Plain bearing pads and plain bearings, and wind turbine nacelle equipped with plain bearings

Abstract

The present invention relates to a plain bearing pad (18) for a plain bearing (9), the plain bearing pad (18) having a bearing surface (20). In the region of the bearing surface (20), a lubricant-transporting groove (29) is formed in a first peripheral surface (28) of the plain bearing pad (18).

Description

Technical Field

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

Background Art

[0002] From Patent Document 1, a bearing element for supporting a rotor hub of a wind turbine is known.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] The problem of the present invention is to provide an improved sliding bearing.

Means for Solving the Problems

[0005] The above problem is solved by the device described in the claims.

[0006] According to the present invention, a sliding bearing pad is formed for the sliding bearing, and the sliding bearing pad has a bearing surface. A lubricating oil transport groove is formed in the first peripheral surface of the sliding bearing pad in the region of the bearing surface. Such a lubricating oil transport groove has the advantage that lubricating oil can be transported upward from the lubricating oil container by this lubricating oil transport groove, and thereby can be distributed over the mating surface of the ring element. By doing so, an improved lubricating effect in the sliding bearing can be achieved, and the life of the sliding bearing can be extended. Furthermore, this measure can eliminate the need for a lubricating oil pump.

[0007] Furthermore, the lubricating oil transport groove has a radial groove depth and a circumferential groove depth, with the circumferential groove depth being 10% to 300%, particularly 20% to 100%, and preferably 60% to 80%, of the radial groove depth. In particular, a lubricating oil transport groove sized in this way is remarkably well-suited for transporting lubricating oil.

[0008] Furthermore, the radial groove depth is considered to be 1 mm to 30 mm, particularly 3 mm to 18 mm, and preferably 6 mm to 13 mm.

[0009] Furthermore, the circumferential groove depth can be set to 1 mm to 30 mm, particularly 2 mm to 18 mm, and preferably 4 mm to 8 mm.

[0010] Furthermore, the radial groove bottom can be formed as a straight line when viewed in the groove cross-section. Such a cross-sectional view is shown in Figure 7. In particular, such a cross-sectional view can be formed as a cylindrical segment or a conical segment. This has the advantage that the lubricating oil transport groove formed in this way can be easily manufactured. In particular, grooves formed in this way can be manufactured by a milling cutter.

[0011] Furthermore, the bottom of the circumferential groove can be formed as a straight line when viewed in the groove cross-section. This has the advantage that lubricating oil transport grooves formed in this way can be easily manufactured. In particular, grooves formed in this way can be manufactured using a milling cutter.

[0012] An embodiment in which the lubricating oil transport groove extends axially along the sliding bearing pad is also advantageous. This approach can improve the volumetric performance of the lubricating oil transport groove.

[0013] Furthermore, the sliding bearing pad is used to be positioned between the inner ring element and the outer ring element, and is configured to be rigidly connected to the inner ring element in operation and to rotate relative to the outer ring element together with the inner ring element, the bearing surface has the basic shape of a spherical crown with a spherical crown radius at the spherical crown portion, the bearing surface of the sliding bearing pad is formed to abut the mating surface of the outer ring element, the lubricating oil transport groove extends in the axial direction of the sliding bearing pad, the lubricating oil transport groove has a first groove end positioned at a first distance from the first end face of the sliding bearing pad and a second groove end positioned at a second distance from the second end face of the sliding bearing pad, a first recess relative to the bearing surface is formed between the first groove end and the first end face of the sliding bearing pad, and a second recess relative to the bearing surface is formed between the second groove end and the second end face of the sliding bearing pad.

[0014] In one modification, the lubricating oil transport groove may have a first groove end positioned at a first distance from the first end face of the sliding bearing pad, and a second groove end positioned at a second distance from the second end face of the sliding bearing pad. This approach has the advantage of being able to close the lubricating oil transport groove at both of its axial ends, thereby improving the transport performance of the lubricating oil transport groove.

[0015] Furthermore, it may be advantageous if a first recess is formed between the first groove end and the first end face of the sliding bearing pad, and a second recess is formed between the second groove end and the second end face of the sliding bearing pad. This has the advantage that lubricating oil can flow from the lubricating oil sump through the recess into the groove in the axial direction, ensuring a sufficient supply of lubricating oil.

