Sliding bearing, nacelle for a wind power generation facility equipped with the sliding bearing, and wind power generation facility

Abstract

The sliding bearing (9) has an inner ring element (13), an outer ring element (14), and at least one sliding bearing element (15), the sliding bearing element being arranged between the inner ring element (13) and the outer ring element (14), and the outer ring element (14) and the inner ring element (13) being pivotally borne relative to each other about the axis of rotation (16) by the sliding bearing element (15). The sliding bearing element (15) has a plurality of sliding bearing pads (22), and each individual sliding bearing pad (22) has a curved bearing surface (27). The curved bearing surface (27) has a first radius (34) along the axis of rotation (16) in the longitudinal section and a second radius (35) perpendicular to the axis of rotation (16) in the cross section. In particular, the second radius (35) is larger than the first radius (34).

Description

Technical Field

[0001] The present invention relates to a sliding bearing, a nacelle for a wind power generation facility equipped with the sliding bearing, and a wind power generation facility.

Background Art

[0002] Patent Document 1 discloses a sliding bearing having an inner ring element and an outer ring element, in which a number of sliding bearing pads are arranged on the inner ring element. This sliding bearing pad has a sliding surface in the shape of a spherical crown, and this sliding surface cooperates with a corresponding sliding surface provided on the outer ring element. This type of spherical bearing is used to be able to absorb both radial forces and axial forces between the inner ring element and the outer ring element.

[0003] The spherical bearing shown in Patent Document 1 must have a predetermined width for a predetermined axial load capacity, so that a predetermined projected axial surface is obtained. Since the radial load capacity in a spherical bearing also depends on the width, an unnecessarily high radial load capacity is often obtained. As a result, the spherical bearing is often over-dimensioned with respect to its radial load capacity and thus has a large weight.

Prior Art Documents

Patent Documents

[0004]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0005] The object of the present invention is to provide an improved sliding bearing. In particular, the object of the present invention is to provide a sliding bearing having a sliding bearing pad width that is as small as possible at a predetermined diameter, and at the same time, the radial load capacity and the axial load capacity conform to a predetermined load profile.

Means for Solving the Problem

[0006] This problem is solved by the device shown in the claims.

[0007] A sliding bearing is provided based on the present invention. This sliding bearing has an inner ring element, has an outer ring element, has at least one sliding bearing element, and the sliding bearing element is arranged between the inner ring element and the outer ring element. The outer ring element and the inner ring element are rotatably borne relative to each other about the axis of rotation by the sliding bearing element. The sliding bearing element has a plurality of sliding bearing pads, and each individual sliding bearing pad has a curved bearing surface. The curved bearing surface has a first radius along the axis of rotation in the longitudinal section and a second radius perpendicular to the axis of rotation in the cross section. In particular, the second radius can be made larger than the first radius.

[0008] The sliding bearing according to the present invention has the surprising advantage that, depending on different radii, when the diameter of the inner ring element is predetermined, the axial load capacity and the radial load capacity of the sliding bearing can be coordinated with each other. Therefore, the weight of each individual sliding bearing pad can be reduced. Furthermore, by optimizing the axial load capacity and the radial load capacity of the sliding bearing, the efficiency of the sliding bearing can be improved.

[0009] Corresponding to the bearing surface, a counter surface can be formed. The bearing surface and the counter surface can together form a sliding bearing pair.

[0010] The longitudinal section along the axis of rotation has a cutting guide extending in the axial direction of the sliding bearing. In that case, the axis of rotation extends within the cutting plane of the cutting guide. In other words, the cutting plane of the longitudinal section is arranged exactly in the center and thus within the axis of rotation of the sliding bearing.

[0011] The axial position of the cross section perpendicular to the axis of rotation is selected at the axial apex of the bearing surface.

[0012] In particular, the first radius extends axially. The second radius can extend circumferentially. Furthermore, the first radius can have a constant value over the entire axial extent of the bearing surface. The first radius can have a central point radially spaced from the axis of rotation.

