Bearing device for wind turbine and wind turbine

Abstract

The present invention relates to a bearing arrangement for a wind turbine, comprising a bearing housing and a drive shaft, wherein the drive shaft is arranged in the bearing housing in an axial direction along a longitudinal axis of the bearing housing, the bearing arrangement further comprising a downwind bearing and an upwind bearing, wherein the downwind bearing and the upwind bearing are arranged between the bearing housing and the drive shaft, wherein the downwind bearing and / or the upwind bearing are radial bearings comprising a plurality of radial bearing pads, wherein each of the plurality of radial bearing pads is attached to one of a plurality of radial bearing bodies of the radial bearing, and the plurality of radial bearing pads are arranged around the drive shaft. The downwind bearing and / or the upwind bearing are connected to an axial bearing of the bearing arrangement, wherein at least one axial bearing pad of the axial bearing is attached to at least one of the plurality of radial bearing bodies.

Description

Technical Field

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

[0002] Typically, a bearing arrangement of a wind turbine comprises a bearing housing and a drive shaft, wherein the drive shaft is arranged in the bearing housing in an axial direction along the longitudinal axis of the bearing housing. A bearing of the bearing arrangement is arranged around the drive shaft so that the drive shaft can rotate in the bearing housing by means of a rotor of the wind turbine. Such a bearing arrangement is known, for example, from EP 3276192 A1.

[0003] Such a bearing may be a radial bearing comprising a plurality of radial bearing bodies, a plurality of radially tiltable support structures fixed to the plurality of radial bearing bodies, wherein each of a plurality of radial bearing pads is attached to one of the plurality of radially tiltable support structures. In addition to the radial bearings, an axial bearing is also required to maintain positive thrust from the wind. The axial bearing is a separate bearing arranged between the bearing housing and the drive shaft. It requires its own assembly space, bearing components and lubrication system. Summary of the invention

[0004] The object of the present invention is to eliminate or at least reduce the disadvantages of the prior art related to the arrangement of radial bearings and axial bearings in a bearing housing, in particular to provide a bearing arrangement for a wind turbine having a simple and cost-effective bearing concept.

[0005] This object is achieved by the subject matter of the claims. In particular, the object is achieved by a bearing arrangement for a wind turbine according to the invention and a wind turbine according to the invention. Further details of the invention are derived from the other claims as well as from the description and the drawings. Therefore, the features and details described in conjunction with the bearing arrangement of the invention are applied in conjunction with the wind turbine of the invention, such that the disclosure of the various aspects of the invention, which are or can be referred to one another, are also applicable.

[0006] According to a first aspect of the present invention, the present invention relates to a bearing device for a wind turbine, the bearing device comprising a bearing housing and a drive shaft, wherein the drive shaft is arranged in the bearing housing in an axial direction along a longitudinal axis of the bearing housing, the bearing device further comprising a downwind bearing and an upwind bearing, wherein the downwind bearing and the upwind bearing are arranged between the bearing housing and the drive shaft, wherein the downwind bearing and / or the upwind bearing are radial bearings comprising a plurality of radial bearing pads, wherein each of the plurality of radial bearing pads is attached to one of a plurality of radial bearing bodies of the radial bearing, and the plurality of radial bearing pads are arranged around the drive shaft, wherein the downwind bearing and / or the upwind bearing are connected to an axial bearing of the bearing device, wherein at least one axial bearing pad of the axial bearing is attached to at least one of the plurality of radial bearing bodies.

[0007] In particular, the downwind bearing is connected to an axial bearing of the bearing arrangement.Furthermore, in particular, each of a plurality of axial bearing pads of the axial bearing is attached to one of the plurality of radial bearing bodies.

[0008] By means of the invention, radial bearings and axial bearings are combined in a cost-effective and simple manner.

[0009] The leeward bearing is particularly arranged around the leeward portion of the drive shaft. The upwind bearing is particularly arranged around the upwind portion of the drive shaft. The leeward bearing may alternatively be referred to as a rear bearing arranged around the rear end portion of the drive shaft. The upwind bearing may alternatively be referred to as a front bearing arranged around the front end portion of the drive shaft. In a wind turbine, the front end of the drive shaft is positioned closer to the rotor than the rear end of the drive shaft.

[0010] Preferably, the at least one axial bearing pad is attached to at least one of the plurality of radial bearing bodies by means of an axially tiltable support structure. The axially tiltable support structure provides a tilting function of the axial bearing for compensating tolerances in the radial fluid bearing.