[0016] Furthermore, the depth of the first recess is considered to be between 2% and 50% of the radial groove depth, particularly between 5% and 30%, and preferably between 8% and 15%.

[0017] Furthermore, the depth of the second recess can be 2% to 50%, particularly 5% to 30%, and preferably 8% to 15%, of the depth of the radial groove. In particular, remarkably good lubrication of the sliding bearing surface can be achieved in the lubricating oil transport groove formed in this manner.

[0018] Furthermore, the lubricating oil transport groove can have a first transition radius toward the radial groove bottom at the first groove end, and a second transition radius toward the radial groove bottom at the second groove end. This has the advantage that the lubricating oil can be well retained in the lubricating oil transport groove formed in this way. Moreover, the lubricating oil transport groove formed in this way can be easily manufactured.

[0019] Furthermore, the transition radius can be set to 1 mm to 20 mm, particularly 3 mm to 15 mm, preferably 5 mm to 7 mm.

[0020] In an alternative embodiment, the lubricating oil transport groove may have a first transition radius toward the circumferential groove bottom at the first groove end, and a second transition radius toward the circumferential groove bottom at the second groove end. This has the advantage that the lubricating oil can be well retained in the lubricating oil transport groove formed in this manner. Moreover, the lubricating oil transport groove formed in this manner can be easily manufactured.

[0021] Furthermore, the radial groove bottom of the lubricating oil transport groove can have individual sub-regions, each of which can have a flat surface.

[0022] Furthermore, the bearing surface of each sliding bearing pad can be made to have a basic spherical shape with a spherical radius at the spherical crown portion. In particular, in a sliding bearing pad configured with such a sliding surface, the lubricating oil transport groove according to the present invention provides remarkably improved sliding characteristics.

[0023] According to a particular embodiment, the circumferential groove depth can be 0.5% to 20%, particularly 1.5% to 10%, preferably 3% to 7% of the bearing surface arc length of the bearing surface. This has the advantage that the lubricating oil transport groove formed in this way is well-suited for lubricating oil transport.

[0024] Furthermore, a lubricating oil suction port can be formed between the lubricating oil transport groove and the bearing surface. This has the advantage that the lubricating oil can be inhaled from the lubricating oil transport groove into the area of the bearing surface in an improved form. In particular, the lubricating oil inlet can be formed to taper starting from the lubricating oil transport groove.

[0025] In the first embodiment, the lubricating oil suction port can be formed with a step. In particular, different step surfaces can be provided, with the step surface closest to the lubricating oil transport groove having the greatest depth and the step surface closest to the bearing surface having the smallest depth.

[0026] In another embodiment, the lubricating oil suction port can be formed in a rounded shape when viewed in cross-section. In particular, the rounding has the greatest depth in the area of the lubricating oil transport groove and transitions tangentially to the bearing surface.

[0027] In another embodiment, the lubricating oil suction port can be formed in the shape of a wedge surface when viewed in cross-section.

[0028] According to the present invention, a sliding bearing is configured. The sliding bearing has an inner ring element, an outer ring element, and at least one sliding bearing element disposed between the inner ring element and the outer ring element, the sliding bearing element including at least two sliding bearing pads, where the bearing surface of the sliding bearing pad abuts against the mating surface of the outer ring element or the mating surface of the inner ring element. The sliding bearing pad is formed in accordance with any of the above-described modes.

[0029] The sliding bearings formed in this way have an astonishingly long lifespan and remarkably good sliding properties.

[0030] In the first embodiment, the sliding bearing pad can be connected to an inner ring element and have a mating surface formed on the outer ring element.

[0031] In an alternative embodiment, the sliding bearing pad can be connected to the outer ring element so that a mating surface is formed on the inner ring element.

[0032] In particular, it may be advantageous if a lubricating oil distribution groove extending in the circumferential direction is formed on the outer circumference of the outer ring element, and a lubricating oil hole is formed that fluidly connects this lubricating oil distribution groove to the mating surface, with the lubricating oil hole opening into an oil pocket in the region of the mating surface. This measure can further improve the supply of lubricating oil to the sliding bearing.

