Axial plain bearing, transmission, and wind turbine
Patent Information
- Authority / Receiving Office
- WO · WO
- Patent Type
- Applications
- Current Assignee / Owner
- Filing Date
- 2026-01-12
- Publication Date
- 2026-08-13
Smart Images
Figure EP2026050534_13082026_PF_FP_ABST
Abstract
Description
[0001] ZF Friedrichshafen AG File 304496 Friedrichshafen 2024-12-19
[0002] Axial guide bearings, gearboxes and wind turbines
[0003] The present invention relates to an axial sliding bearing for mounting a planetary gear on a planet carrier of a planetary gear set of a wind turbine gearbox. The invention also relates to a gearbox and a wind turbine.
[0004] State of the art
[0005] Wind turbines are used to generate electricity from wind energy. For this purpose, wind turbines have a rotor. The rotor's rotational speed is transmitted by a rotor shaft to a gearbox. The gearbox then converts the rotor shaft's rotational speed into a suitable rotational speed to drive a generator. Such gearboxes often have planetary gear sets, in which each planet gear is supported by one or more axial bearings.
[0006] DE 102019207500 A1 describes an axial sliding bearing with at least two physically separate, one-piece segments. At least one segment has at least one wedge surface serving as a sliding surface. During operation, lubricating oil is conveyed through the gap formed between the wedge surface and the planet gear, for example to form a lubricating film for separating the facing end faces of the planet gear and the planet carrier.
[0007] Description of the invention
[0008] One aspect concerns an axial plain bearing for supporting a planet gear on a planet carrier of a planetary gear set in a wind turbine gearbox. The axial plain bearing can therefore be designed to support the planet gear on the planet carrier of the planetary gear set in the wind turbine gearbox. Additionally, the planet gear can be supported on the planet carrier by a radial plain bearing or a rolling bearing. For example, ZF Friedrichshafen AG File 304496 Friedrichshafen 2024-12-19
[0009] The planet gear is rotatably mounted on a planet bolt of the planet carrier. Two axial plain bearings can be arranged at axially opposite ends of the planet gear, both of which can be designed as described here. An axial plain bearing is a plain bearing that can be designed to absorb forces that act parallel to an axis of rotation of the plain bearing. The axis of rotation of the plain bearing can correspond to a longitudinal extension of an associated planet bolt and, alternatively or additionally, to an axis of rotation of the planet gear. For example, the axial plain bearing can absorb axial forces in only one direction. Means that absorb axial forces acting in the opposite direction form, for example, another axial plain bearing. Axial forces act, for example, parallel to the axis of rotation of the planet gear.
[0010] The wind turbine can consist of a tower and a nacelle attached to it. The tower extends, for example, vertically along its length. The nacelle can be mounted on the tower, for example, so that it can rotate or is fixed in place. The nacelle can be located at the top of the tower, for example. The tower can be hollow, for example. The tower can taper towards its top. The tower can be formed from several stacked tower sections.
[0011] The wind turbine can include a gearbox. The gearbox can include a planetary gear set. The planetary gear set can include a planet carrier and one or more planet gears. With multiple planet gears, one or two of the axial sliding bearings described here can be provided for each planet gear. The wind turbine can include a drive train. The drive train can include a gearbox and a generator. The drive train can also include a rotor. Furthermore, the drive train or the wind turbine can include a rotor shaft. The rotor can drive the generator via the gearbox to produce electrical energy. The rotor can be connected to the gearbox via a rotor shaft. The rotor, gearbox, and generator can be attached to the nacelle of the wind turbine, for example, together by a main bearing. The rotor can have a horizontal or a vertical axis of rotation.The rotor can be found, for example, in ZF Friedrichshafen AG file 304496, Friedrichshafen, 2024-12-19.
[0012] They have two, three, four or more rotor blades, which are connected to the rotor shaft via a hub. The drive train can optionally also include a brake.
[0013] The gearbox can have an input shaft and an output shaft. The gearbox can have a gearbox housing. The generator can have a stator and a rotor. The generator can have a generator housing. The input shaft of the gearbox can be connected to the rotor shaft. The output shaft of the gearbox can be connected to the rotor of the generator.