[0011] Further preferably, the at least one of the plurality of radial bearing bodies comprises a radial bearing body projection, the radial bearing body projection extending in an axial direction along the longitudinal axis, and the axially tiltable support structure of the at least one axial bearing pad is attached to the radial bearing body projection. Thereby, a stable but space-saving design of the bearing is achieved.

[0012] Furthermore, preferably, the at least one of the plurality of radial bearing pads and the at least one axial bearing pad are fluidly connected to each other. Thus, the lubrication of the axial bearing and the radial bearing can be effectively combined, thereby reducing the lubrication effort.

[0013] Preferably, the at least one axial bearing pad and the plurality of radial bearing pads are enclosed in a common lubricant overflow chamber, wherein the lubricant overflow chamber is sealed against the drive shaft, the inner space of the bearing housing and the outer side of the bearing housing. Therefore, the lubricant inside the lubricant overflow chamber cannot leave the lubricant overflow chamber except by means of leakage. Therefore, a lubricant overflow chamber in the sense of the present invention is a chamber filled with lubricant, wherein the lubricant is contained in the lubricant overflow chamber. The lubricant can be, for example, oil. Thus, a passive lubrication system is provided in which a lubricant is contained. Since the lubricant is not circulated through several pipelines and pumps, the passive lubrication system provided requires little maintenance, is not prone to failure, is simple and cost-effective.

[0014] Preferably, the axial bearing comprises an axial collar arranged opposite to the at least one axial bearing pad. The axial collar serves as a stop for the at least one axial bearing pad. In particular, the axial collar can be arranged on the drive shaft. Furthermore, the axial collar can be formed integrally with the drive shaft, in particular designed integrally with the drive shaft. The axial collar can in particular extend outwardly from the drive shaft. In other words, the axial collar can extend radially outwardly relative to the cylindrical surface of the drive shaft.

[0015] Preferably, the axial bearing comprises at least one loose bearing pad arranged opposite to the second contact surface of the axial collar, wherein the second contact surface faces in the opposite direction of the first contact surface of the axial collar, wherein the first contact surface of the axial collar is arranged facing the at least one axial bearing pad. Thus, negative thrust, i.e. thrust in the opposite direction to the wind, can be held by the axial bearing. In particular, a plurality of loose bearing pads can be arranged opposite to the second contact surface of the axial collar.

[0016] It is further preferred that the at least one loose bearing pad is attached to the bearing housing, in particular by means of a flange. The at least one loose bearing pad may be locked in particular by means of the flange, in particular by means of a connecting device, such as a bolt. The flange may be attached to or formed integrally with an inner shell surface and / or an inner circumferential portion of the bearing housing. Thereby, a simple and cost-effective structure for the loose bearing pad is provided.

[0017] Further preferably, the axial collar is arranged around a circumferential portion of the drive shaft. In particular, the axial collar may be arranged around the entire circumferential portion of the drive shaft.

[0018] Furthermore, the axial collar is preferably coated with a hardened material. The hardened material can be, for example, cold sprayed onto the axial collar. As a result, the axial collar comprises high elasticity and a high service life.

[0019] Preferably, the plurality of radial bearing bodies are arranged adjacent to each other along the circumferential portion of the cylindrical seat. The cylindrical seat can be formed in the bearing housing. In particular, the cylindrical seat can be formed by the inner shell surface of the bearing housing. In addition, the cylindrical seat can be formed integrally with the bearing housing, in particular designed integrally. As a result, the cylindrical seat of the radial bearing is stably arranged at the bearing housing.

[0020] Preferably, each of the plurality of radial bearing pads is attached to one of the plurality of radial bearing pads by means of a radially tiltable support structure, whereby in particular the radially tiltable support structure is connected to at least one of the plurality of radial bearing bodies by means of a spring connection. The plurality of radially tiltable support structures allow the plurality of radial bearing pads to be tiltable relative to the drive shaft. Thereby, tolerances between the drive shaft and the radial bearing pads can be compensated. At least one of the plurality of radially tiltable support structures may comprise a ball head. The ball head may provide a tilting function for compensating for tolerances in the radial bearing. Furthermore, the at least one of the plurality of radial bearing bodies to which the at least one of the plurality of radially tiltable support structures comprising the ball head is fixed may comprise a ball socket for the ball head.

