Rotor bearing for wind power generation equipment and wind power generation equipment

Abstract

The invention relates to a rotor bearing (1) for a wind power plant, comprising an inner ring (2) and an outer ring (3) rotatable relative to the inner ring (2), defining a bearing interior space (4), in which at least one row (5) of rolling bodies that can roll between the bearing rings is arranged, and the rotor bearing comprises sealing devices (6) for sealing the bearing interior space (4) on one side, wherein at least one of the sealing devices (6) comprises a first sealing element (7) non-rotatably connected to the inner ring (2) and a second sealing element (8) non-rotatably connected to the outer ring (2). 3), on which a first sealing running surface (9) for a first sealing member (7) is formed, wherein a ring attachment (10) is fixed on an inner ring (2), the ring attachment surrounds the sealing ring (8) in the radial direction (R), and a second sealing member (11) is provided which acts between the sealing ring (8) and the ring attachment (10) and defines an annular space (14) formed between a radial outer surface (12) of the sealing ring (8) and a radial inner surface (13) of the ring attachment. The present invention also relates to a wind power generation device having such a rotor bearing (1).

Description

Technical Field

[0001] The invention relates to a rotor bearing for a wind power generation device and a wind power generation device. Background Art

[0002] The rotor bearings of a wind turbine are used to transfer the forces and moments of the rotating rotor hub into the tower and the foundation of the wind turbine and can simultaneously transmit the torque to the drive train leading to the generator. The rotor bearings can be designed as torque bearings or as multiple distributed bearings, such as tapered roller bearings or fixed loose bearings.

[0003] Due to the large forces and moments that the rotor hub has to transmit, it is advantageous for construction reasons if the outer ring is connected to the rotating rotor hub and the stationary inner ring is connected to the machine chamber, i.e. the nacelle, in the above-mentioned bearings. This type of bearing is usually designed as a grease-lubricated rotor bearing, because the grease provides an auxiliary sealing effect. So far, it has not been possible to achieve satisfactory oil-lubricated sealing, especially in external rotating rotor bearings. The advantages of oil lubrication are that on the one hand, the oil can be filtered in the circulating lubrication, thereby reducing the situation of running over particles in the lubricant, and on the other hand, the oil can be actively temperature-controlled to better regulate the temperature of the bearing and, if necessary, other additional cooling / heating systems can be omitted.

[0004] From DE 10 2017 107 553 A1, a tapered roller bearing for mounting a rotor of a wind power plant is known, which tapered roller bearing has an inner ring, an outer ring and two rows of tapered rollers, which are arranged in an O-shaped arrangement between the inner ring and the outer ring. The gap between the inner ring and the outer ring is sealed at least on one side of the tapered roller bearing by a sealing device, which comprises a main seal connected to the inner ring in a non-rotatable manner and a sealing seat ring connected to the outer ring in a non-rotatable manner, wherein the sealing seat ring forms a sealing running surface of the main seal.

[0005] WO 2012 / 136632 A1 discloses an oil-lubricated roller bearing for supporting a rotor of a wind turbine, which has a shaft seal which separates the bearing interior accommodating the rolling elements from the bearing exterior, and a clamping device for axially fixing the shaft seal, the clamping device having an oil drain opening.

[0006] A disadvantage of the two above-mentioned roller bearings is that, when oil is used as lubricant, the leaking oil that occurs can only be caught and discharged when the outer ring is stationary. When used as an outer rotor, the known bearings cannot reliably prevent the leaking oil from flowing into the machine chamber. Summary of the invention

[0007] It is therefore an object of the present invention to provide a rotor bearing for a wind turbine and a wind turbine having a rotor bearing which, when used as an outer rotor, has improved sealing properties for the oil-lubricated bearing interior.

[0008] This object is achieved by a rotor bearing for a wind power plant and a wind power plant according to the invention.

[0009] Thus, a rotor bearing for a wind power plant is realized, which has an inner ring and an outer ring that can rotate relative to the inner ring, wherein the inner ring and the outer ring define a bearing interior space, in which at least one row of rolling bodies that can roll between the bearing rings is arranged. The rotor bearing also has a sealing device for sealing the bearing interior space on one side, wherein at least one of the sealing devices has a first seal that is non-rotatably connected to the inner ring and a sealing seat ring that is non-rotatably connected to the outer ring. A first sealing running surface for the first seal is formed on the sealing seat ring. According to the present invention, a ring attachment is fixed to the inner ring, the ring attachment surrounds the sealing seat ring in the radial direction, and a second seal that acts between the sealing seat ring and the ring attachment is provided, which defines an annular space formed between the radial outer surface of the sealing seat ring and the radial inner surface of the ring attachment.

