Rotor bearing for a wind turbine and wind turbine

Abstract

The invention relates to a rotor bearing for a wind power installation (100) having an inner ring (2) and an outer ring (3), which are rotatable relative to one another and define a bearing interior (4), in which at least one row of rolling bodies (5) is arranged, which can roll between the bearing rings, and having a discharge opening (6) for discharging lubricating oil flowing out of the bearing interior (4), wherein the bearing interior (4) is configured open toward the discharge opening (6) such that lubricating oil can be discharged from the bearing interior (4) via the discharge opening (6) without pressure, and to a wind power installation having such a rotor bearing (1).

Description

TECHNICAL FIELD

[0001] The application relates to a rotor bearing for a wind power installation and to a wind power installation. BACKGROUND

[0002] Rotor bearings of wind power installations serve to guide the forces and torques of a rotating rotor hub into the tower and the foundation of the wind power installation and at the same time enable torque transmission into the drive train towards the generator. Here, the rotor bearing can be configured as a torque bearing or as a plurality of distributed bearings, for example as a desirable conical roller bearing or as a fixed-floating bearing. As a rotor bearing, mostly rolling bearings with at least one inner ring and one outer ring are used, which enable the rotation of the rotor relative to the nacelle by force-fittingly connecting one of the components with the outer ring and the other with the inner ring. The rolling bodies of grease, oil or other lubricants between the inner ring and the outer ring enable the rotational movement.

[0003] Due to the high forces and torques that need to be transmitted by the rotor hub, it is advantageous in the above-mentioned bearing arrangements, determined by the structure, that the outer ring is connected with the rotating rotor hub and the fixed inner ring is connected with the nacelle. Such bearing arrangements are usually implemented as a rotor bearing lubricated by grease, since a bearing lubricated by grease is less prone to leaks and requires less maintenance. For oil lubrication, satisfactory sealing has not been possible to date in rotor bearings that are operated externally. The advantages of oil lubrication are on the one hand that the oil can be filtered in a circulating lubrication, thus reducing the rolling of particles in the lubricant, and on the other hand the possibility of active temperature control of the oil, thus enabling a better adjustment of the temperature of the bearing and, if necessary, the omission of other additional cooling / heating systems.

[0004] A conical roller bearing for supporting a rotor of a wind power installation is known from DE 10 2017 107 553 A1, which has an inner ring, an outer ring and two rows of conical rollers arranged between the inner ring and the outer ring in an O-shaped arrangement. The gap between the inner ring and the outer ring is sealed at least on one side of the conical roller bearing by a sealing device, which comprises a primary seal, which is connected in a torsion-proof manner on the inner ring, and a sealing sleeve, which is connected in a torsion-proof manner on the outer ring, wherein the sealing sleeve forms a sealing rolling surface for the primary seal. Furthermore, the clamping ring, which holds the primary seal, also has a dust seal, which protects the primary seal from external contamination. The disadvantage of this sealing device is that, in the oil lubrication of the bearing and especially in the case of loading with a stationary oil column, it is not possible to reliably prevent oil from flowing out through the two seals.

[0005] In order to improve the sealing, it is proposed in WO 2012 / 136632 A1 for an oil-lubricated rolling bearing for supporting a rotor of a wind power installation, which has a shaft seal separating a bearing interior accommodating rolling elements from the outside of the bearing and a clamping device for axially fixing the shaft seal, which has a discharge opening for oil. Thereby, the lubricating oil that has passed through the shaft seal can be discharged before it flows outwards through a likewise provided dust seal. Disadvantageously, however, the filling level of the lubricating oil in the bearing has to be adjusted expensively in the bearing in order to avoid, inter alia, a poor running behavior and an increased oil leakage due to an over-supply of lubricating oil. SUMMARY

[0006] It is therefore an object of the present application to provide a rotor bearing for a wind power installation and a wind power installation having a rotor bearing, in which the sealing of the oil-lubricated bearing interior is improved and at the same time a permanent supply of a defined amount of lubricating oil in the bearing interior is simplified.