[0014] The planetary gear set can have three rotating elements. One of these elements can be the planet carrier. The other two elements can be, for example, the sun gear and the ring gear. A planet gear can have teeth on its outer circumference that mesh with other elements of the planetary gear set. For example, the planet gear can mesh with the sun gear and the ring gear. Alternatively, the planet gear can mesh with another planet gear and either the sun gear or the ring gear. The sun gear can have teeth on its outer circumference. The ring gear can have teeth on its inner circumference. The planetary gear set can be configured as a negative planetary gear set or a positive planetary gear set. For example, the planet carrier can form the input shaft. For example, the sun gear can form the output shaft.
[0015] For example, the ring gear may be fixed within the gearbox housing. The gearbox may also have more than one planetary gear set, which transmit power from the input shaft to the output shaft.
[0016] The planet gear has helical teeth. Intermeshing gears, such as those of the sun gear or ring gear, can also be helical. The planetary gear set can be designed as a helical planetary gear set. In helical gears, individual teeth cannot be arranged parallel to an axis of rotation. Instead, the teeth can be inclined longitudinally to a longitudinal axis and, alternatively or additionally, to the axis of rotation. A helical gear can... [ZF Friedrichshafen AG File 304496 Friedrichshafen 2024-12-19]
[0017] An axial force component acts on meshing teeth during operation, causing the planetary gear to tilt. The transmitted power can also cause the planetary gear to tilt. This tilting can occur relative to both a longitudinal axis and the axis of rotation of the planet carrier. For example, the planetary gear can tilt relative to the longitudinal axis of the planetary bolt on which it is mounted. This can cause one end face of the planetary gear to move axially closer to a web of the planet carrier during operation, while a corresponding area of the same end face moves axially away from that web. For instance, one area might be radially outward with respect to the central axis of rotation of the planetary gear set, and the other radially inward with respect to the central axis of rotation of the planetary gear set.
[0018] The planet gear can be milled and, alternatively or additionally, forged. The planet carrier can be made from a single piece or from multiple pieces. The planet carrier can have two axially spaced webs, between which a corresponding planet bolt extends for each planet gear.
[0019] The axial plain bearing has a first end face formed on the planet gear and a second end face formed on the planet carrier. The first end face can be formed, for example, on a flange of the planet carrier or on a separate element, such as a shim. The second end face can be formed by an end face of the planet gear facing the first end face. The two end faces can form the sliding surfaces of the axial plain bearing. The axial plain bearing can be designed as a hydrodynamic plain bearing. The two end faces can face each other. Lubricating oil may be present between the two end faces in the axial direction.
[0020] In contrast, no further component can be positioned between the two end faces. If the second end face of the axial sliding bearing is formed on the cheek, the cheek can be machined there and alternatively or additionally hardened. ZF Friedrichshafen AG File 304496 Friedrichshafen 2024-12-19
[0021] The second end face extends flat in the circumferential direction. The second end face can also be flat in the radial direction. The second end face can be a single, flat surface. The second end face can be a continuous surface or have several spaced-apart sub-surfaces. The axis of rotation of the planetary gear set can correspond to an axis of rotation of the rotating elements. The axis of rotation can extend axially. A longitudinal axis of the planetary pin can be parallel to the axis of rotation of the planetary gear set. The axial direction can be defined by the axis of rotation of the planetary gear set and, alternatively or additionally, by a longitudinal extension of the planetary pin. A radial direction can be defined by the axis of rotation of the planetary gear set, the longitudinal extension of the planetary pin, and, alternatively or additionally, by the axis of rotation of the planetary gear.The circumferential direction can refer to an axis corresponding to the longitudinal extent of the planet bolt or to the axis of rotation of the planet gear.
[0022] In the present design of the axial plain bearing, the planet carrier-side sliding surface is not formed by an inclination, wedge surfaces, or steps in the circumferential direction. Instead, the fact that the planet gear tilts during operation due to the helical gearing is utilized. During operation, the planet gear set tilts, for example, relative to the longitudinal axis of a planet bolt of the planet carrier, on which the planet gear is radially supported. This creates a circumferentially tapered gap in a region of the axial plain bearing, in which a lubricating film forms hydrodynamically and separates the planet gear axially from the planet carrier. In one direction of rotation of the planet gear, the tapered gap can form in the circumferential direction due to the tilt of the planet gear during operation, in which oil accumulates, causing the planet gear to float axially on a lubricating film.This allows for a rapid transition away from the area of solid friction or mixed friction in the axial plain bearing. Accordingly, the complex manufacturing of steps and wedge-shaped surfaces on the planet carrier-side part of the axial plain bearing can be dispensed with. Furthermore, corresponding sliding surfaces are often formed in large areas of the planet carrier. In this case, however, the focus can be concentrated on the area where the first end face, and thus the ZF Friedrichshafen AG File 304496 Friedrichshafen 2024-12-19.
