2, which is rotatably received on a tower 3. The nacelle 2 comprises a nacelle housing 4, which forms the main structure of the nacelle 2. In the nacelle housing 4 of the nacelle 2, electrical components of the wind power installation 1, such as a generator, are arranged.

[0082] Furthermore, a rotor 5 is formed which has a rotor hub 6 and rotor blades 7 arranged thereon. The rotor hub 6 is considered to be part of the nacelle 2. The rotor hub 6 is received on the nacelle housing 4 in a rotatable manner by means of a rotor bearing 8. In particular, it is provided that the sliding bearing 9 according to the invention and described in more detail is used as the rotor bearing 8.

[0083] The rotor bearing 8 is used to support the rotor hub 6 on the nacelle housing 4 of the nacelle 2, and the rotor bearing is designed to receive radial forces 10 and axial forces 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 on the center of gravity of the rotor 5. Since the center of gravity of the rotor 5 is outside the rotor bearing 8, a tilting moment 12 is caused in the rotor bearing 8 by the radial force 10. The tilting moment 12 can also be caused by uneven loading of the rotor blades 7. This tilting moment 12 can be received by means of a second sliding bearing, which is arranged at a distance from the sliding bearing 9 according to the present invention.

[0084] The rotor bearing 8 according to the invention can have, for example, a diameter between 0.5 m and 5 m. Of course, it is also conceivable that the rotor bearing 8 is smaller or larger.

[0085] Figure 2 A first embodiment of a nacelle 2 is shown with a sliding bearing 9. The sliding bearing 9 is Figure 2 Described in longitudinal section.

[0086] Of course, in Figure 2 The plain bearing 9 described in the specification can also be used in all other industrial applications besides wind power plants.

[0087] If Figure 2 It can be seen that it can be provided that the sliding bearing 9 has an inner ring element 13 and an outer ring element 14. A sliding bearing element 15 is arranged between the inner ring element 13 and the outer ring element 14, which is used for sliding bearing of the inner ring element 13 relative to the rotation of the outer ring element 14. The inner ring element 13 and the outer ring element 14 are rotatable relative to each other around the rotation axis 16.

[0088] In the description of Figure 2 In the exemplary embodiment of FIG. 2 , the inner ring element 13 is formed directly by the rotor shaft 17 .

[0089] The rotor shaft 17 is Figure 2 As schematically described in Figure 2 It can be seen that provision can be made for the rotor shaft 17 to have a rotor side 18 . The rotor side 18 serves to receive the rotor hub 6 , or the rotor hub 6 can be formed directly on the rotor side 18 .

[0090] If Figure 2 It can also be seen that it can be provided that a first rotor shaft bearing 19 and a second rotor shaft bearing 20 are formed. The first rotor shaft bearing 19 is arranged closer to the rotor hub 6 or the rotor side 18 than the second rotor shaft bearing 20. In particular, it can be provided that the second rotor shaft bearing 20 is formed as a sliding bearing 9 according to the embodiment to be described below. The first rotor shaft bearing 19 can be formed as a loose bearing. The second rotor shaft bearing 20 can be formed as a fixed bearing.

[0091] Furthermore, it can be provided that the outer ring element 14 is coupled to the nacelle housing 4 by means of a support bracket 21. Figure 2 In the embodiment of FIG. 4 , it is therefore provided that the outer ring element 14 is rigidly coupled to the nacelle housing 4 and the inner ring element 13 is rotatable relative to the outer ring element 14 about the rotation axis 16 by means of sliding bearing elements 15. Since in this embodiment the rotor shaft 17 (which can be coupled to the rotor hub 6 and thus to the rotor 5 ) directly forms the inner ring element 13, the rotor shaft 17 can be rotatably received in the nacelle housing 4 by means of the sliding bearing 9.

[0092] exist Figure 3 middle, Figure 2 The sliding bearing 9 is depicted in a perspective view. Figure 3 The outer ring element 14 is axially displaced in the exploded view in order to be able to describe the details of the plain bearing 9. The support bracket 21 is also hidden. Figure 2 and Figure 3 The common diagram is used to illustrate.