[0021] At least one curved interface plate may be attached to at least one of the plurality of radial bearing bodies opposite to the radial bearing pad, wherein the interface plate is arranged to contact the cylindrical seat of the radial bearing. Thereby, the radial bearing pad is arranged with very small tolerances relative to the drive shaft and with low cost relative to manufacturing and assembly. A curved interface plate may be attached to each of the plurality of radial bearing bodies opposite to the radial bearing pad, wherein the interface plate is arranged to contact the cylindrical seat of the radial bearing. The first interface plate side of the at least one interface plate in contact with the cylindrical seat may have a curvature corresponding to the curvature of the cylindrical seat. Thereby, the interface plate may be provided with a large contact surface contacting the cylindrical seat, whereby the stability of the radial bearing is improved. Furthermore, the second interface plate side of the at least one interface plate positioned opposite to the first interface plate may be mainly flat or flat. In this sense, "mainly" means that more than half of the surface of the second interface plate side is flat. Thereby, the attachment of the radial bearing body to the interface plate may be facilitated. At least one of the at least one interface plate may include at least one interface plate attachment device, the at least one interface plate attachment device being used to attach the at least one interface plate to the at least one of the plurality of radial bearing bodies. The at least one of the plurality of radial bearing bodies may comprise a corresponding radial bearing body attachment means. The interface plate attachment means and the corresponding radial bearing body attachment means may be attached to each other by means of a further attachment means element. Thus, the interface plate may be securely attached to the radial bearing body. At least one of the at least one interface plate attachment means may be an interface plate through hole. The interface plate through hole may comprise, for example, a thread. The radial bearing body attachment means may also be a radial bearing body through hole, which may also comprise a thread. The attachment means element may be a bolt, in particular, for example, a threaded bolt.

[0022] The at least one of the plurality of radial bearing bodies to which the at least one interface plate is attached may be fixed by means of a limit stop attached to the cylindrical seat, wherein the limit stop is adjacent to the at least one of the plurality of radial bearing bodies in a tangential direction along a circumferential portion of the cylindrical seat. In particular, the limit stop may be arranged in a groove arranged in the cylindrical seat. Further, the limit stop may be attached to the cylindrical seat by means of a bolt. In particular, each of the plurality of radial bearing bodies is separated from another of the plurality of radial bearing bodies by means of one of the limit stops along the cylindrical seat. The limit stop prevents the interface plate from moving in a tangential direction along a circumferential portion of the cylindrical seat. The at least one of the plurality of radial bearing bodies to which the at least one interface plate is attached may be fixed to the cylindrical seat by means of at least one fastening element, wherein the at least one fastening element at least partially extends through the at least one of the plurality of radial bearing bodies. At least two fastening elements may at least partially extend through at least one of the plurality of radial bearing bodies. In particular, the at least one fastening element may protrude into the cylindrical seat.The fastening element may be, for example, a bolt.The at least one fastening element prevents a movement of the interface plate from the bearing housing to the drive shaft in a radial direction.

[0023] Alternatively, the plurality of bearing bodies are arranged adjacent to each other along the circumferential portion of the cylindrical seat of the bearing housing, wherein the adjacent bearing bodies are locked in terms of movement relative to each other and relative to the cylindrical seat by means of a press-fitted locking piece. The locking piece may protrude above the adjacent bearing bodies. In addition, the locking piece may protrude above the adjacent bearing bodies so that there is a space between the locking piece and the bearing body. The locking piece may be inserted into the cylindrical seat. The locking piece may, for example, be arranged in a groove of the cylindrical seat. The locking piece may also be referred to as a slide-in locking piece because they can easily slide into the groove of the cylindrical seat in the axial direction along the longitudinal axis of the bearing housing. The locking piece may provide a dovetail connection with the cylindrical seat. The bottom portion of the locking piece may extend in a tangential direction along the circumferential portion of the cylindrical seat. For example, the undercut in the groove may extend in a tangential direction of the circumferential portion of the cylindrical seat. At least one of the locking pieces may be a T-shaped rod element or an I-shaped rod element. In addition, all locking pieces may be T-shaped rods and / or I-shaped rod elements. When viewed in the axial direction along the longitudinal axis of the bearing housing, the T-shaped rod element has substantially the shape of a T, and the I-shaped rod element has substantially the shape of an I. At least one spring element may be arranged between at least one of the locking members and one of the adjacent radial bearing bodies. The at least one spring element may be arranged in particular between the upper portion of the locking member and the top surface of the one radial bearing body. In particular, two spring elements may be arranged between at least one of the locking members and one of the adjacent radial bearing bodies. The two spring elements are preferably separated from each other, in particular by means of a locking member arranged between the two spring elements. The spring element supports the locking member by providing a pretension to lock the radial bearing body against the cylindrical seat in the radial direction. The radial direction is the direction from the cylindrical seat to the drive shaft. A rigid element may be arranged between the at least one of the adjacent bearing bodies and the at least one spring element. The rigid element may be made of, for example, metal. The spring element may be an elastomer. The locking member may include a stop plate, which is arranged against the edge of the cylindrical seat in the axial direction along the longitudinal axis. The stop plate may be connected to the edge of the cylindrical seat, for example, by means of bolts. As a result, the movement of the bearing body in the axial direction along the longitudinal axis is locked. At least one wear protection element can be arranged between at least one of the locking elements and the cylindrical seat or the radial bearing body. In particular, at least two wear protection elements can be arranged between the locking element and the cylindrical seat, whereby the wear protection elements are separated from each other by means of the locking element. Furthermore, in particular, at least two wear protection elements can be arranged between the locking element and the radial bearing body, wherein the wear protection elements are separated from each other by means of the locking element and each of the at least two wear protection elements is in contact with only one of the radial bearing bodies. The wear protection element can include or be made of a polymer, in particular a thermosetting polymer. The wear protection element reduces the risk of abrasion of the locking element.