[0010] The rotor bearing according to the invention is therefore equipped with an at least two-stage sealing system formed by a first and a second seal. The annular space enclosed between the first seal and the second seal forms an oil collecting space for leakage oil that has escaped through the first seal. The radial inner surface of the ring attachment fixedly mounted on the inner ring and surrounding the sealing race forms a fixed radial outer wall of the annular space. In the case of a substantially horizontal arrangement of the bearing axis, the leakage oil is captured by the ring attachment over the entire periphery and collected in the lower peripheral area. The second seal reliably prevents the collected leakage oil from escaping.

[0011] The sealing device according to the invention completely captures the escaping oil, which is subjected to centrifugal forces and, when stationary, to gravity forces, and enables it to return to the bearing or otherwise to the oil circuit via a non-rotating ring attachment.

[0012] The first sealing running surface preferably has a smaller diameter than the maximum diameter of the roller contact surface for the rolling element row on the outer ring to form an oil groove. For this purpose, the first sealing running surface is preferably formed on a radially inwardly protruding section of the sealing seat ring. Due to the radial arrangement of the first sealing running surface in the roller contact surface area, lubricating oil will accumulate in the inner space of the bearing up to the roller contact surface before the first seal is loaded with an oil column. Therefore, an oil groove is formed in the peripheral area of ​​the lower part of the inner space of the bearing, which provides the bearing with important emergency operating performance. Even if the circulating lubrication fails, the oil groove can ensure that the bearing is fully lubricated during the rotation process of emergency operation. This improves the operating and failure safety, which is a great advantage especially for wind power generation equipment that is difficult to maintain.

[0013] In a preferred embodiment, the drain opening for connecting the oil recovery element is arranged in the ring attachment, which has a flow cross section which is arranged at least partially radially further outward than the sealing gap of the second seal. In this embodiment, the leakage oil collected in the annular space can be continuously discharged, processed and returned to the bearing interior by circulating lubrication. Advantageously, any leakage that occurs does not cause any maintenance work, since the oil level in the bearing interior can be kept largely constant by the oil recovery. It can even be provided that the first seal is adjusted so that a minimum leakage flow is maintained, for example in order to lubricate the sealing gap of the first seal or in order to increase the oil circulation rate of the circulating lubrication.

[0014] Alternatively or additionally, an oil collecting container can be formed on the attachment ring in the lower peripheral region, which collects the accumulated leaking oil. The oil collecting container can be emptied during regular maintenance work and the bearing can be relubricated with a corresponding amount of oil.

[0015] Preferably, an oil dripping edge is formed on the radial outer surface of the seal seat ring in the annular space in front of the second seal for separating the entrained oil. The oil dripping edge prevents the leaked oil from flowing or creeping along the radial outer surface of the seal seat ring in the direction of the sealing gap of the second seal. Under the influence of gravity and / or centrifugal force, the oil dripping edge causes droplet formation and subsequent separation of the entrained oil droplets formed. The second seal is thus protected from influence and the sealing performance of the sealing device is further increased. The oil dripping edge is preferably formed in a form that narrows at an acute angle in the radial direction.

[0016] In a preferred embodiment, the first seal is clamped axially against the inner ring by the ring attachment. In this way, the first seal can be replaced in a simple manner by removing the ring attachment. For precise radial positioning, the first seal is preferably inserted into a radial shoulder or groove of the inner ring.

[0017] The first seal is preferably a radially acting seal having a sealing lip which bears against the radial inner surface of the sealing seat ring.

[0018] In particular, it can be provided that the first and second seals are held in their position by the ring attachment and that a second sealing running surface for the second seal is formed on the sealing ring. With such a sealing arrangement, both seals of the sealing system can be easily replaced by removing the ring attachment from the inner ring. It is also advantageous if the sealing system does not rotate, so that the sealing lip is not subject to any circumferential deformation. This arrangement is also particularly preferred if the sealing ring is designed integrally with the outer ring or is connected to the outer ring so that it is only separated from the outer ring when the bearing is disassembled.