[0093] If Figure 3 It can be seen that the plain bearing element 15 comprises a plurality of individual plain bearing pads 22 which are arranged distributed over the circumference between the inner ring element 13 and the outer ring element 14 .

[0094] The individual plain bearing pads 22 can each be coupled to the inner ring element 13 by means of a fixing component 23 .

[0095] In particular, it can be provided that each individual plain bearing pad 22 has a step 25 on its inner side 24. The step 25 can form a contact surface, so that the plain bearing pad 22 can contact an axial stop 26 of the inner ring element 13 in the region of the step 25. The plain bearing pad 22 can thus be positioned relative to the inner ring element 13 in the axial direction.

[0096] In particular, it can be provided that the fixing means 23 are designed in the form of a fastening screw, by means of which the individual plain bearing pads 22 can be pressed in the axial direction against the axial stop 26 and thus be fixed.

[0097] The individual sliding bearing pads 22 can therefore be firmly connected to the inner ring element 13 by the described structure in the operating state of the sliding bearing 9 and can therefore rotate together with the inner ring element relative to the outer ring element 14. In order to allow a rotational movement between the inner ring element 13 and the outer ring element 14, a bearing surface 27 is formed on each individual sliding bearing pad 22, which, in the ready-to-use state of the sliding bearing 9, at least partially rests on a corresponding surface 28 of the outer ring element 14.

[0098] The counter surface 28 is arranged on the inner side 29 of the outer ring element 14. The bearing surface 27 of the sliding bearing pad 22 and the counter surface 28 of the outer ring element 14 are designed as sliding surfaces, which slide against each other during the operation of the sliding bearing 9. In particular, it can be provided that the counter surface 28 of the outer ring element 14 is designed as a hard, wear-resistant surface, which can be formed, for example, by hardened steel. The bearing surface 27 of the sliding bearing pad 22 can be formed from a sliding bearing material that is softer than the counter surface 28. Of course, it is also conceivable that the bearing surface 27 has a sliding coating.

[0099] If Figure 2 and Figure 3 It can be seen that it can be provided that an extraction opening 30 is formed, which can be used to extract a single sliding bearing pad 22. The extraction opening 30 can at least partially interrupt the corresponding surface 28 formed in the outer ring element 14. In particular, it can be provided that the extraction opening 30 extends from a first end side 31 of the outer ring element 14. In particular, it can be provided that the extraction opening 30 does not extend to the second end side 32 of the outer ring element 14. More precisely, the extraction opening 30 can extend only to an axial apex 33.

[0100] For replacing the individual sliding bearing pads 22, it is not necessary for the shaft load to be taken up by the outer bearing, but it can be provided that only one individual sliding bearing pad 22 is always replaced by a new sliding bearing pad 22, and this process is repeated until all sliding bearing pads 22 have been replaced. At this point, the fixing member 23 can be released and, after the removal of the fixing member 23, the free sliding bearing pad 22 can be pulled out of the inner ring element 13 in the axial direction.

[0101] Then, a new sliding bearing pad 22 can be installed in the place of the old sliding bearing pad 22 according to the above description. Then, the newly installed sliding bearing pad 22 can be fixed, and then, the inner ring element 13 can be rotated so that the next sliding bearing pad can be replaced according to the steps described above. This process can be repeated until all sliding bearing pads 22 are replaced.

[0102] exist Figure 4 A perspective view of the sliding bearing pad 22 is shown in FIG. 1 , wherein again the same components as in the previous Figures 1 to 3 In order to avoid unnecessary repetition, reference or citation to the previous Figures 1 to 3 Detailed instructions in.

[0103] exist Figure 5 A cross-sectional view of a plain bearing 9 is shown in FIG. 1 , wherein again the same components as in the previous Figures 1 to 4 In order to avoid unnecessary repetition, reference or citation to the previous Figures 1 to 4Detailed instructions in.