[0024] According to a second aspect of the invention, the invention relates to a wind turbine comprising a bearing arrangement according to the invention, wherein the wind turbine further comprises a rotor connected to drive a drive shaft and a generator connected to be driven by the drive shaft.

[0025] The generator may be, for example, a direct drive generator or a geared generator with a gearbox. The rotor is also often referred to as the hub of the wind turbine. Two, three or more wind turbine blades may be attached to the rotor or the hub. The wind turbine may also include a nacelle, which may be supported on a tower of the wind turbine. The nacelle may include a bearing arrangement. The bearing arrangement, in particular the bearing housing and the generator may be attached to the nacelle and / or the tower. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Further advantages, features and details of the invention are revealed from the following description, in which reference is made to the accompanying drawings. Figures 1 to 12 , describes the embodiments of the present invention in detail. Therefore, the features from the claims and the features mentioned in the description may be essential to the present invention, as adopted individually or in any combination. In the accompanying drawings, it is schematically shown:

[0027] Figure 1 is a side view of a wind turbine.

[0028] Figure 2 is along Figure 1 A side perspective view of a section along the longitudinal axis of a bearing arrangement of a wind turbine,

[0029] Figure 3 is along Figure 1 A side view of a cross section of a bearing arrangement of a wind turbine,

[0030] Figure 4 Shows Figure 3 A view of the details of the bearing arrangement,

[0031] Figure 5 Shows Figure 3 A view of further details of the bearing arrangement,

[0032] Figure 6 Shown along Figure 1 A side perspective view of a section along the longitudinal axis of another bearing arrangement of a wind turbine,

[0033] Figure 7 Shown through Figure 6 A front view of a cross section of a bearing arrangement,

[0034] Figure 8 Shows Figure 7 A detailed view of the bearing arrangement showing the radial bearing unit, and

[0035] Fig. 9 Shown as Figure 8 Two views of the curved interface plate shown in the bearing arrangement,

[0036] Fig.10 Shown through Figure 1 A front view of a section of a cross section of another bearing arrangement of a wind turbine, and

[0037] Fig.11 Shows Fig.10 A view of the details of the bearing arrangement, and

[0038] Fig.12 Shows Fig.11 Another view of a detail of the bearing arrangement.

[0039] Figures 1 to 12 Identical objects are named with the same reference numerals. If more than one object of the same kind is present in one figure, the objects are numbered in ascending order, wherein the ascending number of the object is separated from its reference numeral by a dot. Specific dimensions of features and parts in the drawings are exemplary and may be exaggerated for ease of reference only. DETAILED DESCRIPTION

[0040] Figure 1 1 shows a side view of a wind turbine 10. The wind turbine 10 comprises a supporting tower 20 and a nacelle 30, wherein the nacelle 30 is attached to the supporting tower 20. The nacelle 30 comprises a bearing arrangement 70, which is arranged at Figure 1 Not shown, but in Figure 2 The wind turbine 10 further comprises a generator 40 attached to a rotor 50 of the wind turbine 10. Attached to the rotor 50 are two wind turbine blades 60.1, 60.2.