[0033] According to the present invention, a nacelle for a wind turbine is constructed. The nacelle is, Nacelle housing and Rotor shaft and The rotor hub is positioned on the rotor shaft, The rotor has a rotor bearing for supporting the rotor shaft in the nacelle housing. The rotor bearing includes a plurality of sliding bearing pads formed by any of the above embodiments.

[0034] Furthermore, it may be advantageous for the bearing surface of each sliding bearing pad to have a basic spherical shape with a spherical radius in the spherical cap portion and a transition radius in the transition portion.

[0035] In particular, it may be advantageous if a bearing block is configured that houses an outer ring element, and a cover is formed on at least one axial end face of this bearing block, and a lubricating oil container is formed within or connected to the cover. This has the advantage that the lubricating oil container thus formed can adequately store lubricating oil for the hydrodynamic sliding bearing.

[0036] According to a particular embodiment, the rotor bearing includes a bearing block housing an outer ring element, the bearing block having an axial stopper for the outer ring element, the axial stopper may be formed on the axial end face of the bearing block opposite to the rotor hub. This has the advantage that the axial stopper acts in the direction of the main load of the rotor bearing.

[0037] Embodiments in which the plain bearing is designed as a hydrodynamic plain bearing are also advantageous. In particular, hydrodynamic plain bearings have low frictional resistance and therefore high efficiency.

[0038] Furthermore, a permanent magnet can be placed inside the lubricating oil container. This has the advantage that ferromagnetic particles can adhere to the permanent magnet. As a result, the permanent magnet can perform the function of collecting impurities. Such impurities may be generated, for example, by wear on sliding surfaces or other forms of wear. Moreover, the permanent magnet can be placed in the lubricating oil container in a replaceable or removable manner to allow for cleaning of the permanent magnet.

[0039] To better understand the present invention, it will be described in more detail with reference to the following figures.

[0040] Each diagram is presented in a highly simplified, schematic representation. [Brief explanation of the drawing]

[0041] [Figure 1] Figure 1 is a schematic diagram of a wind turbine. [Figure 2] Figure 2 is a perspective view of a first embodiment of a sliding bearing. [Figure 3] Figure 3 is a perspective view of a longitudinal section of the first embodiment of a sliding bearing. [Figure 4] Figure 4 is a perspective view of a first embodiment of a rotor shaft with sliding bearing pads. [Figure 5] Figure 5 is a longitudinal section of another embodiment of a sliding bearing. [Figure 6] Figure 6 is a perspective view of another embodiment of a sliding bearing pad. [Figure 7] Figure 7 is a cross-sectional view of a sliding bearing pad along the cutting line VII-VII in Figure 6. [Figure 8] Figure 8 is a perspective view of another embodiment of a sliding bearing. [Modes for carrying out the invention]

[0042] First, it should be noted that the same component is given the same reference numeral or part name in the different embodiments described. In this case, the disclosures contained throughout the description can be applied mutatis mutandis to the same component having the same reference numeral or part name. Words used to describe selected positions in the description, such as top, bottom, and side, are based on the diagrams shown and directly described, and these positional words will apply mutatis mutandis to the new position if the position changes.

[0043] Figure 1 is a schematic diagram of a first embodiment of a wind turbine for generating electrical energy from wind power. The wind turbine 1 has a nacelle 2 that is rotatably held in a tower 3. The nacelle 2 includes a nacelle housing 4 which forms the main structure of the nacelle. Electrical components such as the generator of the wind turbine 1 are located inside the nacelle housing 4 of the nacelle 2.

[0044] Furthermore, a rotor 5 is formed having a rotor hub 6 and rotor blades 7 attached thereto. The rotor hub 6 is considered part of the nacelle. The rotor hub 6 is rotatably held in the nacelle housing 4 by a rotor bearing 8. In particular, the sliding bearing 9 according to the present invention, which is detailed below, is used as the rotor bearing 8. Specifically, the rotor hub 6 can be positioned on the rotor shaft 16 so that the rotor shaft 16 is supported by the rotor bearing 8.