[0019] The first seal preferably bears against the first sealing running surface with a first lip preload which is greater than the second lip preload of the second seal. In this case, the first seal forms a primary seal which is used to allow as little leakage as possible. The second seal has the function of a secondary seal which only has to seal against splashing oil and provide protection against the ingress of external dust. The lip preload can be applied by the elasticity of the corresponding sealing material. In order to increase the lip preload, a preload spring element can be arranged in the first and / or second seal.

[0020] For centering, axially acting engagement means can be provided on the ring attachment and / or the sealing seat ring, which engage with complementary engagement means on the inner ring and / or respectively on the outer ring. Since the first and second seals act between the ring attachment and the sealing seat ring, and different sealing gap widths can only be reliably sealed with a limited tolerance of a few millimeters, it is necessary to accurately position the ring attachment and the sealing seat ring relative to each other. In particular, in radially acting seals, accurate centering of the ring attachment and the sealing seat ring relative to the bearing axis is very important in order to obtain a sufficient sealing effect. For this purpose, it is advantageous to provide mutually complementary engagement means on the ring attachment and the inner ring or on the sealing seat ring and the outer ring, which facilitate centering of the ring attachment and the sealing seat ring during assembly. The engagement means can, for example, consist of a circumferential or segmented groove or shoulder, into which a corresponding complementary axial projection of the other component engages.

[0021] The sealing ring can be fixed to the outer ring by means of a threaded connection and can be sealed relative to the outer ring by means of an O-ring which is arranged radially on the inside of the threaded connection. In this way, a reliable sealing of the bearing interior is achieved in the region of the joint surface between the sealing ring and the outer ring. Due to the radially inner sealing, the threaded connection is also protected against oil penetrating into the joint gap.

[0022] In order to further improve the seal, at least one further sealing element can be provided between the first seal and the second seal to relieve the pressure of the second seal, which seal separates the annular space. In the simplest case, the further sealing element can be designed, for example, as a sealing gland which can be made of rubber or felt material, for example. Alternatively or additionally, further lip seals can also be provided.

[0023] Furthermore, it is preferred that an additional drain opening is provided in the annular attachment between the additional sealing element and the second seal. In this case, the annular space is divided by the additional sealing element into two chambers, each of which is provided with a drain opening. It can be provided that one or both drain openings are connected to a non-return valve in order to prevent oil from flowing back into the respective chamber.

[0024] In a preferred embodiment, the second seal and the further sealing element are formed as axially acting lip seals with lip preloads directed in the same or opposite directions in the axial direction. By applying an overpressure or underpressure to the chamber formed between the further sealing element and the second seal, the sealing behavior of the chamber can be influenced. Thus, in the case of lip seals acting axially opposite to one another, the sealing effect of both seals can be increased by applying an overpressure to the chamber. In the case of axially co-directional lip seals, the overpressure in the chamber formed between them can be used, for example, to decompress the further sealing element and push the leakage oil flow back into the sealing gap of the further sealing element.

[0025] In a preferred embodiment, the outer ring can have fastening bores for fastening the rotor bearing to the rotor of the wind turbine by means of fastening screws, and the sealing ring can extend in the radial direction into the region of the fastening bores for clamping the sealing ring when assembling the rotor. Advantageously, no additional bores that would weaken the outer ring are required for fastening the sealing ring to the outer ring, since the forces acting on the sealing ring during operation are diverted via the clamping connection. To simplify assembly, it is advantageous to provide a small number of holes in the outer ring so that the sealing ring can be positioned relative to the outer ring already at the factory and can be fixed in its position.

[0026] The sealing ring is preferably made of steel and hardened at least in the area of ​​the first sealing running surface. This reduces the wear of the sealing ring. The sealing ring can be formed in one piece with the outer ring in particular. However, in order to reduce the material expenditure used in production, a two-piece embodiment is preferably used. A low-cost embodiment of the sealing ring made of plastic material is also conceivable.

[0027] In a preferred embodiment, the ring attachment is made of a plastic material, which is sufficient because the ring attachment is only subject to relatively small forces. For example, the ring attachment can be designed as an injection-molded component. The ring attachment can also be made of steel. However, in the case of a one-piece formation, this requires a lot of material expenditure and / or processing work due to the complex structure of the ring attachment. Therefore, the ring attachment made of steel can preferably be formed in at least two parts, one part extending essentially axially and one part extending radially, and the two parts are attached together. For other materials, an at least two-piece design of the ring attachment is also possible.

[0028] The ring attachment and / or the sealing seat ring can also be designed in multiple parts and / or in segments.