[0041] Figure 2 Shown along Figure 1 1 is a side perspective view of a section of a bearing arrangement 70 of a wind turbine 10 along a longitudinal axis A. The bearing arrangement 70 comprises a bearing housing 80 and a drive shaft 90, wherein the drive shaft 90 is arranged in the bearing housing 80 in an axial direction along the longitudinal axis A of the bearing housing 80, as shown in FIG. Figure 2As shown. The longitudinal axis A of the bearing housing 80 corresponds to the longitudinal axis A of the drive shaft 90 and is thus the longitudinal axis A of the bearing device 70. The bearing device 70 also includes a downwind bearing 100 and an upwind bearing 200 as radial bearings, wherein the downwind bearing 100 and the upwind bearing 200 are arranged between the bearing housing 80 and the drive shaft 90. In particular, the downwind bearing 100 is arranged around the downwind portion of the drive shaft 90, and the upwind bearing 200 is arranged around the upwind portion of the drive shaft 90. The drive shaft 90 is operably connected to the generator 40. The generator 40 is shown as a direct-drive generator. However, the generator 40 can also be set as a gear-driven generator, for example.

[0042] Figure 3 Shown along Figure 2 80 is a side view of a cross section of the longitudinal axis A of the bearing device 70. An internal space 82 of the bearing housing 80 is formed between the bearing housing 80 and the drive shaft 90. Lubricant can leak from the downwind bearing 100 and the upwind bearing 200 into the internal space 82 and thereby be collected in the bearing housing 80, which is formed as a funnel 85 in the bottom portion of the bearing housing 80. The lubricant pump 88 is fluidly connected to a discharge outlet (not shown) of the bearing housing 80. In addition, a downwind bearing 100 including a lubricant overflow chamber 101 and an upwind bearing 200 including a lubricant overflow chamber 201 are shown, and their principles and features will be referred to Figure 4 and Figure 5 Further explanation.

[0043] Figure 4 Shown according to Figure 3 Detail IV of an enlarged view of a section through an upwind bearing 200 and its lubricant overflow chamber 201 . A radial bearing body 203 is attached to the bearing housing 80 . Specifically, the radial bearing body 203 is attached to a cylindrical seat 202 formed in the bearing housing 80 . A radially tiltable support structure 204 is fixed to the radial bearing body 203 . A radial bearing pad 205 is attached to the radially tiltable support structure 204 . The radial bearing pad 205 is arranged in sliding contact with the drive shaft 90 . The radially tiltable support structure 204 allows a tilting movement of the radial bearing pad 205 . A plurality of such radial bearing units including a radial bearing body 203 , a radially tiltable support structure 204 and a radial bearing pad 205 are arranged in a series in the lubricant overflow chamber 201 along the cylindrical seat 202 , in particular along a circumferential portion of the cylindrical seat 202 of the upwind bearing 200 .

[0044] The lubricant overflow chamber 201 of the upwind bearing 200 is sealed against the inner space 82 of the bearing housing 80 by means of an inner seal 206. The inner seal 206 of the lubricant overflow chamber 201 of the upwind bearing 200 comprises a plurality of inner sealing plates 207. Two lip seals 212.1, 212.2 are arranged in series between the inner seal 206 and the drive shaft 90 in order to seal the inner seal 206 against the drive shaft 90.

[0045] The lubricant overflow chamber 201 of the upwind bearing 200 is sealed against the outside of the bearing housing 80 by means of an outer seal 208 and a dust seal 210. The outer seal 208 comprises an outer seal plate 209 and two lip seals 212.3, 212.4 arranged in series between the outer seal plate 209 and the drive shaft 90. The dust seal 210 is formed by a dust seal plate 211 and another lip seal 212.5 arranged between the dust seal plate and the drive shaft 90. The dust seal 210 is positioned towards the outside of the bearing housing 80. The dust seal 210 sandwiches the outer seal 208 between the dust seal 210 and the inner seal 206.

[0046] Figure 5 Shown according to Figure 3 Detail V of an enlarged view of a section through a downwind bearing 100 and its lubricant overflow chamber 101 . A radial bearing body 103 is attached to the bearing housing 80 . Specifically, the radial bearing body 103 is attached to a cylindrical seat 102 formed in the bearing housing 80 . A radially tiltable support structure 104 is fixed to the radial bearing body 103 . A radial bearing pad 105 is attached to the radially tiltable support structure 104 . The radial bearing pad 105 is arranged in sliding contact with the drive shaft 90 . The radially tiltable support structure 104 allows a tilting movement of the radial bearing pad 105 . A plurality of such radial bearing units including the radial bearing body 103 , the radially tiltable support structure 104 and the radial bearing pad 105 are arranged in a series in the lubricant overflow chamber 101 along the cylindrical seat 102 , in particular along a circumferential portion of the cylindrical seat 102 of the downwind bearing 100 .