[0013] Furthermore, it can be effective if the bearing surfaces of the sliding bearing pads are each formed as a toroidal segment of a torus having a circular cross section. In particular, the bearing surface in the shape of a toroidal segment can be formed with a sufficiently high accuracy. Furthermore, this bearing surface shape can have good functionality.

[0014] The toroidal segment can be formed by arranging a circular cross section having a first radius at a distance from the axis of rotation and rotating it about the axis of rotation. In that case, the spacing with respect to the axis of rotation can be selected such that the axial apex, that is to say the radially outermost point, is arranged at a distance of the second radius from the axis of rotation.

[0015] Furthermore, the first radius can be made to be between 5% and 99% of the second radius, in particular between 10% and 50%, preferably between 15% and 30%. This brings the advantage that a particularly good distribution between the radial load capacity and the axial load capacity can be achieved by this measure.

[0016] Furthermore, the second radius can be measured at the axial apex.

[0017] It is also effective in cases where the sliding bearing pad can have a first axial extension in a first axial direction and a second axial extension in a second axial direction starting from the axial apex, and in which the first axial extension is greater than the second axial extension. Thereby, this measure provides the advantage that in a structure where the sliding bearing pad is as small as possible, it has a good ability to absorb the axial force directed in the main load direction. In the axial sub-load direction, it is possible to absorb a smaller axial force as required. By having different values for the first axial extension and the second axial extension, the sliding bearing can be adapted as desired to the requirements.

[0018] According to a further evolved form, it is possible for the second axial extension to be between 5% and 99%, in particular between 20% and 95%, preferably between 50% and 80% of the first axial extension. Thereby, this measure provides the advantage that in a structure where the sliding bearing pad is as small as possible, it has a good ability to absorb the axial force directed in the main load direction. In the axial sub-load direction, it is possible to absorb a smaller axial force as required, and overall the structural extension of the sliding bearing is kept as small as possible.

[0019] In an alternative embodiment, the sliding bearing pad can have a first axial extension in a first axial direction and a second axial extension in a second axial direction starting from the axial apex, and the first axial extension is the same size as the second axial extension. The sliding bearing pad formed in this way can have a structure that is as simple as possible. Furthermore, the sliding bearing pad formed in this way can apply an equal load in two axial directions.

[0020] According to a further evolved preferred form, the sliding bearing pad can have a sliding bearing pad width, and the sliding bearing pad width is between 20% and 170% of the first radius, particularly between 60% and 140%, preferably between 90% and 120%. Such a special sliding bearing pad having such a ratio of the sliding bearing pad width to the first radius has surprisingly little wear.

[0021] In other embodiments, the first radius can have a value different from the second 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 area will not be a spherical cap. When the second radius is larger than the first radius or the second radius is smaller than the first radius, the resulting bearing surface has a shape different from that of a spherical cap. A person skilled in the art will likely simply select the first radius and the second radius to be the same size in order to form the bearing surface as simply as possible. In that case, the bearing surface will have the shape of a spherical cap. By the measures according to the present invention, the bearing surface can be easily formed by having a constant value over the entire axial extension, and at the same time, the ratio of the radial load capacity to the axial load capacity can be adjusted by the second radius having a value different from the first radius. Thereby, the sliding bearing element can have as small a width as possible as a whole, and the width is selected to achieve the radial load capacity when the second radius is predetermined. By adapting the first radius, the axial load capacity can be adjusted.

[0022] Therefore, in the first embodiment, the second radius can be made larger than the first radius. In that case, a high axial load capacity can be achieved at a given radial load capacity.

[0023] In other embodiments, the second radius can be made smaller than the first radius. Such a form can be effective when there is a given radial load capacity and only a slight requirement for the axial load capacity.

[0024] According to the present invention, a nacelle for a wind power generation facility is provided, and the nacelle has the following, namely, a nacelle housing, and a rotor hub, and a rotor bearing for supporting the rotor hub in the nacelle housing, and this rotor bearing has a sliding bearing described in any of the above forms.