[0029] Preferably, two rows of tapered rollers are provided as rolling element rows, which are arranged between the inner ring and the outer ring in an X-shaped or O-shaped arrangement. By providing the sealing device according to the invention on both sides, oil grooves can be provided for the two rows of tapered rollers. However, other bearing configurations are also conceivable, for example as a three-roller slewing bearing.

[0030] The object is also achieved by a wind turbine having a tower, a nacelle fixed to the tower and a rotor rotatably supported on the nacelle, wherein the rotor is supported on the nacelle via the above-mentioned rotor bearing. The rotor is non-rotatably connected to an outer ring of the rotor bearing and the nacelle is non-rotatably connected to an inner ring of the rotor bearing.

[0031] Further advantageous embodiments can be found in the following description. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] The invention is explained in more detail below with reference to the embodiments shown in the drawings.

[0033] Figure 1 A wind power plant according to the invention is schematically shown, which has a rotor supported by a rotor bearing according to the invention.

[0034] Figure 2a A first embodiment of a rotor bearing according to the invention is schematically shown in cross-section.

[0035] Figure 2b Schematically shows the Figure 2a A detailed view of a cutout portion X,

[0036] Figure 3 Schematically shows a detailed view of a second embodiment of a rotor bearing according to the invention, which has an oil supply device for decompressing the second seal,

[0037] Figure 4Schematically shows a detailed view of a third embodiment of a rotor bearing according to the invention, which has a further sealing element, the second seal and the further sealing element being formed as co-directional, axially acting lip seals,

[0038] Figure 5 schematically shows a detailed view of a fourth embodiment of a rotor bearing according to the invention having a further sealing element, the second seal and the further sealing element being formed as oppositely directed, axially acting lip seals, and

[0039] Figure 6 Schematically shows a detailed view of a fifth embodiment of a rotor bearing according to the invention, in which the sealing race can be fixed to the outer ring by a threaded connection of the rotor,

[0040] Figure 7 A detailed view of a sixth exemplary embodiment of a rotor bearing according to the invention is schematically shown, which has a two-part ring attachment. DETAILED DESCRIPTION

[0041] In the different figures, identical components are always provided with the same reference symbols and are therefore usually named or mentioned only once.

[0042] Figure 1 The wind power generation device 100 according to the present invention is shown. The wind power generation device 100 includes a tower 110, a nacelle 120 fixed to the tower 110, and a rotor 130 rotatably supported on the nacelle 120. The rotor 130 is supported by a rotor bearing 1 according to the present invention (see Figures 2a to 6 ) is supported on the nacelle 120. Here, the rotor 130 is non-rotatably connected to the outer ring 3, and the nacelle 120 is non-rotatably connected to the inner ring 2. The rotor 130 includes a rotor hub 120 and a plurality of rotor blades 140 fixed to the rotor hub 120. The wind force and gravity acting on the rotor blades 140 are therefore introduced into the outer ring 3 of the rotor bearing 1 through the rotor hub 120, and transferred to the inner ring 2 and the nacelle 120 via the rolling element row 5.

[0043] A first exemplary embodiment of a rotor bearing 1 according to the invention has Figure 2a and Figure 2b. The rotor bearing 1 has an inner ring 2 and an outer ring 3 that can rotate relative to the inner ring 2, and the inner ring and the outer ring define a bearing internal space 4. Two rows of rolling bodies 5 that can roll between the bearing rings are arranged in the bearing internal space 4. The rotor bearing 1 has a sealing device 6 on each side for sealing the bearing internal space 4 on one side, wherein the sealing device 6 has a first seal 7 that is non-rotatably connected to the inner ring 2 and a sealing seat ring 8 that is non-rotatably connected to the outer ring 3, on which a first sealing running surface 9 for the first seal 7 is formed. The ring attachment 10 is fixed to the inner ring 2 and surrounds the sealing seat ring 8 in the radial direction R. In addition, a second seal 11 that acts between the sealing seat ring 8 and the ring attachment 10 is provided, and the second seal defines an annular space 14 formed between the radial outer surface 12 of the sealing seat ring 8 and the radial inner surface 13 of the ring attachment.

[0044] In the embodiment shown, two rows of tapered rollers are provided as rolling element rows 5, which are arranged in an O-shaped arrangement between the inner ring 2 and the outer ring 3. The inner ring 2 consists of two parts 2.1 and 2.2 which are sealed from one another. For example, conceivable alternative bearing designs are tapered roller bearings with rollers arranged in an X-shaped arrangement, symmetrical or asymmetrical tapered roller bearings or 3-roller slewing bearings.