[0047] The lubricant overflow chamber 101 of the downwind bearing 100 is sealed against the inner space 82 of the bearing housing 80 by means of an inner seal 106. The inner seal 106 of the lubricant overflow chamber 101 of the downwind bearing 100 comprises a plurality of inner sealing plates 107. Two lip seals 112.1, 112.2 are arranged in series between the inner seal 106 and the drive shaft 90 in order to seal the inner seal 106 against the drive shaft 90.

[0048] The lubricant overflow chamber 101 is fluidly connected to an effective path provided by the lubricant flow channel 303 of the axial bearing 300 of the bearing device 70. The bearing device 70 with the axial bearing 300 shown is not according to the invention because at least one axial bearing pad 127 of the axial bearing 300 is not attached to at least one of the plurality of radial bearing bodies 103. Figures 10 to 12 The bearing device 70 according to the present invention is explained in detail. Figures 2 to 9 The features of the bearing device 70 shown in FIG. 7 may also be features of the bearing device 70 according to the present invention. Figure 5 The axial bearing 300 shown in the drawing comprises an axial collar 301 and a plurality of axial bearing pads (not shown here) attached to an axial bearing stopper 302. The axial collar 301 is attached to the drive shaft 90. The axial collar 301 extends outward from the drive shaft 90. The axial collar 301 extends along the entire circumferential portion of the drive shaft 90. A lubricant flow channel 303 of the axial bearing 300 is formed between the axial collar 301 and the plurality of axial bearing pads of the axial bearing stopper 302. An overflow channel 304 of the axial bearing 300 is arranged in fluid contact with the lubricant overflow chamber 101. By means of the overflow channel 304, excess lubricant can be released from the lubricant overflow chamber 101. The overflow channel 304 can be connected to the inner space 82 for releasing the lubricant into the bearing housing 80. The downwind bearing 100 has the axial bearing 300 as a seal of the lubricant overflow chamber 101 against the outside of the bearing housing 80.

[0049] Figure 6 Shown along Figure 180 and a side perspective view of a section through the discharge outlet 83 and along the longitudinal axis A of another bearing housing 80 of a wind turbine 10. As can be seen, there are a plurality of radial bearing pads 105.1, 105.2, 105.3, 105.4, 105.5, 105.6, which are arranged in a row at the cylindrical seat 102 of the leeward bearing 100. An inner seal 106 is arranged between the radial bearing pads 105.1, 105.2, 105.3, 105.4, 105.5, 105.6 and the inner space 82 of the bearing housing 80 and is attached to the bearing housing 80, in particular to the cylindrical seat 102. Furthermore, an axial bearing 300 is arranged at the bearing housing 80 next to the leeward bearing 100. Furthermore, there are a plurality of radial bearing pads 205.1, 205.2, 205.3, 205.4, 205.5, 205.6 arranged at the cylindrical seat 202 of the upwind bearing 200. An inner seal 206 is arranged between the radial bearing pads 205.1, 205.2, 205.3, 205.4, 205.5, 205.6 and the inner space 82 of the bearing housing 80 and is attached to the bearing housing 80, in particular to the cylindrical seat 202.

[0050] Figure 7 The diagram shows the flow through the upwind bearing 200. Figure 6 Attached to the cylindrical seat 202 of the upwind bearing 200 are a plurality of radial bearing units 213.1, 213.2, 213.3, 213.4, 213.5, 213.6, 213.7, 213.8, 213.9, 213.10, 213.11, 213.12, 213.13, 213.14.

[0051] Figure 8 Shows Figure 7 Detailed view of the bearing device 70 of FIG. 7 , which shows a cross section of a radial bearing unit 213 and its attachment to a cylindrical seat 202 of a bearing housing 80. A curved interface plate 214 is attached to a radial bearing body 203 of the radial bearing unit 213 opposite the radial bearing pad 205, wherein the interface plate 214 is arranged in contact with a cylindrical seat 202 of an upwind bearing 200 formed as a radial bearing. The radial bearing body 203 comprises a ball socket for a radially tiltable support structure 204, which comprises a ball head seated on the ball socket.

[0052] like Fig. 9As shown in , the interface plate 214 includes a first interface plate side 215 and a second interface plate side 216. The first interface plate side 215 and the second interface plate side 216 have a circular circumferential portion. In other words, the interface plate 214 has a circular circumferential portion. The first interface plate side 215 is positioned opposite to the second interface plate side 216. The second interface plate side 216 is flat. The first interface plate side 215 has a curvature corresponding to the curvature of the cylindrical seat 202. In addition, the interface plate 214 includes six interface plate through holes 217.1, 217.2, 217.3, 217.4, 217.5, 217.6 arranged throughout the interface plate 214. In particular, the interface plate through holes 217.1, 217.2, 217.3, 217.4, 217.5, 217.6 are arranged around the center of the interface plate 214.