[0023] The end face of the planet gear, which forms the axial plain bearing, is axially closest to the planet carrier. This also allows for cost savings. Thus, a characteristic of helical gearing, which is usually considered a disadvantage, is used here to save costs.
[0024] The second end face, and indeed the entire end face of the planet carrier facing the planetary gear set in the area of the axial bearing, can be free of steps, curves, or uneven surfaces. Here too, manufacturing can be simple, and no complex adjustments are necessary to create the tapered gap during operation.
[0025] During operation, the two end faces can be inclined relative to each other. The first end face can be a flat surface. The entire corresponding end face of the planet gear can be a flat surface. When stationary or when no torque is applied to the transmission, the two end faces can be parallel to each other. However, the planet gear can also remain in an inclined orientation, which is determined by the helical gearing. For example, when stationary or when no torque is applied to the transmission, the two end faces can extend in a plane orthogonal to the axis of rotation of the planet gear set. The first end face can be inclined relative to the axis of rotation of the planet gear set during operation and orthogonal to the axis of rotation when stationary. The second end face can be fixed. The second end face can maintain its orientation both during operation and when stationary.The second end face can be designed to form the tapered gap only in one direction of rotation of the planetary gear set and thus also of the planet gear. The inclination of the planet gear during operation is dependent on the direction of rotation, and a corresponding sliding surface can be provided for only one direction of rotation. However, corresponding sliding surfaces can also be provided for both directions of rotation, resulting in an opposite inclination of the planet gear. For this purpose, the second end face can have two separate sub-surfaces. For example, in one direction of rotation, the second end face can be located on a radially outer area of the planetary gear set facing the end face of the planet carrier and thus also ZF Friedrichshafen AG File 304496 Friedrichshafen 2024-12-19.
[0026] The first end face is axially closest. With a second direction of rotation in the opposite direction, the second end face can be axially closest to the facing end face of the planet carrier, and thus also to the first end face, in a radially inner region of the planetary gear set.
[0027] In one embodiment of the axial sliding bearing, the second end face can be formed by at least one shim of the planet carrier, which is arranged on a flange of the planet carrier. The shim can, for example, be made of a softer material than the flange. The shim can be made of bronze or aluminum, for example. The shim can thus simplify the running-in of the axial sliding bearing. Furthermore, with a shim, the second end face can be manufactured more easily and precisely than, for example, with the flange. The flange can be formed as a single casting. The second end face can also be formed from several shims. These shims can be spaced apart circumferentially and can alternatively or additionally be designed as identical parts.For example, the second end face can be formed from two opposing, circumferentially arranged shims, whereby, depending on the direction of rotation, the tapered gap is only formed in one of the two shims during operation. The cheek can be a wall element of the planet carrier extending orthogonally to the axis of rotation of the planetary gear set. For example, the planet pins can extend axially between two cheeks.
[0028] Alternatively, the second end face can be integrally formed in the cheek of the planet carrier. For this purpose, the planet carrier can be post-processed in the corresponding areas, for example by a machining process.
[0029] In one embodiment of the axial sliding bearing, the second end face can be designed in an annular shape. For example, an annular shim can be provided for this purpose. The second end face can thus be a circumferentially closed and flat ring. In this case, the design can be particularly simple, and a flat area of the second end face is always available. (ZF Friedrichshafen AG File 304496 Friedrichshafen 2024-12-19)
[0030] The formation of the tapered gap must be present during operation, regardless of the direction in which the planetary gear tilts due to the helical gearing.
[0031] The first end face can be annular. For example, an entire end face of the planet gear can form the first end face. The first end face can be flat. If there are also non-flat areas on the corresponding end face of the planet gear that do not form the first end face, these areas may, for example, extend less axially towards the axially adjacent part of the planet carrier than the areas that form the first end face.
[0032] In one embodiment of the axial sliding bearing, the second end face may have at least one ring segment forming a portion of a ring shape. The second end face may also consist of one or two ring segments. For example, the ring segment may extend 60° in the circumferential direction. This allows the second end face to be positioned in the area of a contact surface of the planetary gear during operation due to tilting. In this way, the second end face can be very compact, allowing for compact shims and, alternatively or additionally, a small surface area for post-processing.