[0007] This object is achieved by the rotor bearing for a wind power installation and the wind power installation according to the present application.

[0008] Thereby, a rotor bearing for a wind power installation is achieved, which has an inner ring and an outer ring, which are rotatable relative to one another and which define a bearing interior, in which at least one row of rolling elements is arranged, which can roll between the bearing rings, and which has a discharge opening for discharging lubricating oil flowing out of the bearing interior. According to the present application, it is provided that the bearing interior is configured open towards the discharge opening, so that lubricating oil can be discharged from the bearing interior via the discharge opening without pressure. The open configuration of the bearing interior towards the discharge opening ensures that an over-supply of lubricating oil of the rotor bearing is virtually excluded even in the event of a malfunction of a monitoring device. The excess lubricating oil is discharged from the bearing interior without pressure through the overflow and the discharge opening. At the same time, a ventilation of the rotor bearing is ensured by the open construction.

[0009] The bearing interior is preferably fluidically connected to the discharge opening by at least one overflow, which is connected to the outer ring in a torsion-proof manner, the overflow determining a filling level of at least one oil pool configured in the bearing interior in the installed position of the rotor bearing. In the installed position of the rotor bearing, the geodetic height of the overflow determines the maximum filling level of the at least one oil pool configured in the bearing interior. Thereby, a reliable operation of the rotor bearing and a high sealing are achieved independently of the amount of lubricating oil delivered and in all operating states, for example unbalanced states, without the need for a special measuring or regulating device for the oil system.

[0010] The use of the overflow towards the discharge opening has the additional advantage that an oil pool is formed, in which lubricating oil does not accumulate on the seal. In the event of a failure of the lubricant supply, the oil pool advantageously endows the oil-lubricated rotor bearing with an emergency running characteristic. The seal in the rotor bearing according to the application is therefore loaded only by the splashing oil and not by a stationary oil column, thereby improving the sealing of the bearing.

[0011] An oil preparation unit and an oil tank are preferably connected to the discharge opening, from which the lubricating oil can be fed back into the bearing interior space by means of a pump. The oil preparation unit preferably comprises a filter and / or a temperature control device for actively temperature control of the bearing interior space. In this way, the lubricating oil can be filtered and the rolling of particles is avoided. Furthermore, the temperature of the bearing can be better regulated, for example by active oil cooling, and other cooling systems, for example based on water or air, can be dispensed with if necessary. Oil heating devices for starting up the wind power installation at low ambient temperatures can also be considered. Furthermore, condition monitoring is achieved, for example by monitoring the temperature and particles, also remotely.

[0012] In a preferred embodiment, the rotor bearing is configured as a double-row tapered roller bearing or as an axial-radial-roller bearing. Here, one of the bearing rings is configured as a so-called nose ring, which is partially surrounded by a second bearing ring of multipart configuration, between which a plurality of rows of rolling elements are inserted. These bearing configurations allow a largely absorption of radial and axial forces as well as tilting moments, as they occur on the rotor bearing of a wind power installation.

[0013] Preferably, the outer ring of the rotor bearing can be configured as a nose ring, on which at least two raceways for rows of rolling elements that can roll between the bearing rings are configured, and on which one oil collecting ring is connected torsionally on each side. The oil collecting rings can extend radially inwards beyond the radial outer edge of the raceways on the edge side to configure an oil pool on each side. The oil collecting rings can be formed integrally with the outer ring or can be fixed to the outer ring as one or more additional rings. The oil collecting rings preferably widen the outer ring and provide a trough-like receptacle for lubricating oil. The oil collecting rings for this purpose preferably have a substantially axially extending portion and a substantially radially extending edge-side portion. By the radially inwards extending portion of the oil collecting rings on the edge side, an accumulation of lubricating oil into the region of the raceways is achieved. The rolling elements at least partially sink into the oil pool in each cycle and distribute lubricating oil into the bearing interior space in further cycles. Thus, according to the application, the oil lubrication and the backflow of oil take place in such a way that even in the event of a failure of the energy supply or the pump, no leakage out of the bearing occurs, the backflow of excess oil, for example into an oil tank, continues and a continued operation of the bearing is possible at least for a limited period of time.