[0053] like Figure 8 As further shown in FIG. 2 , the interface plate 214 contacts the cylindrical seat 202 of the bearing housing 80 with its first interface plate side 215. The interface plate is connected by means of interface plate through holes 217 visible along the cross section, into which bolts fastening the interface plate 214 to the radial bearing body 203 can be inserted.

[0054] The radial bearing body 203 is fixed to the cylindrical seat by means of two fastening elements 219.1, 219.2 (e.g. bolts), which extend partially through the radial bearing body 203 and protrude into the cylindrical seat 202 of the bearing housing 80, the fastening elements 219.1, 219.2 being located tangentially opposite each other along a circumferential portion of the cylindrical seat 202. The fastening elements 219.1, 219.2 prevent a movement of the interface plate 214 and thereby prevent a movement of the radial bearing body 203 in the radial direction from the bearing housing 80 to the drive shaft 90.

[0055] The radial bearing body 203 is fixed by means of two limit stops 220.1, 220.2 arranged in the grooves of the cylindrical seat 202 of the bearing housing 80, so as to prevent the movement of the interface plate 214 and thereby prevent the radial bearing body 203 from moving in the tangential direction along the circumferential portion of the cylindrical seat 202. Therefore, the two limit stops 220.1, 220.2 are arranged adjacent to and in contact with the radial bearing body 203 in the tangential direction along the circumferential portion of the cylindrical seat 202 and are opposite to each other in the tangential direction.

[0056] Fig.10 Shown through Figure 11. A front view of a section of a cross section of another bearing arrangement 70 of a wind turbine 10. The section is an end section showing a leeward bearing 100 arranged between a bearing housing 80 and a drive shaft 90. Two radial bearing units 113.2 of the leeward bearing 100 are visible and named. A plurality of such radial bearing units 113.2 are arranged in series in the leeward bearing 100.

[0057] Fig.11 Shows Fig.10 XI of a detail of the bearing device 70, which shows in particular the radial bearing unit 113. The radial bearing unit 113 is attached to the cylindrical seat 102 of the bearing housing 80 by means of a radial bearing body 103 of the radial bearing unit 113, wherein the radial bearing body 103 is fixed to the bearing housing 80 by means of a fastening element 119. Furthermore, a radial bearing pad 105 is attached to the radial bearing body 103 by means of a radially tiltable support structure 104.

[0058] The axial bearing pad 127 of the axial bearing 300 is attached to the radial bearing body 103 of the leeward bearing 100 by means of an axially tiltable support structure 126. The axially tiltable support structure 126 is attached to a radial bearing body protrusion 125, which is formed integrally with the radial bearing body 103. The radial bearing body protrusion extends in an axial direction along the longitudinal axis A.

[0059] The axial bearing pads 127 and the radial bearing pads 105 are enclosed in a common lubricant overflow chamber 101. The lubricant overflow chamber 101 is sealed against the drive shaft 90, against the interior space 82 of the bearing housing 80 by means of an inner seal 106, and against the outside of the bearing housing 80 by means of an outer seal. Thereby, the axial bearing pads 127 and the radial bearing pads 105 are fluidly connected to each other.

[0060] When there is a positive thrust from the wind in the axial direction along the longitudinal axis A, i.e., from the axial collar 301 toward the axial bearing pad 127, the axial collar 301 formed integrally with the drive shaft 90 and arranged around the entire circumferential portion of the drive shaft 90 is pressed against the axial bearing pad 127, and the thrust is transmitted to the radial bearing body 103 via the radial bearing body protrusion 125 and from there to the bearing housing 80. The axially tiltable support structure 126 can be tilted relative to the axial collar 301. By means of the tiltable function of the axial bearing 300, the tolerance between the axial collar 301 and the axial bearing pad 127 is compensated.

[0061] Furthermore, when there is a negative thrust in the opposite direction, i.e. from the axial collar 301 towards the inner seal 106, the axial collar 301 is pressed against the loose bearing pads 309 of the axial bearing 300. A plurality of such loose bearing pads 309 are arranged along the entire circumferential portion of the bearing housing 80 by means of the flange 308. The loose bearing pads 309 are arranged opposite to the second contact surface of the axial collar 301, wherein the second contact surface is arranged facing in the opposite direction of the first contact surface of the axial collar 301, wherein the first contact surface of the axial collar 301 is arranged facing the axial bearing pads 127.