[0033] In one embodiment of the axial sliding bearing, it can be provided that the second end face has at least one further ring segment, which is arranged spaced apart in the circumferential direction from the other ring segment.
[0034] For example, the two ring segments can be spaced equally far apart at both ends in the circumferential direction. Depending on the direction of rotation, one of the two ring segments can form the tapered gap with the planet gear due to its tilting during operation. Each ring segment can, for example, be formed from an associated shim. The other ring segment can also form a section of a ring shape. Both ring segments can have an identical shape. Corresponding ring segments can be formed by associated shims, which can be identical parts. ZF Friedrichshafen AG, File 304496, Friedrichshafen, 2024-12-19
[0035] It can also have more than two ring segments or be free of further ring segments.
[0036] In one embodiment of the axial sliding bearing, the second end face can be designed to extend in a plane in the radial direction. This can simplify manufacturing.
[0037] In one embodiment of the axial sliding bearing, the second end face can be designed to extend orthogonally to the axis of rotation of the planetary gear set. This simplifies manufacturing. For example, the second end face can be designed as a flat surface extending in a plane orthogonally to the axis of rotation of the planetary gear set.
[0038] In one embodiment of the axial sliding bearing, the second end face may be inclined to extend perpendicularly to an orthogonal axis of rotation of the planetary gear set. For example, the second end face may extend radially inwards further axially towards the planet gear than radially outwards.
[0039] For example, the second end face can extend further radially outwards and axially towards the planet gear than radially inwards. For example, the second end face can be conical. This allows for a linear contact or gap to be created radially when the planet gear tilts during operation. The second end face can be stepped, curved, or flat in the radial direction. The axial position of the second end face can increase or decrease in a radial direction from the outside inwards, for example, in a stepped, linear, exponential, or other manner.
[0040] A second aspect concerns a gearbox for a wind turbine. The gearbox comprises a planetary gear set with a planet carrier and a planet gear mounted thereon. The planet gear is mounted on the planet carrier by means of the axial sliding bearing as described in the first aspect. The respective advantages and further features can be found in the description of the first aspect, whereby embodiments of the first aspect also include embodiments of the second aspect and vice versa. ZF Friedrichshafen AG File 304496 Friedrichshafen 2024-12-19
[0041] The planet gear is rotatably mounted, for example, on a planetary bolt of the planet carrier. The planet gear is additionally supported on the planet carrier by means of a radial bearing and another axial sliding bearing. The planet gear has helical teeth. The planet gear set can have multiple helical teeth.
[0042] A third aspect concerns a wind turbine with the axial sliding bearing according to the first aspect and, alternatively or additionally, the gearbox according to the second aspect. The respective advantages and further features can be found in the descriptions of the first and second aspects, whereby embodiments of the first and second aspects also constitute embodiments of the third aspect and vice versa.
[0043] Brief description of the characters
[0044] Fig. 1 schematically illustrates a wind turbine with a drive train.
[0045] Fig. 2 schematically illustrates in a first section plane a planetary gear set of a transmission of the drive train, wherein the planetary gear set has axial sliding bearings for respective planet gears.
[0046] Fig. 3 schematically illustrates the planetary gear set in a second section plane, wherein the planetary gear set has a first embodiment of axial sliding bearings.
[0047] Fig. 4 illustrates in a developed radial top view a conventional axial sliding bearing for respective planet gears of the planetary gear set.
[0048] Fig. 5 illustrates in a developed radial top view the axial sliding bearing for the respective planet gears of the planetary gear set according to the respective
[0049] Design features. ZF Friedrichshafen AG File 304496 Friedrichshafen 2024-12-19
[0050] Fig. 6 schematically illustrates the planetary gear set in the second section plane, wherein the planetary gear set has a second embodiment of axial sliding bearings.