[0104] exist Figure 6 2 shows a section of a contact surface 27 on a structurally described annular surface, wherein a first radius 34 and a second radius 35 are described.

[0105] exist Figure 5 In the cross-sectional view, select Figure 2 The section guide of VV in FIG. 3 extends exactly through the axial apex 33 .

[0106] The embodiment according to the invention of the sliding bearing pad 22 is achieved by Figures 2~5 The common diagram is used to illustrate.

[0107] If Figures 2~6 It can be seen that provision can be made for the contact surface 27 to have a first radius 34 and a second radius 35. The second radius 35 extends from the axis of rotation 16 to the axial apex 33. In particular, provision can be made for the second radius 35 to extend in the circumferential direction of the contact surface 27.

[0108] The first radius 34 extends in the axial direction. As can be seen from the figures, it can be provided that the first radius 34 has a first center point 36. The first center point 36 can be located in the plane of the axial apex 33 and is spaced apart from the axis of rotation 16 by a center point distance 38.

[0109] The second radius 35 can have a second center point 37. The second center point 37 can be located on the axis of rotation 16. In particular, it can be provided that by forming the first radius 34 and the second radius 35, the contact surface 27 forms a section of an envelope surface of a torus having a circular cross section.

[0110] If Figures 2~6 It can also be seen that the plain bearing pad 22 can extend in the axial direction starting from the axial apex 33 in a first axial extension 39 and in a second axial extension 40 starting from the axial apex 33 . The sum of the first axial extension 39 and the second axial extension 40 results in a plain bearing pad width 41 .

[0111] If particularly well Figure 2 It can be seen that it can be provided that the first axial extension 39 is greater than the second axial extension 40. As a result of this measure, the sliding bearing pad 22 extends further inwards on the first end side 31 of the outer ring element 14 than on the second end side 32 of the outer ring element 14. As a result, the sliding bearing 9 can absorb higher axial forces in the first axial direction than in the second axial direction. The reasons for this or the advantages of the embodiment according to the invention are explained by Figure 7 explain.

[0112] exist Figure 7As shown in Figure 2 Detail of the sliding bearing 9 described in the previous section, again for the same parts as in the previous section Figures 1 to 6 In order to avoid unnecessary repetition, reference or citation to the previous Figures 1 to 6 Detailed instructions in.

[0113] If Figure 7 It can be seen that the first axial overlap dimension 42 results from the selection of the first radius 34 and the first axial extension 39. The first axial overlap dimension 42 determines the projected axial bearing surface and thus the axial loadability of the plain bearing 9.

[0114] Analogously, a second axial overlap 43 is determined by the first radius 34 and the second axial extension 40. The second axial overlap 43 determines the projected axial bearing surface and thus the possible loadability of the plain bearing 9 in the second axial direction.

[0115] The possible loadability of the plain bearing 9 in the radial direction is determined by the plain bearing pad width 41 .

[0116] In order to illustrate the advantages compared with the sliding bearing pad with a spherical crown surface, schematically Figure 7 A comparable spherical cap surface 44 is described in FIG. The spherical cap surface 44 has a spherical cap radius 45, which is as large as the second radius 35. As can be seen particularly well by Figure 7 It can be seen that the third axial overlap dimension 46 of the spherical crown surface 44 is therefore significantly smaller than the first axial overlap dimension 42. A plain bearing element with a spherical crown surface 44 formed in this way can therefore only absorb smaller axial loads at the same plain bearing pad width 41.

[0117] In an undescribed embodiment, Figures 2 to 7 In contrast to the embodiment of FIG. 3 , it can be provided that the second radius 35 is smaller than the first radius 34. In this embodiment, the support surface 27 has a basic shape similar to an “American football”.

[0118] exist Figure 8 Another and optionally independent embodiment of a sliding bearing 9 is shown in FIG. Figures 1 to 7 In order to avoid unnecessary repetition, reference or citation to the previous Figures 1 to 7 Detailed instructions in.

[0119] If Figure 8 It can be seen that it can be provided that the inner ring element 13 is designed as a structurally independent element which is received on the rotor shaft 17 .