[0014] It is preferred that at least one of the oil collecting rings forms at least one overflow. The lubricating oil then collects on the inner side of the oil collecting ring in an oil pool and flows on the outer side of the oil collecting ring towards the discharge outlet.

[0015] It is particularly preferred that the two oil pools are connected to one another by at least one passage which traverses the outer ring. Such a passage allows the lubricating oil to exchange between the two oil pools. In the case of an installation of the bearing with a stationary outer ring, one passage which traverses the outer ring is already sufficient to achieve a compensation of the filling level of the two oil pools in operation.

[0016] In the case of a rotor bearing which is designed as an outer rotor, it is preferred that a plurality of passages which traverse the outer ring are arranged distributed over the circumference of the outer ring for connecting the two oil pools. In the course of the outer ring, the passages successively immerse into the region of the oil pools. Each passage connects the two oil pools to one another for the duration of the immersion in order to compensate their filling level. After leaving the oil pool, the passage is again emptied, preferably in the direction of its lower lying end.

[0017] The rotor bearing can be installed inclined with respect to the horizontal in order to move the rotor blades further away from the tower of the wind power installation when they are turning and to rule out a contact between the blades and the tower even at high loads. This inclination of the rotor bearing axis can advantageously be used for the oil feed to the generator side and the discharge there.

[0018] In the case of a rotor bearing which is designed as an outer rotor, the oil feed is preferably carried out by means of holes or nozzles introduced in the stationary inner ring.

[0019] The connection of the oil pools on both sides of the rotor bearing achieves a construction form of the rotor bearing which only has a lubricating oil connection on the generator side and a discharge connection on both sides. Thereby, a large part of the pipe routing and pumps from the hub side / rotor side can be dispensed with. The risk of possible leaks, pump failures and maintenance is reduced. Particularly advantageously, a solution is provided which only has a lubricating oil connection on the generator side and a discharge connection, whereby the pipe routing and pumps on the hub side can be completely eliminated.

[0020] In a preferred embodiment, the rotor bearing has an overflow only on one side, and the bearing interior is closed on the other side of the rotor bearing by means of at least one seal. By means of the connection of the two oil pools by means of at least one passage, a compensation of their filling level can be achieved. Thus, the one-sided overflow is sufficient to determine a common filling level of the two oil pools. Thus, it is also possible to avoid a stationary oil column on the seal of the bearing interior on the side where no overflow is provided.

[0021] Preferably, the seal is arranged above the filling level of the oil sump connected to one another by the overflow in the installed position of the rotor bearing. The operation of the seal is generally sufficiently lubricated by the splashing oil. Such an unloaded seal has a high sealing property, so that a leakage is only expected in a very small range. The seal is preferably installed on the rotor side of the bearing, since the interface for oil discharge is preferably installed on the generator side. A further advantage of this arrangement is provided by the preferred direction of the oil flow to the generator, which is determined by the inclination of the drive train.

[0022] It is also conceivable, however, that one of the overflows is connected with the discharge outlet by at least one passage through the outer ring. In this way, in particular, a rotor bearing can be realized in which an overflow is provided on both sides, but the discharge outlet is provided only on one side. The lubricating oil that flows out through the overflow on the rotor side can thus be guided back to the discharge outlet on the nacelle side by means of the passage in the outer ring.