[0025] Particularly in the nacelle according to the present invention, the sliding bearing according to the present invention provides easy maintenance of the sliding bearing.

[0026] Furthermore, the sliding bearing pads of the sliding bearing can have a first axial extension in a first axial direction and a second axial extension in a second axial direction starting from an axial apex, and in that case the first axial extension is greater than the second axial extension, and the sliding bearing pads are housed in the nacelle housing such that, namely, the first axial extension is formed on the side opposite to the rotor hub at the axial apex. As a result, this measure provides the advantage that an increased axial force on the sliding bearing pads can be absorbed particularly well. The increased axial force on the sliding bearing pads is caused by the wind force acting on the rotor hub.

[0027] According to a special form, it is possible that a first rotor shaft bearing and a second rotor shaft bearing are formed, the first rotor shaft bearing is arranged closer to the rotor hub than the second rotor shaft bearing, and the second rotor shaft bearing is formed as a sliding bearing based on the above description. Such a structure has a surprisingly simple form and can absorb the forces generated in the rotor shaft well by the above-described form.

[0028] According to a preferred development, the sliding bearing pads can be fixed to the rotor shaft.

[0029] Furthermore, it may be preferred if the individual sliding bearing pads each have a fixing profile facing the bearing surface.

[0030] In particular, the inner ring element can have at least one receiving portion on its radially outer side, and the receiving portion is used to couple the sliding bearing pad to the inner ring element by shape. By this measure, the sliding bearing pad can be easily replaced, and at the same time, the sliding bearing pad is firmly attached when the driving of the sliding bearing is ready.

[0031] According to a special form, it is possible to form a radial stopper for the sliding bearing pad on the inner ring element within the area of the receiving portion. Thereby, the advantage is brought that the sliding bearing pad can be accurately positioned axially.

[0032] According to a preferred development, a fixing element can be provided, and the sliding bearing pad is pressed against the axial stopper in the axial direction by using it. Thereby, the advantage is brought that the sliding bearing pad can be fixed axially or accurately positioned, and thereby the functionality of the sliding bearing can be obtained.

[0033] Furthermore, at least one anti-relative rotation element can be formed, which acts between the axial stopper and at least one of the sliding bearing pads. By this measure, at least one of the sliding bearing pads can be fixed so as not to rotate relative to the axis.

[0034] Furthermore, the axial stopper can be formed as a stopper ring, and the stopper ring is mounted on the shaft. In particular, the axial stopper ring can be shrink-fitted onto the shaft.

[0035] In an alternative embodiment, the axial stopper can be formed directly on the shaft. Furthermore, positioning protrusions corresponding to the axial stopper can be formed on the sliding bearing pad.

[0036] In an alternative embodiment, the sliding bearing pad can be fixed to the nacelle housing. This can be done directly or via an intermediate bearing holder.

[0037] In this type of configuration, the bearing surface can be formed on the inside of the sliding bearing pad.

[0038] The counter surface for the bearing surface can be formed on the inner ring element. In particular, the counter surface can be formed directly on the shaft, in which case the shaft forms the inner ring element. In an alternative embodiment, the counter surface can also be arranged on an inner ring element formed to be structurally self - supporting, in which case the inner ring element is coupled to the shaft. In particular, the inner ring element can be shrink - fitted onto the shaft.

[0039] In particular, the outer ring element can have at least one receiving portion on its radially inner side, and this receiving portion is used to couple the sliding bearing pad to the outer ring element in terms of shape. By this measure, the sliding bearing pad can be easily replaced, and at the same time a firm attachment of the sliding bearing pad is obtained when the drive of the sliding bearing is ready.

[0040] According to a special configuration, it is possible to form an axial stopper for the sliding bearing pad on the outer ring element within the region of the receiving portion. This brings the advantage that the sliding bearing pad can be accurately positioned axially.