[0045] The rotor bearing 8, which supports the rotor hub 6 in the nacelle housing 4 of the nacelle 2, is configured to absorb radial forces 10 and axial forces 11. The axial force 11 is generated by wind force. The radial force 10 is generated by the gravity of the rotor 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, the radial force 10 causes a tilt moment 12 within the rotor bearing 8. The tilt moment 12 is also caused by uneven loading on the rotor blades 7. This tilt moment 12 can be absorbed by a second bearing positioned at a distance from the rotor bearing 8. The second bearing can be formed, for example, in the area of ​​the generator.

[0046] Figure 2 shows a first embodiment of the sliding bearing 9 installed inside the nacelle 2. Of course, the sliding bearing 9 shown in Figure 2 can be used in any industrial application other than wind turbines. In Figure 2, the sliding bearing 9 is shown in a perspective view.

[0047] Figure 3 shows a first embodiment of the sliding bearing 9 in a perspective longitudinal section view.

[0048] In the following section, the sliding bearing 9 will be described with reference to Figures 2 and 3.

[0049] As can be seen from Figures 2 and 3, the sliding bearing 9 can have an inner ring element 13 and an outer ring element 14. A sliding bearing element 15 is positioned between the inner ring element 13 and the outer ring element 14, and this sliding bearing element 15 acts as a sliding bearing for the inner ring element 13, which rotates relative to the outer ring element 14.

[0050] In the embodiments shown in Figures 2 and 3, the inner ring element 13 is formed as the rotor shaft 16. Of course, the inner ring element 13 may be a different shaft. Furthermore, it is also conceivable that the inner ring element 13 be formed as an independent member and held by the shaft, particularly the rotor shaft 16.

[0051] As can be seen particularly clearly in Figure 3, the outer ring element 14 can be held within the bearing block 17. In particular, the bearing block 17 can be connected to the nacelle housing 4, or alternatively, molded directly within the nacelle housing 4. In this embodiment, the outer ring element 14 is thus rigidly connected to the nacelle housing 4, and the inner ring element 13 can be rotatable relative to the outer ring element 14 about the rotation axis 19 by the sliding bearing element 15.

[0052] Furthermore, the bearing block 17 can be configured to function directly as the outer ring element 14.

[0053] As a result, the rotor shaft 16 is rotatably held within the nacelle housing 4 by the sliding bearing 9.

[0054] As can be further seen from Figures 2 and 3, the sliding bearing element 15 includes a plurality of individual sliding bearing pads 18 distributed circumferentially between the inner ring element 13 and the outer ring element 14.

[0055] Each sliding bearing pad 18 is rigidly connected to the inner ring element 13 in the operating state of the sliding bearing 9 by the structure shown in Figure 3, thereby rotating together with the inner ring element 13 relative to the outer ring element 14. To enable rotational movement between the inner ring element 13 and the outer ring element 14, each sliding bearing pad 18 has a bearing surface 20 formed thereon, which contacts the mating surface 21 of the outer ring element 14 in the usable state of the sliding bearing 9. This mating surface 21 is located on the inner surface 22 of the outer ring element 14.

[0056] The bearing surface 20 of the sliding bearing pad 18 and the mating surface 21 of the outer ring element 14 are formed as sliding surfaces that come into contact with and slide against each other during the operation of the sliding bearing 9. In particular, the mating surface 21 of the outer ring element 14 is formed as a wear-resistant, hard surface, which can be made of, for example, hardened steel. The bearing surface 20 of the sliding bearing pad 18 can be made of a sliding bearing material that is softer than the mating surface. Of course, the bearing surface 20 may also be provided with a sliding coating.

[0057] As can be seen particularly clearly in Figure 3, each individual sliding bearing pad 18 can have a bearing surface 20 that is curved when viewed in the axial direction.

[0058] As can be seen further in Figure 3, a cover 24 can be positioned on the axial end face 23 of the bearing block 17. This cover 24 is used to enclose the inside of the bearing block 17.

[0059] As can be seen further in Figure 3, a lubricating oil container 25 used to hold lubricating oil 26 can be connected to the cover 24. In particular, in this case, a through hole 27 is formed inside the cover 24, allowing the lubricating oil 26 to flow from the lubricating oil container 25 into the interior of the bearing block 17 through this through hole.

[0060] Of course, it is also possible that the lubricating oil container 25 is located in a different place on the bearing block 17.

