Blade bearing

Abstract

The following embodiments relate to a blade bearing comprising: a bearing inner ring (12) and a bearing outer ring (14), wherein the bearing inner ring (12) is indirectly or directly connected to the bearing outer ring (14) via at least one row of rolling elements (16); a gap (18) extending in the axial and circumferential direction between the bearing inner ring (12) and the bearing outer ring (14); an annular gap seal (20) arranged at least partially within the gap (18); wherein the gap seal (20) has a sealing foot (22) for fastening the gap seal (20) within an anchor groove (24) extending in the circumferential direction of the bearing inner ring (12), wherein the gap seal (20) has a first sealing lip (26) extending from the sealing foot (22) and a second sealing lip (28) for contacting the outer bearing ring (14), wherein the bearing outer ring (14) has a sealing groove (30), which is open towards the gap (18) and extends in the circumferential direction, for at least partially receiving the first sealing lip (26), and has a projection (32) which is adjacent to the sealing groove (30) and extends in the circumferential direction, wherein the projection (32) is arranged at least partially between the first sealing lip (26) and the second sealing lip (28), and wherein the first sealing lip (26) has at least a first sealing edge (34) for contacting a first sealing surface (36) and a second sealing edge (38) for contacting a second sealing surface (40) within the sealing groove (30), wherein the first sealing edge (34) has a mounting groove (42), which is open substantially in the direction of the gap (18) and extends in the circumferential direction, for receiving a mounting tool (64) and / or for receiving lubricant.

Description

[0001] Leaf bearing

[0002] Technical field

[0003] The following descriptions concern a blade bearing, particularly for a wind turbine, with a gap seal, which saves axial installation space. Furthermore, the following descriptions concern a wind turbine with said blade bearing.

[0004] Technical background

[0005] In blade bearings, particularly for use in wind turbines, static gap seals are used to prevent grease leakage. "Static" means that the gap seal seals the gap between the bearing rings both during stationary (stationary) and during rotational movements of the inner or outer bearing rings. During operation, the blade bearing performs a pivoting movement to adjust the blade angle for optimal wind power utilization.

[0006] The purpose of sealing blade bearings is twofold: firstly, to prevent grease from escaping the bearing interior, thus preventing environmental contamination and lubricant depletion inside the bearing; and secondly, to prevent the ingress of solid contaminants and liquids from the outside, which could impair the bearing's function, for example, through corrosion or mechanical damage. Therefore, the gap seals must ensure complete tightness during operation. Simultaneously, the gap seal must bridge any changes in the sealing gap caused by deformation and displacement due to load-induced radial movement of the rings relative to each other without leakage. These changes in the sealing gap are particularly significant in large bearings and can easily amount to several millimeters. During operation, increased internal pressure can build up inside the blade bearing.The gap seal must therefore ensure a reliable seal even under increased internal bearing pressures.

[0007] Furthermore, it is necessary to relubricate the bearing at regular intervals to ensure normal operation and a sufficient service life. However, there is a risk that high local pressures may occur during relubrication, which can lead to grease leakage and even damage and leakage of the gap seal.

[0008] Another essential characteristic that a gap seal for blade bearings must possess is its reliable installation capability. It must be ensured that the gap seal reliably assumes a defined position within the installation space, a position that remains unchanged during operation and under (local) overpressure. This aspect is particularly crucial for large bearings, as even slight misalignment can lead to leaks and seal failure.

[0009] From EP 2 672 133 Bl, a large rolling bearing with a gap seal that seals the gap between the bearing rings is known. A gap seal for large rolling bearings must meet various requirements, listed above and below.

[0010] In blade bearings, the widening of the gap between the bearing rings, caused by the loads acting on the bearing rings during operation, increases with the bearing ring diameter for a given load. This applies, for example, to blade bearings of wind turbines, which are subjected to both large static loads (e.g., bending moments due to the weight of the rotor blade) and high dynamic loads (e.g., due to the wind-induced forces and moments transmitted by the rotor blade) during operation. As a rule of thumb, the gap between the bearing rings widens by approximately 1 millimeter for every meter of increase in the inner bearing ring diameter.