[0045] In order to form the oil groove, the diameter of the first sealing running surface 9 is smaller than the maximum diameter of the roller contact surface 15 for the rolling element row 5 on the outer ring 3. The first sealing running surface 9 for the first seal 7 is therefore attached to the sealing ring 8 in the radial direction R so that it is arranged in the area of ​​the roller contact surface 15 for the rolling element row 5 formed on the outer ring 3. In the bearing inner space 4, the introduced lubricating oil therefore accumulates until it reaches the roller contact surface 15, so that the rolling elements are immersed in the oil groove in the peripheral area of ​​the lower part of the bearing during each rotation and are wetted with lubricant. Since the sealing ring 8 has a radially inwardly protruding part, on which the sealing running surface 9 is arranged, an oil groove is formed in the raceway system, which ensures sufficient wetting of the rolling contacts and sliding guides in the bearing even in the event of an oil supply failure. The maximum filling height H of the oil groove is at Figure 2b Marked by a dotted line.

[0046] like Figure 2bAs shown, a discharge port 16 for connecting an oil recovery element can be provided in the ring attachment 10, the flow cross section of which is arranged at least partially in the radial direction R further outward than the sealing gap 17 of the second seal 11. In the illustrated embodiment, the discharge is performed in the radial direction R. The rotor bearing is mounted in such a way that the discharge port 16 is arranged in the lowermost peripheral section in the vertical direction to ensure effective oil discharge. The ring attachment 10 is preferably formed in a groove shape with a side surface rising toward the second seal 11 in the region of the discharge port 16. Even at an inclination of the axis of the rotor bearing, which is usually about 6°, the discharge port 16 is preferably located below the second seal 11, so that the second seal is not loaded by the existing oil, but only by the spray oil. The discharge port 16 is therefore arranged in the region of a recess 26 formed in the radial inner surface of the ring attachment, so that the further sealing element 22 is located above the return flow level defined by the recess 26.

[0047] Drainage is achieved by connecting the annular space 14 between the first seal 7 and the second seal 11 to the recovery part of the oil lubrication system of the rotor bearing 1. The leaking oil can be actively fed back to the oil lubrication system by negative pressure, or it can also be passively fed back to the oil lubrication system by geodetic height difference. Preferably, a discharge port 16 is provided on both sides of the bearing on the sealing device 6. The oil is supplied and discharged by a supply device, which is connected to the fixed inner ring 2 by a pipe or a hose. In this case, even if the monitoring device fails, oversupply of the bearing is reliably avoided. Ventilation of the bearing must also be ensured.

[0048] Due to the discharge of the leakage oil, a certain amount of leakage oil flow is tolerable or even desirable. This reduces the required seal preload and the resulting rotational resistance. In addition, seal wear is minimized and the service life of the seals 7, 11 is increased, which helps to reduce the maintenance work of the wind power plant 100.

[0049] In the annular space 14, in front of the second seal 11, an oil dripping edge 18 is formed on the radial outer surface 12 of the sealing seat ring 8 to separate the entrained oil. The oil dripping edge 18 is preferably arranged in front of the further sealing element 22. By providing the oil dripping edge 18, a simpler and cheaper sealing type can be used for the second seal 11.

[0050] Both seals 7, 11 can be designed to seal radially or also axially (with respect to the bearing axis A of the rotor bearing). In principle, the two seals 7, 11 can be designed identically. However, in a preferred embodiment, the first seal 7 rests on the first sealing running surface 9 with a first lip preload force that is greater than the second lip preload force of the second seal 11. As a result, the first seal 7 forms a main seal and the second seal 11 forms a secondary seal. In the embodiment shown, it is preferably provided that the first seal 7 is designed as a radially acting main seal and the second seal 11 is designed as an axially acting secondary seal 11.

[0051] The first seal 7 is preferably formed as a non-headless, joined lip seal. As the sealing material of the first seal 7, preferably nitrile rubber (NBR) or hydrogenated nitrile rubber (HNBR) is used.

[0052] The second seal 11 is preferably made of Perbunan as a dust seal. Alternatively, the second seal 11 can also be made of NBR or HNBR, for example.