[0061] Figure 4 shows a perspective view of the rotor shaft 16 and the sliding bearing pad 18 positioned thereon. Here again, the same reference numerals or names are used for the same components as in Figures 1 to 3. To avoid unnecessary repetition, the detailed explanations in Figures 1 to 3 are noted and referred to.

[0062] As can be seen from Figure 4, the individual sliding bearing pads 18 can be distributed circumferentially and held by the inner ring element with spacing between them in the circumferential direction.

[0063] As can be seen in Figure 5, a lubricating oil distribution groove 30 extending in the circumferential direction can be formed on the outer circumference of the outer ring element 14. This lubricating oil distribution groove 30 can be formed on the surface where the outer ring element 14 abuts against the bearing block 17. In this case, the lubricating oil distribution groove 30 is partitioned by the outer ring element 14 and the bearing block 17, thereby forming a flow path for transporting lubricating oil. Furthermore, a lubricating oil hole 31 can be formed to fluidly connect the lubricating oil distribution groove 30 and the mating surface 21. This has the advantage that lubricating oil can be supplied to the sliding bearing pad 18 via the lubricating oil distribution groove 30 using an oil pump.

[0064] Furthermore, the lubrication hole 31 can be made to open into the oil pocket 32. The oil pocket 32 ​​can extend axially from the outer ring element.

[0065] Furthermore, seals can be placed on both sides of the lubricating oil distribution groove 30 to serve the function of sealing the lubricating oil distribution groove 30 between the outer ring element 14 and the bearing block 17.

[0066] Figure 6 shows the sliding bearing pad 18 in a first perspective view. Figure 7 shows the sliding bearing pad 18 of Figure 6 in a cross-sectional view.

[0067] As can be seen from Figure 6, a lubricating oil transport groove 29 is formed on the first circumferential surface 28 of the sliding bearing pad 18. This lubricating oil transport groove 29 can be formed in the area of ​​the bearing surface 20. In particular, the lubricating oil transport groove 29 can be positioned to interrupt the bearing surface 20.

[0068] As can be seen from Figure 7, the lubricating oil transport groove 29 can have a radial groove depth 33. Furthermore, the lubricating oil transport groove 29 can have a circumferential groove depth 34. In particular, in this case, the lubricating oil transport groove 29 has a radial groove bottom 35 and a circumferential groove bottom 36.

[0069] As can be seen particularly clearly from Figure 6, the first groove end 38 can be formed on the first end face 37 of the sliding bearing pad 18, and it can be positioned at a first distance 39 from the first end face 37.

[0070] As can be seen further from Figure 6, a second groove end 41 is formed in the region of the second end face 40 of the sliding bearing pad. The second groove end 41 can be positioned at a second distance 42 from the second end face 40.

[0071] As can be seen further from Figure 6, a first recess 43 is formed in the region of the first groove end 38. This first recess 43 can be formed in the form of a recess relative to the bearing surface 22. As can be seen further from Figure 6, a second recess 44 can be formed in the region of the second groove end 41. This second recess 44 can be a recess relative to the bearing surface 20.

[0072] As can be seen further from Figure 6, a first transition radius 45 can be formed between the radial groove bottom 35 and the first groove end 38 of the lubricating oil transport groove 29.

[0073] Furthermore, a second transition radius 46 can be formed between the radial groove bottom 35 and the second groove end 41.

[0074] As can be seen further in Figure 6, a lubricating oil intake port 51 can be formed between the lubricating oil transport groove 29 and the bearing surface 20. As can be seen in Figure 6, the lubricating oil intake port 51 can be formed with steps, and may have a first stepped surface 52, a second stepped surface 53, and a third stepped surface 54. Of course, more or fewer individual stepped surfaces can also be formed.

[0075] As can be seen from Figure 7, the bearing surface 20 can have a bearing surface arc length 47. The bearing surface arc length 47 is measured in the circumferential direction of the bearing surface 20. In particular, the bearing surface arc length 47 is measured at the minimum diameter of the bearing surface.

[0076] As can be clearly seen in Figure 6, the bearing surface 20 can be formed in the shape of a spherical cap. In particular, a spherical cap portion 49 with a spherical cap radius of 50 can be formed.

[0077] Figure 8 shows another, possibly independent, embodiment of the sliding bearing pad 18, where the same reference numerals or names are used for the same components as in Figures 1-7. To avoid unnecessary repetition, the detailed descriptions in Figures 1-7 are noted and referenced.