[0041] According to a preferred development, a fixing element can be provided, using which the sliding bearing pad is axially pressed against an axial stopper provided on the outer ring element. This brings the advantage that the sliding bearing pad can be axially fixed or accurately positioned, thereby obtaining the functionality of the sliding bearing.

[0042] The present invention further relates to a wind power plant having a nacelle, the nacelle comprising: a nacelle housing, a rotor hub and rotor blades attached thereto, - a rotor bearing for bearing the rotor hub in the nacelle housing. This rotor bearing has a sliding bearing according to any of the forms described above.

[0043] According to a special form, the rotor bearing has a bearing holder in which an outer ring element can be accommodated.

[0044] In an alternative embodiment, the bearing holder can be formed directly on the outer ring element.

[0045] This bearing holder can be fixed to the nacelle housing.

[0046] In an alternative embodiment, it is also conceivable to form the bearing holder directly in the nacelle housing. Thus, the outer ring element can also be formed directly in the nacelle housing.

[0047] According to a development, it is possible to form a removal opening in the outer ring element, the removal opening starting from the first end face of the outer ring element and interrupting the counter face of the outer ring element. Thereby, this measure brings the advantage that the individual bearing pads can be easily replaced, and for this purpose it is not necessary to disassemble the entire sliding bearing into its individual parts. In particular, it is conceivable that, by this measure, the individual sliding bearing pads can be replaced in the state in which the sliding bearing is incorporated, and it is not necessary to disassemble the entire sliding bearing. Furthermore, the removal opening can extend from the first end face of the outer ring element at least to the apex of the sliding bearing element.

[0048] Furthermore, in the driving state of the sliding bearing, it is conceivable to arrange a porous material such as a sponge in the extraction opening and temporarily store lubricating oil using the same. By this measure, the sliding surfaces of the individual sliding bearing pads can be uniformly covered with a lubricating oil film.

[0049] The individual sliding bearing pads can be easily removed from their driving positions through the extraction opening.

[0050] Furthermore, the extraction opening can be formed to widen radially toward the first end face. Thereby, the outer ring element can have as high stability as possible, and at the same time, the advantage is brought that the sliding bearing pad can be taken out of the extraction opening as easily as possible.

[0051] Furthermore, a sliding bearing pad receiving ring can be formed, which is used to fix the sliding bearing pad, and in that case, the sliding bearing pad receiving ring is attached to the inner ring element. Thereby, the advantage is brought that the sliding bearing pad can be firmly coupled to the inner ring element by this measure.

[0052] Furthermore, the sliding bearing pad receiving ring can be shrink-fitted onto the inner ring element. Especially for the rotor shaft, this is an extremely good and effective connection. When shrink-fitting, the sliding bearing pad receiving ring is heated and / or the inner ring element is cooled, thereby facilitating the axial press fit. After temperature compensation, that is, after compensation for thermal expansion, a firm attachment of the sliding bearing pad receiving ring onto the inner ring element is obtained.

[0053] In an alternative embodiment, or additionally, the sliding bearing pad receiving ring can be coupled to the inner ring element by a material-to-material connection such as a welding connection.

[0054] In yet another embodiment, the sliding bearing pad receiving ring can be coupled to the inner ring element using a form-fit coupling, such as a screw connection.

[0055] Furthermore, a plurality of threaded holes can be formed in the sliding bearing pad receiving ring, and these threaded holes are arranged in the axial direction of the sliding bearing pad receiving ring and are used to accommodate fixing screws. At this time, a through hole is formed in the sliding bearing pad, and the fixing screw is inserted therethrough, whereby the sliding bearing pad is fixed to the sliding bearing pad receiving ring by the fixing screw. Such a connection between the sliding bearing pad and the sliding bearing pad receiving ring can be easily formed.

[0056] In the deployed state, the sliding bearing pad can have a stepped portion on its inner side, and the stepped portion abuts against the end face of the sliding bearing pad receiving ring. At this time, the through hole is arranged in the region of the stepped portion. By this measure, a connection that can sufficiently apply a load between the sliding bearing pad and the inner ring element is obtained.