[0053] In order to improve the sealing effect, it is also possible to use spring-assisted sealing systems, such as finger spring seals, in particular for the first seal 7 , or felt and / or labyrinth seals.

[0054] like Figure 2b As shown, the first seal 7 can be axially clamped on the inner ring 2 by means of a ring attachment 10. For this purpose, the ring attachment 10 is preferably fixed to the inner ring 2 by means of a threaded connection and seals against it. When the screws are tightened, the seal 7 is clamped in the radial shoulder of the inner ring 2 and is thereby radially positioned at the same time.

[0055] In the embodiment shown, the first seal 7 and the second seal 11 are held in their position by the ring attachment 10, and the seal seat ring 8 has a first sealing running surface 9 for the first seal 7 and a second sealing running surface 19 for the second seal 11. The advantage of this solution is that only the ring attachment 10 has to be removed to replace the seals.

[0056] The sealing ring 8 is preferably fixed to the outer ring 3 by a threaded connection. In this case, through-screws can also be used to fix one sealing ring 8 on each side of the bearing 1 at the same time. However, the sealing ring can also be formed in one piece with the outer ring.

[0057] For centering, axially acting engagement means 20 are provided on the ring attachment 10 and the sealing seat ring 8, which engage with complementary engagement means 21 on the inner ring 2 and, respectively, on the outer ring 3. Figure 2a and Figure 2bIn the embodiment shown, the ring attachment 10 has an axial projection 20 which engages axially in a front groove on the inner ring 2 and thereby prevents radial movement of the ring attachment 10. Likewise, the sealing seat ring 8 has a stop edge which engages in a front shoulder on the outer ring 3.

[0058] like Figure 2b As shown, the sealing ring 8 is preferably fixed to the outer ring 3 by means of a threaded connection and is sealed relative to the outer ring 3 by means of an O-ring which is arranged radially inside the threaded connection.

[0059] The sealing seat ring 8 is preferably made of steel which is hardened at least in the region of the first sealing running surface 9 to reduce seal wear. However, the sealing seat ring can also be formed, for example, from another metal or plastic material.

[0060] The ring attachment 10 is preferably made of a plastic material. However, it is also conceivable and possible to form it from steel.

[0061] When formed from steel, the ring attachment 10 and the sealing seat ring 8 may be implemented separately or in one piece in the form of a forged ring, a cast ring or a combined ring.

[0062] exist Figure 2a In the embodiment shown, the sealing device 6 is formed identically on both sides of the bearing. However, in alternative embodiments, the sealing device 6 can also have a different design on both sides of the bearing. For example, an additional sealing element can be provided only on one side (see Figure 4 and Figure 5 ), or an oil collection container may be provided in place of the oil recovery member.

[0063] Figure 3 FIG. 2 shows a second embodiment of a rotor bearing 1 according to the invention. In contrast to the first embodiment, the second seal 11 is arranged so that it acts radially. Figure 3 As shown, regardless of its direction of action, the second seal 11 can be retained by the seal seat ring 8. Then, a second sealing running surface 19 is formed on the ring attachment 10.

[0064] Furthermore, unlike the first embodiment, Figure 3 An axial drain port 16 is shown in the ring attachment 10 for connection to an oil recovery member.

[0065] Furthermore, an oil conveying device 24 is provided on the radially outer surface 12 of the sealing seat ring 8, which is adapted to convey the entrained oil away from the second seal 11 when the outer ring 3 rotates in the preferred direction of rotation. The radially outer surface 12 is then formed such that the entrained oil is guided away from the second seal 11. Figure 3As shown, the oil conveying means 24 can be formed, for example, as thread-shaped grooves 25 in the radially outer surface 12 of the sealing seat ring 8. It is also conceivable to use inclined lamellae as the oil conveying means 24, for example.

[0066] Otherwise, the description of the first exemplary embodiment applies correspondingly to the second exemplary embodiment.

[0067] exist Figure 4 A third embodiment of the rotor bearing according to the present invention is shown in . The main difference between the third embodiment and the first embodiment is that at least one additional sealing element 22 is provided between the first seal 7 and the second seal 11 to relieve the pressure of the second seal 11 and divide the annular space 14 into two chambers.

[0068] The second seal 11 and the further sealing element 22 are formed as axially acting lip seals with an axially oriented lip preload. In addition, the chamber between the further sealing element 22 and the second seal 11 is equipped with a further drain opening 27 in the ring attachment 10. In this way, a three-stage sealing system is formed with a second oil collecting chamber, which can be connected to an oil collecting container or an oil recovery element via the further drain opening 27. This can further reduce the leakage volume flow that still remains. Advantageously, the oil recovery element is connected to a non-return valve so that oil from the oil recovery element cannot flow back into the second chamber.