[0120] exist Fig. 9 Another and optionally independent embodiment of a sliding bearing 9 is shown in FIG. Figures 1 to 8 In order to avoid unnecessary repetition, reference or citation to the previous Figures 1 to 8 Detailed instructions in.

[0121] If Fig. 9 It can be seen that it can be provided that the sliding bearing pad 22 is fixed on the outer ring element 14. The counter surface 28 can therefore be formed on the inner ring element 13. Fig. 9 In the exemplary embodiment of FIG. 1 , it can be provided that the inner ring element 13 is formed as part of the rotor shaft 17 .

[0122] Based on the Fig. 9 In an alternative embodiment (not shown) of the embodiment of , it can also be provided that the inner ring element 13 formed with the counter surface 28 is formed in the form of a separately formed component which is received on the rotor shaft 17 .

[0123] The various embodiments show possible implementation schemes. It should be noted that the present invention is not limited to the specifically described implementation schemes of the present invention. More precisely, various combinations of the individual implementation schemes are possible, and such variation possibilities are within the capabilities of technicians working in this technical field based on the teaching of the technical processing through the present invention.

[0124] The scope of protection is determined by the claims. However, the description and the drawings can be used to interpret the claims. Individual features or combinations of features from the different embodiments shown and described can form independent inventive solutions. The tasks underlying the independent inventive solutions can be derived from the description.

[0125] In this specification, all data about numerical ranges can be understood as these numerical ranges together include any and all sub-ranges from these numerical ranges. For example, data 1 to 10 can be understood as all sub-ranges starting from the lower limit 1 and the upper limit 10 are included together, that is, all sub-ranges starting from the lower limit 1 or greater and ending at the upper limit 10 or less are included together, for example 1 to 1.7, or 3.2 to 8.1, or 5.5 to 10.

[0126] For the sake of clarity it is useful to point out that elements are partially not depicted to scale and / or are enlarged and / or reduced in size for a better understanding of the structure.

[0127] Reference numerals list

[0128] 1 Wind power equipment

[0129] 2 Cabin

[0130] 3 Towers

[0131] 4 Cabin shell

[0132] 5 rotors

[0133] 6 rotor hub

[0134] 7 Rotor Blades

[0135] 8 Rotor bearings

[0136] 9. Sliding bearings

[0137] 10 Radial force

[0138] 11 Axial force

[0139] 12 Overturning moment

[0140] 13 Inner ring element

[0141] 14 Outer ring element

[0142] 15 Sliding bearing element

[0143] 16Rotation axis

[0144] 17 Rotor shaft

[0145] 18 Rotor side

[0146] 19 first rotor shaft support

[0147] 20 Second rotor shaft support

[0148] 21 Support bracket

[0149] 22 Sliding bearing pad

[0150] 23Fixed components

[0151] 24 Inside

[0152] 25 steps

[0153] 26 Axial stop

[0154] 27 Support surface

[0155] 28 corresponding faces

[0156] 29 Inside

[0157] 30 Extraction opening

[0158] 31 First end side of outer ring element

[0159] 32 The second end side of the outer ring element

[0160] 33 Axial Vertex

[0161] 34 First Radius

[0162] 35 Second Radius

[0163] 36 First Center Point

[0164] 37 Second center point

[0165] 38 center point spacing

[0166] 39 First axial extension dimension

[0167] 40 Second axial extension dimension

[0168] 41 Sliding bearing pad width

[0169] 42 First axial overlap dimension

[0170] 43 Second axial overlap dimension

[0171] 44 ball crown

[0172] 45 crown radius

[0173] 46 Third axial overlap dimension

Claims

1. A sliding bearing (9), comprising: - inner ring element (13); - an outer ring element (14); - at least one sliding bearing element (15), which is arranged between the inner ring element (13) and the outer ring element (14), by means of which the outer ring element (14) and the inner ring element (13) are supported so as to be rotatable relative to one another about a rotation axis (16), the sliding bearing element (15) comprising a plurality of sliding bearing pads (22), each individual sliding bearing pad (22) having a curved bearing surface (27); It is characterized in that The curved support surface (27) has a first radius (34) in a longitudinal section along the rotation axis (16) and a second radius (35) in a cross section orthogonal to the rotation axis (16), in particular the second radius (35) being greater than the first radius (34).