[0078] As can be seen from Figure 8, the radial groove bottom 35 can have a first sub-region 55, a second sub-region 56, and a third sub-region 57 along its entire length. Of course, it is also possible to form more or fewer individual sub-regions.

[0079] The above embodiments illustrate possible forms, and it should be noted here that the present invention is not limited to the embodiments specifically illustrated, and conversely, the individual embodiments can be combined in various ways, and this modifiability is within the scope of the ability of those skilled in the art who are engaged in the art based on the teachings relating to the technical acts of the present invention.

[0080] The scope of protection is defined by the claims. However, the detailed description and drawings must be used to interpret the claims. The individual features or combinations of features described in the different embodiments illustrated and described can constitute independent inventive solutions in themselves. The problems underlying these independent inventive solutions can be read from this specification.

[0081] In the description of this invention, all indications relating to a range of values ​​should be understood to include any subranges within that range. For example, the indication 1 to 10 should be understood to include all subranges from the lower limit of 1 to the upper limit of 10. That is, all subranges start at or above the lower limit of 1 and end at or below the upper limit of 10, for example, 1 to 1.7, 3.2 to 8.1, or 5.5 to 10.

[0082] Finally, as a formal point, in order to make the structure easier to understand, some elements were not depicted to scale, and / or enlarged, and / or reduced. According to embodiment (1), a sliding bearing pad (18) for a sliding bearing (9) having a bearing surface (20), The sliding bearing pad (18) is characterized in that a lubricating oil transport groove (29) is formed on the first circumferential surface (28) of the sliding bearing pad (18) in the region of the bearing surface (20). According to embodiment (2), the lubricating oil transport groove (29) has a radial groove depth (33) and a circumferential groove depth (34), wherein the circumferential groove depth (34) is 10% to 300%, particularly 20% to 100%, and preferably 60% to 80%, of the radial groove depth (33). According to embodiment (3), the radial groove bottom (35) is formed as a straight line when viewed in the groove cross-section. According to embodiment (4), the circumferential groove bottom (36) is formed as a straight line when viewed in the groove cross-section. According to embodiment (5), the sliding bearing pad (18) is used to be positioned between the inner ring element (13) and the outer ring element (14), and the sliding bearing pad (18) is configured to be tightly connected to the inner ring element (13) in the operating state and to rotate together with the inner ring element (13) relative to the outer ring element (14), the bearing surface (20) has the basic shape of a spherical cap with a spherical cap radius (50) in the spherical cap portion (49), the bearing surface (20) of the sliding bearing pad (18) is formed to abut against the mating surface (21) of the outer ring element (14), and the lubricating oil transport groove (29) is the sliding bearing pad (1 8) Extending in the axial direction, the lubricating oil transport groove (29) has a first groove end (38) positioned at a first distance (39) from the first end face (37) of the sliding bearing pad (18), and a second groove end (41) positioned at a second distance (42) from the second end face (40) of the sliding bearing pad (18), wherein a first recess (43) with respect to the bearing surface (20) is formed between the first groove end (38) and the first end face (37) of the sliding bearing pad (18), and a second recess (44) with respect to the bearing surface (20) is formed between the second groove end (41) and the second end face (40) of the sliding bearing pad (18). According to embodiment (6), the lubricating oil transport groove (29) is characterized by having a first groove end (38) positioned at a first distance (39) from the first end face (37) of the sliding bearing pad (18), and a second groove end (41) positioned at a second distance (42) from the second end face (40) of the sliding bearing pad (18). According to embodiment (7), a first recess (43) relative to the bearing surface (20) is formed between the first groove end (38) and the first end face (37) of the sliding bearing pad (18), and a second recess (44) relative to the bearing surface (20) is formed between the second groove end (41) and the second end face (40) of the sliding bearing pad (18). According to embodiment (8), the lubricating oil transport groove (29) has a first transition radius (45) toward the radial groove bottom (35) at the first groove end (38), and the lubricating oil transport groove (29) has a second transition radius (46) toward the radial groove bottom (35) at the second groove end (41). According to embodiment (9), the bearing surface (20) of each sliding bearing pad (18) is characterized in that the spherical cap portion (49) has a basic spherical shape with a spherical cap radius (50). According to embodiment (10), the circumferential groove depth (34) is characterized by being 0.5% to 20%, particularly 1.5% to 10%, and preferably 3% to 7%, of the bearing surface arc length (47) of the bearing surface (20). According to embodiment (11), a lubricating oil inlet (51) is formed between the lubricating oil transport groove (29) and the bearing surface (20). According to embodiment (12), the sliding bearing (9) is, Inner ring element (13), Outer ring element (14), The system includes at least one sliding bearing element (15) disposed between the inner ring element (13) and the outer ring element (14), the sliding bearing element (15) including at least two sliding bearing pads (18), In a sliding bearing (9), the bearing surface (20) of the sliding bearing pad (18) and the mating surface (21) of the outer ring element (14) or the mating surface (21) of the inner ring element (13) are in contact with each other. The sliding bearing (9) is characterized in that the sliding bearing pad (18) is formed according to any one of claims 1 to 10. According to embodiment (13), the sliding bearing (9) according to 12 is characterized in that a lubricating oil distribution groove (30) extending in the circumferential direction is formed on the outer circumference (48) of the outer ring element (14), a lubricating oil hole (31) is formed that fluidly connects the lubricating oil distribution groove (30) to the mating surface (21), and the lubricating oil hole (31) opens into an oil pocket (32) in the region of the mating surface (21). According to embodiment (14), the nacelle (2) for the wind turbine (1) is, Nacelle housing (4) and Rotor shaft (16) and The rotor hub (6) is positioned on the rotor shaft (16), A nacelle (2) having a rotor bearing (8) for supporting the rotor shaft (16) in the nacelle housing (4), A nacelle (2) for a wind turbine (1), characterized in that the rotor bearing (8) has a sliding bearing pad (18) according to any one of claims 1 to 10. [Explanation of symbols]