[0069] Another possibility for optimization is to set an overpressure or underpressure for the first and / or second oil collecting chamber. Figure 4 In the co-directional lip seal of the second chamber, the other sealing element 22 is released by the overpressure in the second chamber and the flow direction of the leakage volume flow is deflected in the direction of the first chamber. The sealing effect and the friction torque can be optimized by the good combination of overpressure / negative pressure in the two oil collecting chambers and the arrangement of the lip seal.

[0070] Figure 5 A fourth embodiment of the present invention is shown. Figure 4 The main difference of the exemplary embodiment shown is that the second seal 11 and the further sealing element 22 are designed as lip seals acting in opposite directions and axially. In this sealing arrangement, the overpressure formed in the second oil collecting chamber between the seals leads to an increase in the sealing effect of the two seals. The sealing lips are arranged in such a way that the corresponding sealing gap is closed by the overpressure.

[0071] Otherwise, the description of the first exemplary embodiment applies correspondingly to the third and fourth exemplary embodiments.

[0072] Figure 6 The fifth embodiment shown in Figure 2bThe difference from the first embodiment in the embodiment shown is that the sealing ring 8 extends in the radial direction into the region of the fixing boreholes 23 in the outer ring 3. The fixing boreholes 23 are primarily used to fix the rotor bearing to the rotor of the wind turbine by means of fixing screws 28. In the embodiment shown, the sealing ring 8 can be clamped to the connection structure by means of this standard threaded connection when assembling the rotor. This has the advantage that only fewer and smaller screws and boreholes have to be introduced into the rotating ring for assembly, and the dimensional accuracy of the sealing ring 8 is still guaranteed in the clamped state.

[0073] Otherwise, the description of the first exemplary embodiment applies correspondingly.

[0074] Figure 7 A sixth embodiment of a rotor bearing according to the invention is shown, which differs from the first embodiment in that the ring attachment 10 is formed in two parts. The ring attachment comprises a first ring extending essentially radially and a second ring extending essentially axially, which are joined together in a corner region and sealed against each other. For example, a threaded connection 29 can be used to join the rings. However, other joining methods are also conceivable, such as welding or gluing.

[0075] The at least two-piece design of the ring attachment 10 has the advantage that complex shapes of the ring attachment 10 can be manufactured more cost-effectively, assembly is simplified and the seal 7,

[0076] 11. In an alternative embodiment, the separate ring attachment 10 can also be segmented.

[0077] Otherwise, the description of the first exemplary embodiment applies correspondingly.