[0011] A reliably functioning gap seal must be able to compensate for such gap widening without losing its sealing effect. Furthermore, a gap seal must reliably seal the gap between the bearing rings both in static conditions (i.e., in the case of blade bearings, for example, when the rotor blade is stationary) and in dynamic conditions (i.e., in the case of blade bearings, for example, when the rotor blade is rotating around the rotor hub at varying speeds).

[0012] A gap seal must also be able to withstand an overpressure inside the bearing, such as 3 bar or more, which may occur during operation or be deliberately introduced into the bearing, without negatively affecting the sealing effect.

[0013] Finally, the gap seal must be as easy and safe to install as possible; in particular, incorrect installation of the gap seal that negatively impairs the sealing effect must be avoided.

[0014] The object of the invention is to provide a blade bearing with improved sealing and a smaller axial installation space.

[0015] Starting from this situation, the present problem is to propose a blade bearing in which the required axial installation space can be reduced cost-effectively by using a gap seal according to the invention.

[0016] Description - Technical Solution

[0017] The present problem is solved by the features of the independent claim. Advantageous embodiments are specified in the dependent claims, the description, and the drawings. Where technically feasible, the teachings of the dependent claims can be combined arbitrarily with those of the main and dependent claims.

[0018] In particular, the problem is solved by a blade bearing, especially for a wind turbine, comprising:

[0019] - an inner bearing ring and an outer bearing ring, wherein the inner bearing ring is connected to the outer bearing ring indirectly or directly via at least one row of rolling elements;

[0020] - a gap extending axially and circumferentially between the inner bearing ring and the outer bearing ring; - an annular gap seal arranged at least partially within the gap;wherein the gap seal has a sealing base for force-fit and / or form-fit fastening of the gap seal within an anchor groove (24) extending in the circumferential direction of a bearing ring, wherein the gap seal has a first sealing lip extending from the sealing base and a second sealing lip for contacting the bearing ring opposite the bearing ring with the anchor groove, wherein the bearing ring opposite the bearing ring with the anchor groove has a sealing groove open towards the gap and extending in the circumferential direction for at least partially receiving the first sealing lip and a projection adjacent to the sealing groove and extending in the circumferential direction, wherein the projection is arranged at least partially between the first sealing lip and the second sealing lip.

[0021] Within the scope of the present invention, the anchor groove can be provided in the inner bearing ring. In this case, the sealing groove is arranged in the outer bearing ring. This arrangement is described further below and illustrated in the figures. However, other embodiments of the invention are also conceivable in which the anchor groove is located in the outer bearing ring and the sealing groove in the inner bearing ring. To simplify the wording in this description and improve the readability of the text, exemplary embodiments are described below in which the anchor groove is located in the inner bearing ring and the sealing groove in the outer bearing ring, without this limiting the disclosure of the invention to this arrangement.

[0022] By positioning the sealing base of the gap seal on the inner bearing ring, an additional sealing surface on the inner bearing ring can be omitted, thus reducing the axial installation space of the inner bearing ring. Extending from the sealing base, the first and second sealing lips face the outer bearing ring. The first sealing lip can be inserted into the sealing groove and, together with the sealing base, seals against a large portion of the internal bearing pressure acting on the gap seal. Both the first and second sealing lips extend circumferentially. Consequently, both the first and second sealing lips are circumferentially ring-shaped.

[0023] The following sections explain advantageous aspects and subsequently describe preferred modified embodiments. Explanations, particularly regarding advantages and definitions of features, are essentially descriptive and preferred, but not limiting, examples. If an explanation is limiting, this will be explicitly stated.

[0024] Where ordinal numbers, such as "first," "second," etc., are used, for example to designate a component, an element, a process step, or a process action, these ordinal numbers are solely for differentiation in the designation and do not indicate any dependencies or sequences. This means, in particular, that a device does not need to have a "first component" to have a "second component." A device can also have a "first component" and a "third component" without necessarily having a "second component." Multiple units with the same ordinal number are also possible, for example, multiple "first components."