[0057] In the first embodiment, the sliding bearing can be formed as a hydrodynamic bearing.

[0058] In other embodiments, the sliding bearing can be formed as a hydrostatic bearing.

[0059] In yet another embodiment, the sliding bearing can be formed as a self-lubricating bearing.

[0060] To better understand the present invention, the present invention will be described in detail with reference to the following figures.

[0061] The figures are each a highly simplified schematic representation.

Brief Description of the Drawings

[0062]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Figure 8

Figure 9

DETAILED DESCRIPTION OF THE INVENTION

[0063] First, it should be noted that in the embodiments described differently, the same parts are provided with the same reference numerals or the same component names. In that case, the disclosure included in the entire description can be transferred meaningfully to the same parts having the same reference numerals or the same component names. Also, the positional descriptions selected in the description, such as up, down, side, etc., are related to the figures directly described and shown. This positional description is transferred to a new position meaningfully when the position changes.

[0064] FIG. 1 is a schematic representation showing a first embodiment of a wind power generation facility 1 for generating electrical energy from wind energy. The wind power generation facility 1 has a nacelle 2, and the nacelle is rotatably attached to a tower 3. The nacelle 2 has a nacelle housing 4, which forms the main structure of the nacelle 2. Electrical technical components, such as a generator of the wind power generation facility 1, are arranged in the nacelle housing 4 of the nacelle 2.

[0065] Furthermore, a rotor 5 is formed, and the rotor has a rotor hub 6 and rotor blades 7 arranged thereon. The rotor hub 6 is regarded as a part of the nacelle 2. The rotor hub 6 is rotatably attached to the nacelle housing 4 by a rotor bearing 8. In particular, as the rotor bearing 8, a sliding bearing 9 according to the present invention shown in detail below is used.

[0066] The rotor bearing 8 used to bear the rotor hub 6 on the nacelle housing 4 of the nacelle 2 is formed to absorb a radial force 10 and an axial force 11. The axial force 11 is brought about by the force of the wind. The radial force 10 is brought about by the self-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 located outside the rotor bearing 8, a tilting moment 12 is brought about by the radial force 10 within the rotor bearing 8. The tilting moment 12 may also be brought about similarly by the non-uniform load of the rotor blades 7. This tilting moment 12 can be absorbed by a second sliding bearing, and the second sliding bearing is arranged at a distance from the sliding bearing 9 according to the present invention.

[0067] The rotor bearing 8 according to the present invention can have a diameter, for example, between 0.5 m and 5 m. Of course, it is also conceivable that the rotor bearing 8 is smaller or larger than that.

[0068] FIG. 2 shows a first embodiment of the nacelle 2 having a sliding bearing 9. This sliding bearing 9 is shown in a longitudinal section in FIG. 2.

[0069] Of course, the sliding bearing 9 shown in FIG. 2 can also be applied to all other industrial applications other than wind power generation equipment.

[0070] As is apparent from FIG. 2, the sliding bearing 9 can have 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 and is used to rotationally slide the inner ring element 13 relative to the outer ring element 14. The inner ring element 13 and the outer ring element 14 are rotatable relative to each other about the axis of rotation 16.

[0071] In the embodiment shown in FIG. 2, the inner ring element 13 is directly formed by the rotor shaft 17.

[0072] This rotor shaft 17 is shown schematically in FIG. 2. As is apparent from FIG. 2, the rotor shaft 17 can have a rotor side 18. The rotor side 18 is used to accommodate the rotor hub 6 or the rotor hub 6 can be directly formed on the rotor side 18.

[0073] As is further apparent from FIG. 2, a first rotor shaft bearing 19 and a second rotor shaft bearing 20 can be formed. The first rotor shaft bearing 19 can be arranged closer to the rotor hub 6 or closer to the rotor side 18 than the second rotor shaft bearing 20. In that case, in particular, the second rotor shaft bearing 20 can be formed as the sliding bearing 9 as described later. The first rotor shaft bearing 19 can be formed as a floating bearing. The second rotor shaft bearing 20 can be formed as a fixed bearing.