[0083] 1 Wind Turbine 2 Nacer 3 towers 4 Nacelle Housing 5 rotors 6 rotor hubs 7 rotor blades 8 rotor bearings 9. Plain bearings 10 Radial force 11 Axial force 12. Moment of inclination 13 Inner ring elements 14 Outer ring elements 15. Sliding bearing elements 16 rotor shaft 17. Bearing block 18 Plain bearing pads 19 Rotation axis 20 Bearing surface 21 Opponent's side 22 Inner self 23 Axial end face of bearing block 24 Cover 25 Lubricating oil container 26 Lubricating oil 27 Through hole 28 Peripheral surface 29 Lubricating oil transport groove 30 Lubricating oil distribution groove 31 Lubricant hole 32 Oil pockets 33 Radial groove depth 34. Circumferential groove depth 35 Radial groove bottom 36 Circumferential groove bottom 37 First end surface 38 End of first groove 39. First distance 40 Second end face 41 End of the second groove 42 Second distance 43. First recess 44. Second recess 45 First transition radius 46. ​​Second transition radius 47. Bearing surface arc length 48 Outer circumference of the outer ring element 49 Crown part 50 crown radius 51 Lubricant intake port 52 1st step surface 53 2nd step surface 54 3rd step surface 55 First partial region of the bottom of the radial groove 56 Second partial region of the radial groove bottom 57 Third sub-region of the radial groove bottom

Claims

1. A sliding bearing pad (18) for a sliding bearing (9), having a bearing surface (20), A lubricating oil transport groove (29) is formed on the first circumferential surface (28) of the edge of the bearing surface (20) of the sliding bearing pad (18). The sliding bearing pad (18) is used to be positioned between the inner ring element (13) and the outer ring element (14). The sliding bearing pad (18) is configured to be rigidly connected to the inner ring element (13) in the operating state and to rotate together with the inner ring element (13) relative to the outer ring element (14). The bearing surface (20) has a basic spherical shape with a spherical radius (50) in the spherical cap portion (49), The bearing surface (20) of the sliding bearing pad (18) is formed to contact the mating surface (21) of the outer ring element (14), The lubricating oil transport groove (29) extends in the axial direction of the sliding bearing pad (18), The lubricating oil transport groove (29) has a first groove end (38) positioned at a first distance (39) from the first end face (37) of the sliding bearing pad (18), and a second groove end (41) positioned at a second distance (42) from the second end face (40) of the sliding bearing pad (18). A first recess (43) relative to the bearing surface (20) is formed between the first groove end (38) and the first end face (37) of the sliding bearing pad (18). A sliding bearing pad (18) is characterized in that a second recess (44) is formed between the second groove end (41) and the second end face (40) of the sliding bearing pad (18) relative to the bearing surface (20).