[0025] The complete sealing of the blade bearing is achieved through a combination of the first and second sealing lips. During operation, these prevent grease from escaping into the gaps between the seal and the installation space and from being subsequently transported further by "pumping mechanisms." By positioning the gap seal within the annular space on the inner bearing ring, the sealing performance of the gap seal is significantly increased, and the required axial installation space of the inner bearing ring is reduced.

[0026] The sealing effect of the gap seal is significantly improved compared to the prior art, particularly when there is increased internal pressure inside the bearing. This is because the curved section of the first sealing lip, located in the gap and interacting with a fourth sealing surface, is pressed against this fourth sealing surface by the internal bearing pressure. This fourth sealing surface is formed on a projection of the outer bearing ring, especially on the mounting chamfer. This increases the sealing effect of the gap seal, even when the bearing rings move radially relative to each other under load. Furthermore, this reduces the risk of the gap seal being forced out of its installed position by overpressure inside the bearing. Overpressure present inside the bearing during operation ensures that the first sealing lip is pressed against a first sealing surface located within the sealing groove, thereby increasing the sealing effect.Furthermore, the first sealing lip is arranged to be displaceable within the sealing groove, so that the sealing effect of the first sealing lip is maintained even when the bearing rings move relative to each other.

[0027] The gap seal according to the invention achieves, in particular, an overpressure resistance of greater than 3 bar, and especially greater than 5 bar, because with small to medium sealing gap expansions, only the sealing base and the first sealing lip are subjected to overpressure, while the second sealing lip can assume and maintain a defined, stable position in the installation space. This has the positive effect that the rotational resistance also remains low, since, in particular, the second sealing lip is not additionally pressed against the third sealing surface by the overpressure, which would increase friction and thus rotational resistance and wear.

[0028] Overall, the gap seal according to the invention, the manner of its arrangement in the gap between the bearing rings and the interaction of the first and second sealing lips with the sealing surfaces formed on the outer bearing ring provide a blade bearing which, compared to the prior art, has a significantly improved sealing, less wear and less axial installation space for the inner bearing ring.

[0029] The gap seal can be designed as an extruded sealing profile and can consist in particular of the materials NBR (Nitrile Butadiene Rubber), HNBR (Hydrogenated Nitrile Butadiene Rubber) or FKM (Fluoro-rubber).

[0030] Alternatively or additionally, the first sealing lip may have at least one first sealing edge for contacting a first sealing surface and a second sealing edge for contacting a second sealing surface within the sealing groove. In particular, the first sealing edge may have a mounting groove, open substantially in the direction of the gap and extending circumferentially, for receiving a mounting tool and / or for receiving lubricant. The first and second sealing surfaces are, in particular, two surfaces arranged parallel to each other and opposite each other within the sealing groove. The mounting groove of the first sealing edge allows the first sealing lip to be securely inserted into the sealing groove. For this purpose, a first edge of a curved mounting tool can be placed in the mounting groove, and the first sealing lip can be moved or inserted into the sealing groove by the mounting tool.

[0031] Alternatively or additionally, the first sealing lip can be slidably mounted within the sealing groove. Specifically, it is provided that the first sealing lip is slidably mounted within the sealing groove by at least 1 millimeter per 1 meter of bearing inner ring diameter. In particular, it is provided that the first sealing lip is slidably mounted within the sealing groove by at least one millimeter, and especially by at least two millimeters. Static and dynamic loads on the blade bearing can cause relative movements of the bearing rings to change the gap width. To ensure continued adequate sealing by the gap seal, the first sealing lip is slidably mounted within the sealing groove. This allows the gap to be reliably sealed even with larger fluctuations in its width.

[0032] Alternatively or additionally, the projection can be provided with a circumferentially extending mounting chamfer adjacent to the sealing groove to facilitate the installation of the first sealing lip within the sealing groove. This simplifies the installation of the gap seal into the sealing groove. The mounting chamfer prevents deformation of the first sealing lip, the first sealing edge, and the second sealing edge when the gap seal is inserted into the sealing groove by increasing the clearance for the curved section of the first sealing lip. This additional clearance facilitates the insertion of the first sealing lip, along with the first and second sealing edges, into the sealing groove and simultaneously protects the first sealing lip and the first and second sealing edges from damage. The mounting chamfer serves, in particular, as an additional, pressure-dependent fourth sealing surface.At increased pressures in the gap, the first sealing lip can be pressed against the mounting chamfer, further improving the sealing effect of the gap seal. In particular, the projection is formed integrally with the bearing outer ring. This eliminates the need for additional seals.