[0023] In a preferred embodiment, a ring mount is fixed on the inner ring, which ring mount radially surrounds the oil collecting ring forming the overflow and contains the discharge outlet, wherein the ring mount is sealed with respect to the oil collecting ring. This embodiment is preferred for rotor bearings designed as outer rotors. In this way, the discharge outlet is fixed positionally on the stationary inner ring by means of the ring mount.

[0024] Preferably, the inner ring is sealed with respect to the outer ring on both sides of the bearing, directly or indirectly, by a sealing system comprising at least two seals, between which a drainage chamber for collecting the leakage oil is respectively formed. By forming a multi-stage sealing system on both sides of the bearing, the amount of lubricating oil that flows out of the bearing in operation is further reduced.

[0025] Furthermore, it can be provided that the drainage chambers are connected to one another on both sides of the rotor bearing by means of at least one passage through the outer ring. In this way, the leakage oil that flows out on both sides of the bearing can be discharged on one side. The continuous emptying of the two drainage chambers in operation, which is thereby achieved, reduces the load on the respective second seal. The sealing property of the bearing is thus improved and the maintenance intervals are extended.

[0026] Alternatively or additionally, the drainage chambers can be equipped with an oil collecting container in the lower circumferential region, which collects the falling leakage oil. Due to the small residual leakage, a small collecting container is already suitable for collecting and temporarily storing the leakage over a long period of time. The oil collecting container can be emptied either manually in the normal maintenance work or, for example, by means of a level-regulated pump and the bearing is re-lubricated with the corresponding amount of oil.

[0027] Furthermore, the object is achieved by a wind power installation having a tower, a nacelle fixed at the tower and a rotor rotatably supported at the nacelle, wherein the rotor is supported at the nacelle via a rotor bearing as described before. Here, the rotor is preferably torsionally connected with the outer ring of the rotor bearing and the nacelle is torsionally connected with the inner ring of the rotor bearing. According to a preferred embodiment, the rotational axis of the rotor bearing forms an angle of 2° to 10° with the horizontal, which promotes the flow of lubricating oil through the passages traversing the outer ring.

[0028] Further advantageous embodiments can be gathered from the following description. BRIEF DESCRIPTION OF DRAWINGS

[0029] The application is explained in detail below with the help of embodiments shown in the drawings.

[0030] Figure 1 A wind power installation according to the application is schematically shown with a rotor supported by a rotor bearing according to the application,

[0031] Figure 2 A first embodiment of a rotor bearing according to the application is schematically shown in a sectional view with an oil overflow and a plurality of passages in the outer ring connecting oil sumps on both sides of the rotor bearing,

[0032] Figure 3 A detail view of a rotor bearing according to the application is schematically shown, Figure 2

[0033] Figure 4 A detail view of a second embodiment of a rotor bearing according to the application is schematically shown, wherein the oil sumps on both sides of the sealing system and the drainage chambers on both sides are connected to each other by means of passages traversing the outer ring. DETAILED DESCRIPTION

[0034] In the different figures, identical parts are always provided with the same reference signs and are therefore generally also only named or mentioned once each.

[0035] A wind power installation 100 according to the application is shown in Figure 1 The wind power installation 100 comprises a tower 110, a nacelle 120 fixed at the tower 110 and a rotor 130 rotatably supported at the nacelle 120. The rotor 130 is supported at the nacelle 120 via a rotor bearing 1 according to the application (cf. Figures 2 to 4 ). Here, the rotor 130 is preferably torsionally connected with the outer ring 3 and the nacelle 120 is torsionally connected with the inner ring 2. The rotor 130 comprises a rotor hub 150 and a plurality of rotor blades 140 fixed at the rotor hub 150. The wind force and the gravitational force acting on the rotor blades 140 can thus be introduced into the outer ring 3 of the rotor bearing 1 by means of the rotor hub 150 and transmitted to the inner ring 2 and the nacelle 120 by means of the rolling bodies 5.​