[0074] Furthermore, the outer ring element 14 can be coupled to the nacelle housing 4 by a bearing holder 21. Thus, in the embodiment shown in FIG. 2, the outer ring element 14 is firmly coupled to the nacelle housing 4, and the inner ring element 13 is rotatable about the axis of rotation 16 relative to the outer ring element 14 by a sliding bearing element 15. Thus, in this embodiment, since the rotor hub 6 and the rotor shaft 17 which can be coupled to the rotor 5 therewith directly form the inner ring element 13, the rotor shaft 17 can be rotatably received in the nacelle housing 4 using the sliding bearing 9.

[0075] In FIG. 3, the sliding bearing 9 of FIG. 2 is shown in a perspective view. In order to make it easier to see and to be able to show the details of the sliding bearing 9, the outer ring element 14 has been axially displaced in the exploded perspective view of FIG. 3. The bearing holder 21 has also been omitted. The sliding bearing 9 will be described below with reference to FIGS. 2 and 3 together.

[0076] As can be seen from FIG. 3, the sliding bearing element 15 has a plurality of sliding bearing pads 22 which are distributed over the circumferential surface between the inner ring element 13 and the outer ring element 14.

[0077] Each individual sliding bearing pad 22 can be coupled to the inner ring element 13 using fixing means 23.

[0078] In particular, each individual sliding bearing pad 22 can have a step 25 on its inner side 24. Since this step 25 can form an abutment surface, the sliding bearing pad 22 can abut against the axial stop 26 of the inner ring element 13 in the region of the step 25. Thereby, the sliding bearing pad 22 can be positioned axially relative to the inner ring element 13.

[0079] In particular, the fixing means 23 can be formed in the form of fixing screws, and using them, the individual sliding bearing pads 22 can be axially pressed against the axial stopper 26 and thereby fixed.

[0080] Therefore, the individual sliding bearing pads 22 can be firmly coupled to the inner ring element 13 in the driving state of the sliding bearing 9 by the structure described above, and thus can rotate with respect to the outer ring element 14 together with the inner ring element. In order to enable the rotational movement between the inner ring element 13 and the outer ring element 14, bearing surfaces 27 are respectively formed on the individual sliding bearing pads 22, and the bearing surfaces are at least regionally adjacent to the counter surface 28 of the outer ring element 14 in the ready-to-use state of the sliding bearing 9.

[0081] This 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 formed as sliding surfaces, and they slide in contact with each other during the driving of the sliding bearing 9. In particular, the counter surface 28 of the outer ring element 14 can be formed as a wear-resistant hard surface, and the surface can be formed by, for example, hardened steel. The bearing surface 27 of the sliding bearing pad 22 can be formed from a softer sliding bearing material compared to the counter surface 28. Of course, it is also conceivable that the bearing surface 27 has a sliding coating.

[0082] As is apparent from FIGS. 2 and 3, an extraction opening 30 can be formed, which can be used to extract the individual sliding bearing pads 22. This extraction opening 30 can at least partially interrupt a counter surface 28 formed in the outer ring element 14. In particular, the extraction opening 30 can extend starting from the first end face 31 of the outer ring element 14. In particular, this extraction opening 30 can be prevented from extending to the second end face 32 of the outer ring element 14. Rather, this extraction opening 30 can be made to extend only up to the axial apex 33.

[0083] In order to replace the individual sliding bearing pads 22, it is not necessary to absorb the axial load of the shaft externally. Only one individual sliding bearing pad 22 can always be replaced with a new sliding bearing pad 22, and this process is repeated until all the sliding bearing pads 22 are replaced. Then the fixing means 23 can be removed, and the sliding bearing pad 22 freed after the removal of the fixing means 23 can be axially pulled out from the inner ring element 13.