2. The sliding bearing pad (18) according to claim 1, characterized in that the lubricating oil transport groove (29) has a radial groove depth (33) and a circumferential groove depth (34), and the circumferential groove depth (34) is 10% to 300% of the radial groove depth (33).

3. The sliding bearing pad (18) according to Claim 2, characterized in that the circumferential groove depth (34) is 20% to 100% of the radial groove depth (33).

4. The sliding bearing pad (18) according to claim 3, characterized in that the circumferential groove depth (34) is 60% to 80% of the radial groove depth (33).

5. The sliding bearing pad (18) according to claim 1 or 2, characterized in that the radial groove bottom (35) is formed as a straight line when viewed in the groove cross-section.

6. A sliding bearing pad (18) according to any one of claims 1 to 5, characterized in that the bottom portion (36) of the circumferential groove is formed as a straight line when viewed in the cross-section of the groove.

7. The sliding bearing pad (18) according to any one of claims 1 to 6, characterized in that the lubricating oil transport groove (29) has a first groove end (38) positioned at a first distance (39) from the first end face (37) of the sliding bearing pad (18) and a second groove end (41) positioned at a second distance (42) from the second end face (40) of the sliding bearing pad (18).

8. A sliding bearing pad (18) according to claim 7, characterized in that a first recess (43) is formed between the first groove end (38) and the first end face (37) of the sliding bearing pad (18) with respect to the bearing surface (20), and a second recess (44) is formed between the second groove end (41) and the second end face (40) of the sliding bearing pad (18) with respect to the bearing surface (20).

9. The sliding bearing pad (18) according to claim 7 or claim 8, characterized in that the lubricating oil transport groove (29) has a first transition radius (45) toward the radial groove bottom (35) at the first groove end (38), and the lubricating oil transport groove (29) has a second transition radius (46) toward the radial groove bottom (35) at the second groove end (41).

10. The sliding bearing pad (18) according to any one of claims 1 to 9, characterized in that the bearing surface (20) of each sliding bearing pad (18) has a basic shape of a spherical crown with a spherical crown radius (50) in the spherical crown portion (49).

11. The sliding bearing pad (18) according to claim 2, characterized in that the circumferential groove depth (34) is 0.5% to 20% of the bearing surface arc length (47) of the bearing surface (20).

12. The sliding bearing pad (18) according to claim 11, characterized in that the circumferential groove depth (34) is 1.5% to 10% of the bearing surface arc length (47) of the bearing surface (20).

13. The sliding bearing pad (18) according to claim 12, characterized in that the circumferential groove depth (34) is 3% to 7% of the bearing surface arc length (47) of the bearing surface (20).

14. A sliding bearing pad (18) according to any one of claims 1 to 13, characterized in that a lubricating oil intake port (51) is formed between the lubricating oil transport groove (29) and the bearing surface (20).

15. A sliding bearing (9), The inner ring element (13) and, The outer ring element (14) and, The system includes at least one sliding bearing element (15) disposed between the inner ring element (13) and the outer ring element (14), the sliding bearing element (15) including at least two sliding bearing pads (18), In a sliding bearing (9), the bearing surface (20) of the sliding bearing pad (18) and the mating surface (21) of the outer ring element (14) or the mating surface (21) of the inner ring element (13) are in contact with each other. The sliding bearing (9) is characterized in that the sliding bearing pad (18) is formed according to any one of claims 1 to 13.

16. A nacelle (2) for a wind turbine (1), Nacelle housing (4) and Rotor shaft (16) and The rotor hub (6) is positioned on the rotor shaft (16), In a nacelle (2) having a rotor bearing (8) for supporting the rotor shaft (16) in the nacelle housing (4), The rotor bearing (8) A nacelle (2) for a wind turbine (1), characterized by having a sliding bearing pad (18) according to any one of claims 1 to 13.

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