[0078] Description of Reference Numerals

[0079] 1Rotor bearing

[0080] 2.2.1.2.2 Inner Ring

[0081] 3 Outer ring

[0082] 4 Bearing internal space

[0083] 5 rolling element rows

[0084] 6 Sealing device

[0085] 7 First seal

[0086] 8 Sealing seat ring

[0087] 9 First sealing running surface

[0088] 10 ring attachment

[0089] 11 Second seal

[0090] 12 Radial outer surface

[0091] 13 Radial inner surface

[0092] 14 Ring Space

[0093] 15 Roller contact surface

[0094] 16 Discharge port

[0095] 17 Sealing gap

[0096] 18 drops of oil edge

[0097] 19 Second sealing running surface

[0098] 20 Jointing device

[0099] 21 Complementary engagement device

[0100] 22 Sealing element

[0101] 23 Fixed drilling

[0102] 24 Oil delivery device

[0103] 25 slots

[0104] 26 Depression

[0105] 27 Discharge port

[0106] 28 fixing bolts

[0107] 29 Threaded connection

[0108] 100 Wind power generation equipment

[0109] 110 Tower

[0110] 120 Cabin

[0111] 130 rotor

[0112] 140 rotor blades

[0113] 150 rotor hub

[0114] R Radial

[0115] H Filling height

[0116] A Bearing axis

Claims

1. A rotor bearing for a wind power plant (100), the rotor bearing comprising an inner ring (2) and an outer ring (3) rotatable relative to the inner ring (2), the inner ring and the outer ring defining a bearing interior space (4), at least one row (5) of rolling bodies being arranged in the bearing interior space and being able to roll between the bearing rings (2, 3), and the rotor bearing comprising sealing devices (6) for sealing the bearing interior space (4) on one side, at least one of the sealing devices (6) comprising a first seal (7) non-rotatably connected to the inner ring (2) and a sealing seat ring (8) non-rotatably connected to the outer ring (3), a first sealing running surface (9) for the first seal (7) being formed on the sealing seat ring, characterized in that: A ring attachment (10) is fixed on the inner ring (2), the ring attachment surrounds the sealing seat ring (8) in the radial direction (R), and a second seal (11) is provided between the sealing seat ring (8) and the ring attachment (10), the second seal defining an annular space (14) formed between a radial outer surface (12) of the sealing seat ring (8) and a radial inner surface (13) of the ring attachment; a discharge port (16) for connecting an oil recovery member is provided in the ring attachment (10), and has a flow cross section which is at least partially arranged radially (R) further outward than a sealing gap (17) of the second seal (11).

2. The rotor bearing according to claim 1, characterized in that: The first sealing running surface (9) has a smaller diameter than the maximum diameter of the roller contact surface (15) for the rolling element row (5) on the outer ring (3) to form an oil groove.

3. The rotor bearing according to any one of claims 1 to 2, characterized in that: In the annular space (14), in front of the second seal (11), an oil dripping edge (18) is formed on the radial outer surface (12) of the sealing seat ring (8) for separating the entrained oil.

4. The rotor bearing according to any one of claims 1 to 2, characterized in that: The first seal (7) is clamped axially against the inner ring (2) by means of a ring attachment (10).

5. The rotor bearing according to any one of claims 1 to 2, characterized in that: The first seal (7) and the second seal (11) are held in their positions by means of a ring attachment (10), and a second sealing surface (19) for the second seal (11) is formed on the sealing seat ring (8).

6. The rotor bearing according to any one of claims 1 to 2, characterized in that: The first sealing element (7) bears against the first sealing running surface (9) with a first lip preload force which is greater than a second lip preload force of the second sealing element (11).

7. The rotor bearing according to any one of claims 1 to 2, characterized in that: For centering, axially acting engagement means (20) are provided on the ring attachment (10) and / or the sealing seat ring (8) which engage with complementary engagement means (21) on the inner ring (2) and / or respectively on the outer ring (3).

8. The rotor bearing according to any one of claims 1 to 2, characterized in that: The sealing seat ring (8) is fixed to the outer ring (3) by means of a threaded connection and is sealed relative to the outer ring (3) by means of an O-ring which is arranged radially inside the threaded connection.

9. The rotor bearing according to any one of claims 1 to 2, characterized in that: In order to relieve the pressure of the second seal (11), at least one further sealing element (22) is arranged between the first seal (7) and the second seal (11), said further sealing element dividing the annular space (14).

10. The rotor bearing according to claim 9, characterized in that The second seal (11) and the further sealing element (22) are designed as axially acting lip seals with lip preloads directed in the same or opposite directions in the axial direction.

11. The rotor bearing according to claim 9, characterized in that: In the ring attachment (10), a further discharge opening (27) is provided between the further sealing element (22) and the second seal (11).

12. The rotor bearing according to any one of claims 1 to 2, characterized in that: The outer ring (3) has a fixing bore (23) for fixing the rotor bearing (1) to the rotor (130) of the wind power generation device (100) by means of fixing bolts (28), and the sealing ring (8) extends in the radial direction (R) into the area of ​​the fixing bore (23) for clamping the sealing ring (8) when assembling the rotor (130).

13. The rotor bearing according to any one of claims 1 to 2, characterized in that: The sealing seat ring (8) is made of steel and is hardened at least in the region of the first sealing running surface (9).

14. The rotor bearing according to any one of claims 1 to 2, characterized in that: The ring attachment (10) is made of plastic material.

15. The rotor bearing according to any one of claims 1 to 2, characterized in that: Two rows of tapered rollers are provided as rolling element rows (5), which are arranged in an X or O shape between the inner ring (2) and the outer ring (3).

16. A wind power plant having a tower (110), a nacelle (120) fixed to the tower (110), and a rotor (130) rotatably supported on the nacelle (120), characterized in that: The rotor (130) is supported on the nacelle (120) via a rotor bearing (1) according to any one of claims 1 to 15, wherein the rotor (130) is non-rotatably connected to an outer ring (3) and the nacelle (120) is non-rotatably connected to an inner ring (2).

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