[0084] Next, a new sliding bearing pad 22 can be inserted into the position of the old sliding bearing pad 22 according to the above description. Next, the new sliding bearing pad 22 can be fixed, and the inner ring element 13 can be further rotated, whereby the next sliding bearing pad can be replaced according to the steps described above. This process can be repeated until all the sliding bearing pads 22 are replaced.

[0085] FIG. 4 shows a perspective view of the sliding bearing pad 22, and here too the same reference numerals or component names are used for the same parts as in the preceding FIGS. 1 to 3. To avoid unnecessary repetition, reference is made to or the detailed description in the preceding FIGS. 1 to 3 is referred to.

[0086] FIG. 5 shows a cross-sectional view of the sliding bearing 9, where the same reference numerals or component names are used for the same parts as in the preceding FIGS. 1 to 4. To avoid unnecessary repetition, reference is made to or the detailed description in the preceding FIGS. 1 to 4 is indicated for reference.

[0087] In FIG. 6, segments of the bearing surface 27 are inscribed on a toroid that is structurally shown, and a first radius 34 and a second radius 35 are inscribed.

[0088] For the cross-sectional view of FIG. 5, the cutting guide shown as V-V in FIG. 2 is selected, where the cutting guide extends precisely through the axial apex 33.

[0089] The form of the sliding bearing pad 22 according to the present invention will be described while viewing FIGS. 2 to 5 together.

[0090] As apparent from FIGS. 2 to 6, the bearing surface 27 can 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, the second radius 35 can extend circumferentially of the bearing surface 27.

[0091] The first radius 34 extends axially. As apparent from the figure, the first radius 34 can have a first center point 36. The first center point 36 can be located in the plane of the axial apex 33 and can be spaced from the axis of rotation 16 by a center point spacing 38.

[0092] The second radius 35 can have a second center point 37. This second center point 37 can be located on the axis of rotation 16. In particular, by forming the first radius 34 and the second radius 35, the bearing surface 27 can form a segment of an envelope surface of a toroid having a circular cross-section.

[0093] As is apparent from FIGS. 2 to 6, the sliding bearing pad 22 can extend in the axial direction by a first axial length (extension) 39 starting from the axial apex 33 and can also extend by a second axial length (extension) 40 starting from the axial apex 33. The first axial extension 39 and the second axial extension 40 together result in a sliding bearing pad width 41.

[0094] In particular, as is apparent from FIG. 2, the first axial extension 39 can be made larger than the second axial extension 40. By this measure, the sliding bearing pad 22 is drawn further inwards at the first end face 31 of the outer ring element 14 than at the second end face 32 of the outer ring element 14. Thus, the sliding bearing 9 can absorb a higher compressive contact force in the first axial direction than in the second axial direction. The reason or the advantage of the embodiment according to the invention will be explained with reference to FIG. 7.

[0095] FIG. 7 shows the details of the sliding bearing 9 as shown in FIG. 2, and here too the same reference signs or component names are used for the same parts as in FIGS. 1 to 6 preceding. To avoid unnecessary repetition, reference is made to or the detailed description in FIGS. 1 to 6 preceding is referred to.

[0096] As is apparent from FIG. 7, the selection of the first radius 34 and the first axial extension 39 results in a first axial overlap 42. This axial overlap 42 defines the projected axial bearing surface and thereby the axial load capacity of the sliding bearing 9 can be determined.

[0097] Similarly, the first radius 34 and the second axial extension 40 define a second axial overlap 43. This second axial overlap 43 defines the projected axial bearing surface and thus the possible load capacity of the sliding bearing 9 in the second axial direction.

[0098] The possible load capacity in the radial direction is determined by the sliding bearing pad width 41.