[0036] exist Figure 2 The diagram illustrates a first embodiment of a rotor bearing 1 according to the invention for use in wind power equipment. The rotor bearing 1 includes an inner ring 2 and an outer ring 3, which are rotatable relative to each other and define an internal bearing space 4. Within the internal bearing space 4, two rows of rolling elements 5, which are exemplarily arranged between the rings 2 and 3, are arranged. Furthermore, the rotor bearing includes a drain port 6 for discharging lubricating oil flowing from the internal bearing space 4. The internal bearing space 4 is configured to open toward the drain port 6, allowing lubricating oil to be discharged from the internal bearing space 4 without pressure via the drain port 6. The internal bearing space 4 and the drain port 6 are fluidly connected via an overflow portion 7, which is torsionally connected to the outer ring 3. In the illustrated mounting position of the rotor bearing 1, the overflow portion 7 defines the filling height H of the oil sump 8 formed within the internal bearing space 4.

[0037] In the illustrated embodiment, two rows of tapered rollers are configured as rolling element rows, arranged in an O-shape between the inner ring 2 and the outer ring 3. The inner ring 2 is assembled from two mutually sealing sub-rings 2.1 and 2.2. Contemplated alternative bearing designs include, for example, tapered roller bearings with an X-shaped arrangement of rollers, symmetrical or asymmetrical tapered roller bearings, or axial-radial roller bearings, such as three-row roller slewing couplings.

[0038] Rotor bearing 1 in Figure 2 The image shows the installation position. In this position, the rotation axis A forms an angle between 2° and 10° with the horizontal plane. This facilitates the flow of lubricating oil through the channel traversing the outer ring. The lower side of the rotor bearing 1 (in...) is positioned relative to the wind power unit 100. Figure 2 (shown in the middle on the left) is preferably positioned on the side of the pod 120, and the higher side (in) Figure 2 (shown on the right) is disposed on the side of rotor 130.

[0039] In the illustrated embodiment, the outer ring 3 is configured as a convex nose ring 9, on which two raceways 10 are formed for a row of rolling elements that can roll between the inner ring 2 and the outer ring 3. An oil collecting ring 11 is connected to each side of the outer ring 3 to resist relative rotation. This oil collecting ring extends radially inward beyond the radially outer edge 12 of the raceway 10 on its edge side to form an oil pool 8. Here, in... Figure 2 The oil collecting ring 11 shown on the left side forms the overflow section 7.

[0040] As in Figure 3 According to Figure 2 As can be seen more clearly in the detailed drawings of the embodiment, the two oil tanks 8 are connected by multiple channels 13 that traverse the outer ring. Figure 2As can be seen in the middle, they are arranged distributed over the circumference of the outer ring 3. After half a revolution of the outer ring 3, the channels 13 shown above in the middle are immersed in the oil pools 8 and the channels 13 shown below in the middle are empty. By providing oil collecting grooves 20 in the oil collecting rings 11, the channels 13 can be introduced with sufficient spacing from the hardened raceway 10. The channels 13 are preferably configured as through-holes. Figure 2 Figure 2 The channels 13 shown below in the middle are empty. By providing oil collecting grooves 20 in the oil collecting rings 11, the channels 13 can be introduced with sufficient spacing from the hardened raceway 10. The channels 13 are preferably configured as through-holes.

[0041] Preferably, the number and distribution of the channels 13 over the circumference are selected such that, independently of the angular position of the inner ring 2, the outer ring 3 relative to one another, at least one channel provides a connection of the two oil pools 8. In a rotor bearing designed as an inner rotor, accordingly, the channels 13 are already sufficient for the oil pools 8 to be permanently connected to one another in operation in order to compensate for the filling height.

[0042] The channels 13 preferably extend substantially parallel to the axis of rotation A of the rotor bearing 1. Alternatively, the channels can also have a directional component in the circumferential direction of the rotor bearing. By the directional component of the channels selected according to the preferred direction of rotation of the rotor bearing, the pumping action can be enhanced, since the channels preferably empty in the direction of their lower end after floating out of the oil pool.