[0033] Alternatively or additionally, the second sealing lip may contact a third sealing surface extending circumferentially on the outside of the bearing ring having the sealing groove by means of a third sealing edge. In particular, the third sealing edge is designed as a multi-stage sealing edge and has a plurality of circumferentially extending contact elements designed to make contact with the third sealing surface. Specifically, the second sealing lip prevents the ingress of dirt and / or liquids into the gap. Sealing against the ingress of rainwater, splash water, and contaminants into the gap of the blade bearing is achieved via the multi-stage sealing edge of the second sealing lip. The preload of the second sealing lip can be adjusted to the sealing gap requirements via the lip angle and the sealing lip length, taking into account the installation limitations.The sealing requirement, particularly against water ingress, is achieved by combining several contact elements arranged in series on the multi-stage third sealing edge. The grooves between the contact elements can be designed as pressure chambers, allowing the back pressure acting on the outside in front of the second sealing lip to dissipate. This functional principle promotes a higher level of sealing against the ingress of contaminants, rain, and splash water into the blade bearing gap. The number of contact elements is at least two, preferably at least three, and particularly at least four. Generally, a high number of contact elements ensures that the gap remains sealed even under static and / or dynamic gap changes.

[0034] Alternatively or additionally, the third sealing surface can extend at least partially along the projection. This third sealing surface is located on the outer side of the bearing's outer ring. This prevents dirt and liquids from penetrating the gap.

[0035] Alternatively or additionally, the longitudinal axis of the sealing groove and the longitudinal axis of the projection can be arranged to run essentially parallel to each other in cross-section. This ensures that the second and third sealing surfaces are also arranged parallel to each other on the outer bearing ring.

[0036] Alternatively or additionally, the sealing base may be provided with at least one projecting, circumferentially extending fastening element for the frictional and / or positive locking of the gap seal within the anchor groove. In particular, the at least one fastening element is designed as a barb, especially in the form of an anchor seal. The at least one fastening element allows the gap seal to be securely mounted to the inner bearing ring. Alternatively or additionally, the sealing base may be provided with at least one projecting, circumferentially extending stop element for positive locking to limit the installation depth of the sealing base within the anchor groove. This ensures that the gap seal is properly mounted to the inner bearing ring.

[0037] Alternatively or additionally, the bearing ring with the anchor groove may have a lubricant bore extending to the gap between the at least one row of rolling elements and the anchor. Lubricant can be introduced into the gap through this bore, lubricating the at least one row of rolling elements arranged between the inner and outer bearing rings. The introduction of lubricant increases the pressure within the gap. The gap seal is designed to withstand this pressure, and / or to press the first sealing lip against the opposite mounting chamfer, and / or to displace the first sealing lip deeper into the sealing groove. This further enhances the sealing of the gap by the gap seal.

[0038] Alternatively or additionally, the anchor groove can be arranged outside the gap on the bearing ring that has the anchor groove. In particular, the anchor groove and the projection are arranged axially spaced apart from each other. A portion of the gap seal can thus be arranged outside the gap and on the outside of the bearing ring that has the sealing groove. This arrangement reduces the axial installation space on the bearing ring that has the anchor groove. Preferably, this reduces the axial installation space of the entire large-diameter bearing.