[0062] Fig.12 Shown as used in Fig.11 The bearing device 70 of the downstream bearing 100 Fig.11 The radial bearing unit 113 of the bearing device 70 of the embodiment of the present invention is shown in FIG. 1 . It can be clearly seen that the radial bearing body protrusion 125 is formed integrally with the radial bearing body 103, and the axially tiltable support structure 126 is attached to the radial bearing body protrusion 125, and furthermore the axial bearing pad 127 is attached to the axially tiltable support structure 126, for example by means of a spring system (not shown). The axially tiltable support structure 126 and the radially tiltable support structure 104 may comprise the same parts. In particular, the axially tiltable support structure 126 may comprise a ball head. Furthermore, the radial bearing body protrusion 125 may comprise a ball socket for the ball head, and the ball head may be movably arranged in the ball socket.

Claims

1. A bearing device (70) for a wind turbine (10), comprising a bearing housing (80) and a drive shaft (90), wherein the drive shaft (90) is arranged in the bearing housing (80) in an axial direction along a longitudinal axis (A) of the bearing housing (80), the bearing device (70) further comprising a downwind bearing (100) and an upwind bearing (200), wherein the downwind bearing (100) and the upwind bearing (200) are arranged between the bearing housing (80) and the drive shaft (90), wherein the downwind bearing (100) and / or the upwind bearing (200) are radial bearings comprising a plurality of radial bearing pads, wherein each of the plurality of radial bearing pads is attached to one of a plurality of radial bearing bodies of the radial bearing, and the plurality of radial bearing pads are arranged around the drive shaft (90), It is characterized in that The downwind bearing (100) and / or the upwind bearing (200) are connected to an axial bearing (300) of the bearing device (70), wherein at least one axial bearing pad (127) of the axial bearing (300) is attached to at least one of the plurality of radial bearing bodies, wherein the at least one axial bearing pad (127) is attached to the at least one of the plurality of radial bearing bodies by means of an axially tiltable support structure (126), and Wherein, at least one of the multiple radial bearing bodies includes a radial bearing body protrusion (125), which extends in an axial direction along the longitudinal axis (A), and an axially tiltable support structure (126) of at least one axial bearing pad (127) is attached to the radial bearing body protrusion.

2. The bearing device (70) according to claim 1, It is characterized in that At least one of the plurality of radial bearing pads and the at least one axial bearing pad (127) are fluidly connected to each other.

3. The bearing device (70) according to claim 1, It is characterized in that The at least one axial bearing pad (127) and the plurality of radial bearing pads are enclosed in a common lubricant overflow chamber, wherein the lubricant overflow chamber is sealed against the drive shaft (90), the interior space (82) of the bearing housing (80) and the outside of the bearing housing (80).

4. The bearing device (70) according to claim 1, It is characterized in that The axial bearing (300) comprises an axial collar (301) arranged opposite to the at least one axial bearing pad (127).

5. The bearing device (70) according to claim 4, It is characterized in that The axial bearing (300) includes at least one loose bearing pad (309), which is arranged opposite to the second contact surface of the axial collar (301), wherein the second contact surface is arranged to face the opposite direction of the first contact surface of the axial collar (301), and wherein the first contact surface of the axial collar (301) is arranged to face the at least one axial bearing pad (127).

6. The bearing device (70) according to claim 5, It is characterized in that The at least one loose bearing pad (309) is attached to the bearing housing (80), in particular by means of a flange (308).

7. The bearing device (70) according to claim 4, It is characterized in that The axial collar (301) is arranged around a circumferential portion of the drive shaft (90).

8. The bearing device (70) according to claim 4, It is characterized in that The axial collar (301) is coated with a hardened material.

9. The bearing device (70) according to any one of claims 1 to 8, It is characterized in that The plurality of radial bearing bodies are arranged adjacent to each other along a circumferential portion of the cylindrical seat (102).

10. The bearing device (70) according to any one of claims 1 to 8, It is characterized in that Each of the plurality of radial bearing pads is attached to one of the plurality of radial bearing bodies by means of a radially tiltable support structure (104).

11. A wind turbine (10) comprising a bearing device (70) according to any one of claims 1 to 10, wherein: The wind turbine (10) also includes a rotor (50) operably connected to drive the drive shaft (90) and a generator (40) operably connected to be driven by the drive shaft (90).

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