2. The sliding bearing (9) according to claim 1, characterized in that: The bearing surface (27) of the sliding bearing pad (22) is accordingly designed as a toroidal surface segment of a toroidal surface with a circular cross section.

3. The sliding bearing (9) according to claim 1 or 2, characterized in that: The first radius (34) is between 5% and 99%, in particular between 10% and 50%, and preferably between 15% and 30%, of the second radius (35).

4. The sliding bearing (9) according to any one of claims 1 to 3, characterized in that The second radius (35) is measured at the axial apex (33).

5. The sliding bearing (9) according to claim 4, characterized in that: The sliding bearing pad (22) has a first axial extension (39) in a first axial direction and a second axial extension (40) in a second axial direction starting from an axial apex (33), the first axial extension (30) being greater than the second axial extension (40).

6. The sliding bearing (9) according to claim 5, characterized in that The second axial extension (40) is between 5% and 99%, in particular between 20% and 95%, and preferably between 50% and 80%, of the first axial extension (39).

7. The sliding bearing (9) according to claim 4, characterized in that The sliding bearing pad (22) has, starting from an axial apex (33), a first axial extension (39) in a first axial direction and a second axial extension (40) in a second axial extension direction, the first axial extension (39) being of the same size as the second axial extension (40).

8. The sliding bearing (9) according to any one of the preceding claims, characterized in that The sliding bearing pad (22) has a sliding bearing pad width (41) which is between 20% and 170%, in particular between 60% and 140%, preferably between 90% and 120%, of the first radius (34).

9. The sliding bearing (9) according to any one of the preceding claims, characterized in that The second radius (35) has a different value than the first radius (34), which has a constant value over the entire axial extension of the bearing surface.

10. The sliding bearing (9) according to any one of the preceding claims, characterized in that The second radius (35) is smaller than the first radius (34).

11. A nacelle (2) for a wind power device (1), the nacelle (2) comprising: - Nacelle shell (4); - rotor hub (6); - A rotor bearing (8) for supporting a rotor hub (6) on a nacelle housing (4); characterised in that the rotor bearing (8) has a sliding bearing (9) according to any of the preceding claims, the sliding bearing having a plurality of sliding bearing pads (22).

12. The nacelle (2) according to claim 11, characterized in that The sliding bearing pad (22) of the sliding bearing (9) has a first axial extension (39) in a first axial direction and a second axial extension (40) in a second axial direction starting from an axial apex (33), the first axial extension (39) being greater than the second axial extension (40), the sliding bearing pad (22) being received in the nacelle housing (4) such that the first axial extension (39) is formed on a side of the axial apex (33) facing away from the rotor hub (6).

13. Nacelle (2) according to claim 11 or 12, characterized in that A first rotor shaft bearing (19) and a second rotor shaft bearing (20) are formed, wherein the first rotor shaft bearing (19) is arranged closer to the rotor hub (6) than the second rotor shaft bearing (20), and the second rotor shaft bearing (20) is formed as a sliding bearing (9) according to any one of claims 1 to 8.

14. Nacelle (2) according to any one of claims 11 to 13, characterized in that The sliding bearing pad (22) is fixed on the rotor shaft (17).

15. Nacelle (2) according to any one of claims 11 to 14, characterized in that The sliding support pad (22) is fixed on the cabin shell (4).

16. A wind power installation (1) having a nacelle (2), the nacelle (2) comprising: - Nacelle shell (4); - a rotor hub (6) having rotor blades arranged on the rotor hub; - a rotor bearing (8) for supporting the rotor hub (6) on the nacelle housing (4); characterised in that the rotor bearing (8) comprises a sliding bearing (9) according to any one of claims 1 to 10.

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