[0039] Alternatively or additionally, the first sealing lip may be provided with a curved section, at least in part. In particular, the curved section is intended to extend adjacent to the mounting chamfer. Specifically, the curved section is intended to be pressurized against the mounting chamfer by the pressure in the gap. Good and error-free installation of the gap seal is ensured, in particular, by the combination of the stop element, the curved section, and the mounting chamfer. Reliable installation of the gap seal into the sealing groove is made possible, in particular, by the mounting chamfer on the projection. The mounting chamfer prevents deformation of the first sealing lip, the first sealing edge, and the second sealing edge when the gap seal is inserted into the sealing groove by increasing the clearance for the curved section of the first sealing lip. This additional clearance prevents the screwing in or...Inserting the first sealing lip with the first and second sealing edges into the sealing groove is facilitated, and at the same time, the first sealing lip and the first and second sealing edges are protected from damage. The stop element allows for setting a predetermined position of the gap seal in the anchor groove. According to the arrangement described above, the gap seal can be removed from the gap and replaced during maintenance. For this purpose, the gap seal, especially the first sealing lip, can be unscrewed from the gap along the mounting chamfer. This ensures a long-lasting blade bearing.

[0040] Alternatively or additionally, the gap seal may be provided with overpressure resistance against an internal pressure of at least 3 bar acting from the gap direction. This overpressure resistance is achieved on the seal seat side by the combination of the seal base with at least one fastening element in the anchor groove. On the sealing lip side, overpressure resistance is achieved by the locking effect of the first sealing edge with its mounting groove, which is open substantially in the direction of the gap and extends circumferentially, and the curved section of the first sealing lip that can be acted upon against the mounting chamfer. The first sealing lip is displaceable within the sealing groove by the pressure applied to the mounting groove and the curved section.

[0041] In one embodiment, the bearing ring with the anchor groove has a curved guide surface opposite the sealing groove, which increases the gap in the axial direction. This guide surface is intended to allow tool-free installation of the seal, thus simplifying assembly.

[0042] The problem is further solved by a method for mounting the gap seal on the inner bearing ring and the outer bearing ring of the blade bearing, which can be designed and further developed as described above, comprising the following steps:

[0043] - Providing a gap seal; - Providing a curved assembly tool;

[0044] - Positioning a first edge of the assembly tool in the assembly groove of the first sealing edge of the first sealing lip;

[0045] - Screwing the first sealing lip at least partially through the gap into the sealing groove;

[0046] - Proceed with the assembly tool in the circumferential direction until the first sealing lip is positioned around the entire circumference with the first and second sealing edges within the sealing groove;

[0047] - Pressing the sealing foot into the anchor groove along the entire circumference.

[0048] The assembly method allows the gap seal to be quickly and easily positioned on the inner and outer bearing rings in the area of ​​the gap. In particular, disassembly and replacement of the gap seal during maintenance work is also easily possible.

[0049] It is preferred that the sequence of process steps can be varied, unless a specific sequence is technically required. However, the aforementioned sequence of process steps is particularly preferred.

[0050] The task is still solved by a wind turbine with a blade bearing, which can be designed and further developed as described above.

[0051] Brief description of the drawings

[0052] A preferred technical solution is explained in more detail below with reference to the accompanying drawings and preferred embodiments. The term "figure" is abbreviated as "Fig." in the drawings.

[0053] The drawings show

[0054] Fig. 1 shows a sectional view of a section of a first embodiment of a blade bearing;

[0055] Fig. 2 is an enlarged sectional view of the gap seal of the blade bearing according to Fig. 1; and Fig. 3 is an enlarged sectional view of the gap seal during assembly;

[0056] Fig. 4 shows an enlarged sectional view of the bearing rings with the gap according to a second embodiment.

[0057] Detailed description of the drawings

[0058] The described embodiments are merely examples that can be modified and / or supplemented in various ways within the scope of the claims. Each feature described for a particular embodiment can be used independently or in combination with other features in any other embodiment. Each feature described for an embodiment of a particular claim category can also be used accordingly in an embodiment of a different claim category.

[0059] To simplify the wording in the present figure description and improve the readability of the descriptive text, the embodiments described below are designed with the anchor groove located in the inner bearing ring and the sealing groove in the outer bearing ring. It is understood that this does not limit the disclosure of the invention to this arrangement. The anchor groove can also be located in the outer bearing ring and the sealing groove in the inner bearing ring.