[0043] As can be seen in particular in the Figure 3 middle, in the first embodiment, the rotor bearing 1 has a spillway 7 only on one side, and the bearing interior 4 is closed on the other side of the rotor bearing 1 by means of a seal 14. To this end, a height difference can be provided between the two oil collecting rings 11, which results from the installation position of the rotor bearing and / or by the structural design of the two oil collecting rings 11. The seal 14 serves to ensure a pressureless oil discharge on one side in all, for example also unbalanced, transient operating states or also in operating states that occur only for a short time. This leads to an asymmetrical hub-side and generator-side sealing system design, by means of which it is ensured that, in addition to a small amount of leakage / emission of the seal 14, the amount of oil delivered can be reliably discharged on the generator side. The seal 14 is arranged above the filling level H of the oil pools 8 connected to one another, which is determined by the spillway 7, in the installation position of the rotor bearing 1 shown.

[0044] Behind the seal 14, a drain chamber 17 is arranged, which is closed outwardly by at least one further seal, with a further discharge opening 19. On the discharge opening 19, for example, a collection container can be connected, which collects the leaked oil flowing out. In an outer rotor, the drain chamber 17 is preferably formed by a ring mount, which is fastened on the inner ring 2, surrounds the oil collecting ring 11 in the radial direction R and is sealed relative to the oil collecting ring.

[0045] ​The rotor bearing 1 also has, on the side of the overflow 7, a ring mount 15 fixed to the inner ring 2, which surrounds the oil collecting ring 11 forming the overflow 7 in the radial direction R and which contains the discharge opening 6. The ring mount 15 is also sealed with respect to the oil collecting ring 11 in the case of a discharge chamber 17 being formed.

[0046] The use of a ring mount as a seal support ring is advantageous in terms of the installation and replacement of the seal on the device.

[0047] As shown in Figure 2 and Figure 3 , the inner ring 2 is preferably sealed with respect to the outer ring 3 on both sides of the bearing 1 directly or indirectly, respectively, by a sealing system 16, which comprises at least two seals between which a discharge chamber 17 for collecting the leaked oil is formed.

[0048] Figure 4 A second embodiment of the rotor bearing 1 according to the application is shown. Unlike the first embodiment, the discharge chambers 17 of the sealing system 16 are connected to one another via at least one second passage 18 that traverses the outer ring 3 on both sides of the rotor bearing 1. The second passage 18 can be provided in addition to and separately from the passage 13 that connects the oil sump 8. The passage 13 is shown in Figure 4 in dashed lines, since it is provided in the other cross section of the rotor bearing 1. Like the passage 13 that connects the oil sump 8, it is also advantageous for the second passages 18 to be arranged distributed over the circumference of the outer ring in the outer rotor.

[0049] The leaked oil that is discharged from the discharge chambers 17 can be cleaned and reintroduced into the lubricating oil circulation system if necessary. Alternatively, the leaked oil can be collected and disposed of centrally.

[0050] Furthermore, the embodiments described with respect to the first embodiment apply correspondingly.

[0051] According to an embodiment not shown, one of the overflows can also be connected to the discharge opening by at least one passage that traverses the outer ring.

[0052] Furthermore, the embodiments described with respect to the first two embodiments apply correspondingly.