[0099] To clarify the advantages for a sliding bearing pad having a spherical crown surface, a comparable spherical crown surface 44 is schematically shown in FIG. 7. The spherical crown surface 44 will have a spherical crown radius 45, which is of the same size as the second radius 35. Thus, as can be seen particularly clearly from FIG. 7, the third axial overlap 46 of the spherical crown surface 44 is much smaller than the first axial overlap 42. Thus, a sliding bearing having a spherical crown surface 44 formed in this way can absorb less axial load when the sliding bearing pad width 41 is equal.

[0100] In an embodiment not shown, different from the embodiments of FIGS. 2 to 7, the second radius 35 can be made smaller than the first radius 34.

[0101] In this type of embodiment, the bearing surface 27 has a basic shape similar to that of an "American football".

[0102] FIG. 8 shows another, in some cases self - standing, embodiment of the sliding bearing 9, where again the same reference numerals or component names are used for the same parts as in FIGS. 1 to 7 preceding. To avoid unnecessary repetition, reference is made to or the detailed description of FIGS. 1 to 7 preceding is indicated.

[0103] As is apparent from FIG. 8, the inner ring element 13 can be formed as a structurally self - standing element, and that element is attached to the rotor shaft 17.

[0104] FIG. 9 shows another, in some cases self - standing, embodiment of the sliding bearing 9, where again the same reference numerals or component names are used for the same parts as in FIGS. 1 to 8 preceding. To avoid unnecessary repetition, reference is made to or the detailed description of FIGS. 1 to 8 preceding is indicated.

[0105] As is apparent from FIG. 9, the sliding bearing pad 22 can be fixed to the outer ring element 14. Accordingly, the counter surface 28 can be formed on the inner ring element 13. In the embodiment shown in FIG. 9, the inner ring element 13 can be formed as part of the rotor shaft 17.

[0106] In an alternative embodiment not shown, based on the form of FIG. 9, the inner ring element 13 having the counter surface 28 can be formed in the form of a self - standing component, which is attached to the rotor shaft 17.

[0107] The embodiments show possible embodiments, but it should be noted here that the present invention is not limited to the specifically shown embodiments. Rather, it is possible to combine the individual embodiments with each other in various ways, and these possibilities of variation are within the discretion of those skilled in the art based on the teachings for technically handling the present invention.

[0108] The protection scope is defined by the claims. However, the specification and the drawings should be used to interpret the claims. Individual features or combinations of features derived from the various embodiments shown and described can represent an independent inventive solution in themselves. The problems underlying the independent inventive solutions can be read from the specification.

[0109] All descriptions of value ranges within the specific description include any sub - ranges and all sub - ranges together. For example, the description from 1 to 10 includes all sub - ranges starting from the lower limit of 1 and the upper limit of 10, that is, all sub - ranges starting from 1 or more and ending at 10 or less, such as from 1 to 1.7, or from 3.2 to 8.1, or from 5.5 to 10.

[0110] Finally, for the sake of clarity, the elements are shown not to scale, and / or enlarged and / or reduced in order to facilitate understanding of the structure.

Description of Symbols

[0111] 1 Wind power generation equipment 2 Nacelle 3 Tower 4 Nacelle housing 5 Rotor 6 Rotor hub 7 Rotor blade 8 Rotor bearing 9 Sliding bearing 10 Radial force 11 Axial force 12 Tilt moment 13 Inner ring element 14 Outer ring element 15 Sliding bearing element 16 Axis of rotation 17 Rotor shaft 18 Rotor side 19 First rotor shaft bearing 20 Second rotor shaft bearing 21 Bearing holder 22 Sliding bearing pad 23 Fixing means 24 Inner side 25 Step portion 26 Axial stopper 27 Bearing surface 28 Counter surface 29 Inner side 30 Removal opening 31 First end face of the outer ring element 32 Second end face of the outer ring element 33 Axial apex 34 First radius 35 Second radius 36 First center point 37 Second center point 38 Center point interval 39 First axial extension 40 Second axial extension 41 Sliding bearing pad width 42 First axial overlap 43 Second axial overlap 44 Spherical crown surface 45 Spherical crown radius 46 Third axial overlap

Images