[0060] Figure 1 shows a sectional view of a section of a first embodiment of a blade bearing 10, particularly for a wind turbine, comprising an inner bearing ring 12 and an outer bearing ring 14, wherein the inner bearing ring 12 is connected to the outer bearing ring 14 directly or indirectly via at least one row of rolling elements 16. A gap 18 extending axially and circumferentially is arranged between the inner bearing ring 12 and the outer bearing ring 14. The gap 18 serves, among other things, to lubricate the row of rolling elements 16, and is sealed by a gap seal 20 arranged on the inner bearing ring 12 and the outer bearing ring 14. The gap seal 20 prevents, in particular, grease or lubricant from escaping from the gap 18 into the environment, as well as dirt and / or liquids from penetrating the gap 18.The gap seal 20 has a sealing base 22 for the force-fit and / or form-fit fastening of the gap seal 20 within a lug 24 extending in the circumferential direction of the inner bearing ring 12. From the sealing base 22, a first sealing lip 26 and a second sealing lip 28 extend towards the outer bearing ring 14 for contacting the latter. The outer bearing ring 14 has a sealing groove 30 open towards the gap 18 and extending in the circumferential direction for at least partial reception of the first sealing lip 26 and a projection 32 adjacent to the sealing groove 30 and extending in the circumferential direction, wherein the projection 32 is arranged at least partially between the first sealing lip 26 and the second sealing lip 28. A lubrication bore 62 is arranged between the anchor 24 and the row of rolling elements 16, through which a lubricant can be introduced into the gap 18.

[0061] Figure 2 shows an enlarged sectional view of the gap seal 20 of the blade bearing 10 according to Fig. 1, wherein the first sealing lip 26 has at least a first sealing edge 34 for contacting a first sealing surface 36 and a second sealing edge 38 for contacting a second sealing surface 40 within the sealing groove 30, wherein in particular the first sealing edge 34 has a mounting groove 42, open substantially in the direction of the gap 18 and extending circumferentially, for receiving a mounting tool 64 and / or for receiving lubricant. The mounting groove 42 allows the gap seal 20 with the first sealing edge 34 and the second sealing edge 38 to be positioned quickly and easily within the sealing groove 30. Additionally, the projection 32 also has a mounting chamfer 44 adjacent to the sealing groove 30 and extending circumferentially to facilitate the mounting of the first sealing lip 26 within the sealing groove 30.The second sealing lip 28 has a third sealing surface 46 extending circumferentially on the outside of the bearing outer ring 14 and at least partially along the projection 32. This third sealing surface 46 is contacted by means of a third sealing edge 48 of the second sealing lip 28. The third sealing edge 48 is designed as a multi-stage sealing edge with four circumferentially extending contact elements 50 that are configured to make contact with the third sealing surface 46. The grooves arranged between the contact elements 50 are designed as pressure chambers 60, through which the back pressure acting on the outside in front of the second sealing lip 28 can dissipate. This operating principle promotes a higher degree of tightness against the ingress of contaminants, rain, and splash water. The third sealing edge 48 prevents the ingress of dirt and / or liquids into the gap 18.The longitudinal axis of the sealing groove 30 and the longitudinal axis of the projection 32 run essentially parallel to each other in cross-section. Furthermore, the first sealing lip 26 has, at least in sections, a curved section 54 extending adjacent to the mounting chamfer 44. The curved section 54 can thus be acted upon by means of an internal pressure in the gap 18, sealing against the adjacent mounting chamfer 44. The mounting chamfer 44 can therefore, particularly at sufficiently high internal bearing pressures, have or form a fourth sealing surface 56.The sealing base 22 has at least one projecting fastening element 52 extending circumferentially for the force-fit and / or form-fit fastening of the gap seal 20 within the anchor groove 24, and at least one projecting stop element 58 extending circumferentially for the form-fit limitation of the installation depth of the sealing base 22 within the anchor groove 24. The anchor 24 is arranged outside the gap 18 on the inner bearing ring 12, with the anchor groove 24 and the projection 32 being spaced apart from each other in the axial direction 66. This arrangement allows the gap seal 20 to be inserted into the inner bearing ring 12 and the second sealing lip 28 to be arranged on the outside of the outer bearing ring 14.