[0053] Legend of the Figures

[0054] 1 rotor bearing

[0055] 2 inner ring

[0056] 2.1, 2.2 partial ring

[0057] 3 outer ring

[0058] 4 bearing interior space

[0059] 5 rolling element

[0060] 6outlet

[0061] 7overflow

[0062] 8oil sump

[0063] 9nose ring

[0064] 10raceway

[0065] 11oil ring

[0066] 12radially outer edge of raceway

[0067] 13passage

[0068] 14seal

[0069] 15ring mount

[0070] 16sealing system

[0071] 17drain chamber

[0072] 18second passage

[0073] 19outlet of drain chamber

[0074] 20oil collection groove

[0075] 100wind turbine

[0076] 110tower

[0077] 120nacelle

[0078] 130rotor

[0079] 140rotor blade

[0080] 150rotor hub

[0081] Rradial direction

[0082] Hfilling height

[0083] Abearing axis

Claims

1. A rotor bearing for a wind power installation (100) having an inner ring (2) and an outer ring (3), which can be rotated relative to one another and define a bearing interior space (4) in which at least one row of rolling bodies (5) that can roll between the bearing rings is arranged, and which has a discharge opening (6) for discharging lubricating oil that flows out of the bearing interior space (4), characterized in that The bearing interior space (4) is open towards the discharge opening (6) such that lubricating oil can be discharged from the bearing interior space (4) via the discharge opening (6) without pressure; the bearing interior space (4) is fluidically connected to the discharge opening (6) by at least one overflow (7) which is connected in a rotationally fixed manner to the outer ring (3), the overflow determining a filling level (H) of at least one oil pool (8) in the bearing interior space (4) in the installed position of the rotor bearing (1); The outer ring (3) is configured as a nose ring (9), and at least one of the oil collecting rings (11) is connected in a rotationally fixed manner on both sides of the nose ring, at least one of the oil collecting rings (11) forming at least one overflow (7); At least two raceways (10) for a rolling body row which can roll between the inner ring (2) and the outer ring (3) are configured on the nose ring, the oil collecting rings extending in the radial direction (R) inwards beyond the radially outer edges (12) of the raceways (10) to form each one oil pool (8); An annular mounting (15) is fixed to the inner ring (2), the annular mounting enclosing the oil collecting rings (11) which form the overflow (7) in the radial direction (R) and containing the discharge opening (6), and the annular mounting (15) is sealed relative to the oil collecting rings (11).

2. The rotor bearing of claim 1, wherein The two oil pools (8) are connected to one another by at least one passage (13) which traverses the outer ring (3).

3. The rotor bearing of claim 2, wherein The rotor bearing (1) is designed as an outer rotor, and a plurality of passages (13) which traverse the outer ring (3) are arranged distributed over the circumference of the outer ring (3) in order to connect the two oil pools (8).

4. The rotor bearing of any of claims 1-3, wherein, The rotor bearing (1) has an overflow (7) only on one side, and the bearing interior space (4) on the other side of the rotor bearing (1) is closed by means of at least one seal (14).

5. The rotor bearing of claim 4, wherein The seal (14) is arranged above the filling level (H) of the oil pools (8) which are connected to one another by means of the overflow (7) in the installed position of the rotor bearing (1).

6. The rotor bearing of any of claims 1-3, wherein, One of the overflows is connected to the discharge opening by at least one passage which traverses the outer ring.

7. The rotor bearing of any one of claims 1 to 3, wherein, The inner ring (2) is sealed relative to the outer ring (3) on both sides of the bearing (1) directly or indirectly by means of a respective sealing system (16) which comprises at least two seals between which a drainage chamber (17) for collecting leaking oil is configured.

8. The rotor bearing of claim 7, wherein The drainage chambers (17) are connected to one another on both sides of the rotor bearing (1) via at least one second passage (18) which traverses the outer ring (3).

9. A wind energy device having a tower (110), a nacelle (120) fixed on the tower (110), and a rotor (130) rotatably supported on the nacelle (120), characterized in that The rotor (130) is supported on the pod (120) via a rotor bearing (1) according to any one of claims 1 to 8.

10. Wind energy plant according to claim 9, wherein the rotor (130) is connected in a rotationally fixed manner to the outer ring (3), and the pod (120) is connected in a rotationally fixed manner to the inner ring (2).

11. The wind power plant according to claim 9 or 10, characterized in that The rotational axis (A) of the rotor bearing (1) encloses an angle with the horizontal which is in the range from 2° to 10°.

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