[0062] Figure 3 shows an enlarged sectional view of the gap seal 20 during assembly, in which the curved assembly tool 64 engages with a first edge in the assembly groove 42 of the first sealing edge 34 of the first sealing lip 26 and at least partially rotates the first sealing lip 26 through the gap 18 into the sealing groove 30. The assembly tool 64 can then be moved circumferentially (perpendicular to the plane of Figure 3) until the first sealing lip 26 is positioned within the sealing groove 30 along its entire circumference with the first and second sealing edges 34, 38. Finally, the seal base 22 can be secured within the lug 24 along its entire circumference by force-fit and / or positive locking. This enables simple and quick assembly and disassembly of the gap seal 20 on the inner bearing ring 12 and the outer bearing ring 14.

[0063] Fig. 4 shows an enlarged sectional view of the bearing rings 12, 14 with the gap 18 according to a second embodiment. The gap seal 20 is not shown for clarity. In contrast to the first embodiment according to Fig. 3, the outer bearing ring 14, which has the anchor groove 24, has a curved guide surface 18a 240547P10WÖ - 15 - which is arranged opposite the sealing groove 30. The guide surface has a radius of curvature, so that it is curved and the outer bearing ring 14 has a concave opening towards the inner bearing ring 12. This shape of the guide surface 18a increases the gap 18 in the axial direction in the area of ​​the guide surface 18a. The curved guide surface 18a allows the seal to be installed even without an installation tool. The first sealing lip 26 is guided and positioned correctly by the guide surface 18a in the sealing groove 30.This ensures safe and simplified installation of the gap seal 20.

[0064] Reference symbol list

[0065] 10 leaf bearings

[0066] 12 inner bearing ring

[0067] 14 Outer bearing ring

[0068] 16 W rolling element series

[0069] 18 gaps

[0070] 18a Guide surface

[0071] 20 Gap seal

[0072] 22 Sealing foot

[0073] 24 Anchor groove

[0074] 26 first sealing lip

[0075] 28 second sealing lip

[0076] 30 sealing groove

[0077] 32 jump

[0078] 34 first sealing edge

[0079] 36 first sealing surface

[0080] 38 second sealing edge

[0081] 40 second sealing surface

[0082] 42 Mounting groove

[0083] 44 Assembly phase

[0084] 46 third sealing surface

[0085] 48 third sealing edge

[0086] 50 contact elements

[0087] 52 Fastening element

[0088] 54 curved section

[0089] 56 fourth sealing surface

[0090] 58 Stop element

[0091] 60 pressure chamber

[0092] 62 S chmi ermittelb bohrung

[0093] 64 assembly tools

[0094] 66 Axial direction

Claims

Claims 1. Blade bearings, especially for a wind turbine, comprising: - a bearing inner ring (12) and a bearing outer ring (14), wherein the bearing inner ring (12) is connected to the bearing outer ring (14) indirectly or directly via at least one row of rolling elements (16); - a gap (18) extending in the axial and circumferential direction between the inner bearing ring (12) and the outer bearing ring (14); - an annular gap seal (20) arranged at least partially within the gap (18); wherein the gap seal (20) has a sealing foot (22) for force-fit and / or form-fit fastening of the gap seal (20) within an anchor (24) extending in the circumferential direction of a bearing ring, wherein the gap seal (20) has a first sealing lip (26) extending from the sealing foot (22) and a second sealing lip (28) for contacting the bearing ring (14) opposite the bearing ring (12) with the anchor groove (24), wherein the bearing ring (14) opposite the bearing ring (12) with the anchor groove (24) has a sealing groove (30) open towards the gap (18) and extending in the circumferential direction for at least partially receiving the first sealing lip (26) and a projection (32) adjacent to the sealing groove (30) and extending in the circumferential direction,wherein the projection (32) is at least partially arranged between the first sealing lip (26) and the second sealing lip (28), and wherein the first sealing lip (26) has at least a first sealing edge (34) for contacting a first sealing surface (36) and a second sealing edge (38) for contacting a second sealing surface (40) within the sealing groove (30), wherein the first sealing edge (34) has an assembly groove (42) that is substantially open in the direction of the gap (18) and extends circumferentially for receiving an assembly tool (64) and / or for receiving lubricant.

2. Blade bearing according to claim 1, wherein the first sealing lip (26) is slidably mounted within the sealing groove (30), wherein in particular the first sealing lip (26) is displaceably mounted up to 1 millimeter within the sealing groove (30) per 1 meter of bearing inner ring diameter.

3. Blade bearing according to one of the preceding claims, wherein the projection (32) has a mounting chamfer (44) adjacent to the sealing groove (30) and extending in the circumferential direction for easier mounting of the first sealing lip (26) within the sealing groove (30).

4. Blade bearing according to one of the preceding claims, wherein the second sealing lip (28) contacts a third sealing surface (46) extending circumferentially on the outside of the bearing ring (14) having the sealing groove (30) by means of a third sealing edge (48), wherein in particular the third sealing edge (48) is designed as a multi-stage sealing edge and has a plurality of contact elements (50) extending circumferentially and designed to be contactable with the third sealing surface (46), wherein in particular the second sealing lip (28) prevents the ingress of dirt and / or liquids into the gap (18).

5. Blade bearing according to one of the preceding claims, wherein the third sealing surface (46) extends at least partially along the projection (32).

6. Leaf bearing according to one of the preceding claims, wherein the longitudinal axis of the sealing groove (30) and the longitudinal axis of the projection (32) are substantially parallel to each other in cross-section.

7. Leaf bearing according to one of the preceding claims, wherein the sealing foot (22) has at least one projecting fastening element (52) extending in the circumferential direction for force-fit and / or form-fit fastening of the gap seal (20) within the anchor groove (24), wherein in particular the at least one fastening element (52) is designed as a barb, in particular in the form of an anchor seal.

8. Blade bearing according to one of the preceding claims, wherein the sealing foot (22) has at least one projecting stop element (58) extending in the circumferential direction for the form-fitting limitation of the installation depth of the sealing foot (22) within the anchor (24).

9. Blade bearing according to one of the preceding claims, wherein the bearing ring (12) having the anchor groove (24) has a lubricant bore (62) extending to the gap (18) between the at least one row of rolling elements (16) and the anchor (24) for introducing lubricant.

10. Blade bearing according to one of the preceding claims, wherein the anchor groove (24) is arranged outside the gap (18) on the bearing ring (12) having the anchor groove (24), wherein in particular the anchor groove (24) and the projection (32) are arranged spaced apart from each other in the axial direction (66).

11. Blade bearing according to one of the preceding claims, wherein the first sealing lip (26) has at least a sectionally curved section (54), wherein in particular the curved section (54) extends adjacent to the mounting chamfer (44), wherein in particular the curved section (54) can be acted upon by the pressure in the gap (18) to seal against the mounting chamfer (44).

12. Blade bearing according to one of the preceding claims, wherein the gap seal (20) has an overpressure resistance to an internal pressure of at least 3 bar acting from the gap direction.

13. Blade bearing according to one of the preceding claims, wherein the bearing ring (12) with the anchor (24) has a curved guide surface (18a) opposite the sealing groove (30), which increases the gap (18) in the axial direction.

14. Method for mounting the gap seal (20) on the inner bearing ring (12) and the outer bearing ring (14) of the blade bearing according to any one of claims 1 to 13, comprising the following steps: - Provide a gap seal (20); - Providing a curved assembly tool (64); - Positioning a first edge of the mounting tool (64) in a mounting groove (42) of the first sealing edge (34) of the first sealing lip (26); - Turning the first sealing lip (26) at least partially through the gap (18) into the sealing groove (30); - Moving the assembly tool (64) circumferentially until the first sealing lip (26) is arranged around the entire circumference with the first (34) and second sealing edge (38) within the sealing groove (30); - Pressing the sealing foot (22) into the anchor groove (24) along the entire circumference.

15. Wind turbine with a blade bearing according to one of claims 1 to 13.

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