[0051] Detailed description of embodiments
[0052] Fig. 1 illustrates a wind turbine 10 with a horizontal drive train. The wind turbine 10 has a rotor 12, which is held on a rotor shaft 16 via a hub 14. The axis of rotation of the rotor shaft 16 extends essentially horizontally. The rotor shaft 16 is supported in a nacelle 20 by two rolling bearings 18, 38. A rotor bearing housing 40 is provided for this purpose, which is attached to a machine bed 42 of the nacelle 20. The rotor shaft 16 is mechanically connected to a generator 24 via a gearbox 22. A brake 26 is also arranged in the operative connection between the gearbox 22 and the generator 24, which acts on an input shaft of the generator 24. The nacelle 20 is rotatably mounted at the upper end of a tower 28, which is anchored to the ground. In another embodiment, the wind turbine 10 is designed as an offshore installation. In addition to tower 28, wind turbine 10 has a grid connection 30.The first of the rolling bearings 18 faces the rotor 12 and is also referred to as the rotor-side bearing 18. The second of the rolling bearings 38 faces the generator 24 and is also referred to as the generator-side bearing 38. Both rolling bearings 18 and 38 are designed as tapered roller bearings. At least the rotor bearing housing 40, the rotor 12, the rotor shaft 16, the gearbox 22, and the generator 24 form components of the drive train of the wind turbine 10.
[0053] Figure 2 illustrates a planetary gear set 60 of the transmission 22, by means of which a rotational speed and a torque applied to the rotor 12 are translated for the generator 24. The section plane of Figure 2 extends radially and has a central axis of rotation of the planetary gear set 60. The planetary gear set 60 comprises a sun gear 62, a planet carrier 64, and a ring gear 66 as rotating elements. The planet carrier 64 has a first web 68, which extends radially and is permanently fixed to the rotor shaft 16. ZF Friedrichshafen AG File 304496 Friedrichshafen 2024-12-19
[0054] The planet carrier 64 thus forms an input shaft for the gearbox 22 and is connected to the rotor shaft 16. Axially spaced from the first web 68, the planet carrier 64 has a second web 70, which also extends radially. Planet bolts 72 extend axially between the webs 68 and 70, two of which are shown in Fig. 2. A plurality of planet gears 74 are rotatably mounted on the planet carrier 64, here on associated planet bolts 72 of the planet carrier 64. The ring gear 66 is fixed to a gearbox housing. The sun gear 62 forms an output shaft for the gearbox 22 and is connected to a rotor of the generator 24. The planet gears 74 mesh with the ring gear 66 and the sun gear 62. The central axis of rotation of the planet gear set 60 corresponds here to an axis of rotation of the sun gear 62, the planet carrier 64 and also to an axis of rotation of the ring gear 66, provided that the latter is not fixed.The respective axes of rotation of the planet gears 74 are radially offset and essentially correspond to the arrangement of the planet bolts 72.
[0055] Additionally, the gearbox 22 has a radially extending stationary component 76. Lubricating oil is guided via the stationary component 76 and an oil guide ring 78 into an oil line 80 in each planetary pin 72. The oil line 80 supplies lubricating oil to a radial bearing, by which the planet gears 74 are mounted on the respective planetary pin 72. The radial bearings are designed as plain bearings. Accordingly, there is a radial gap between an outer circumferential surface of the respective planetary pin 72 and the associated planetary gear 74.
[0056] The respective meshing teeth of the planet gears 74, the ring gear 66, and the sun gear 62 are designed as helical gears. During operation, the planet gears 74 tilt in accordance with the direction of rotation of the rotor 12. Fig. 2 shows an operating condition in which the planet gears 74 are tilted radially outwards with respect to the central axis of rotation of the planet gear set 60 in the direction of the rotor 12, and radially inwards with respect to the central axis of rotation of the planet gear set 60 in the direction of the generator 24. Accordingly, during operation, with a certain direction of rotation of the rotor 12, a radially outer region of the planet gears 74 is axially tilted. ZF Friedrichshafen AG File 304496 Friedrichshafen 2024-12-19
[0057] closer to the first web 68 and a radially inner area of the planet gears 74 axially closer to the second web 70. With a reverse direction of rotation of the rotor 12, the inclination is also reversed.
[0058] Between the first web 68 and the respective planet gear 74, a first axial sliding bearing 90 is provided for each planet gear 74. Between the second web 70 and the respective planet gear 74, a second axial sliding bearing 92 is provided for each planet gear 74.
[0059] Each axial plain bearing 90, 92 has a first end face 96 formed on the respective planet gear 74. In this case, the first end faces 96 of the first axial plain bearing 90 are each formed by an end face of each planet gear 74 facing the first web 68. Similarly, the first end faces 96 of the second axial plain bearing 92 are each formed by an end face of each planet gear 74 facing the second web 70. These end faces, and thus also the first end faces 96, are annular in shape.
[0060] Each axial sliding bearing 90, 92 has a second end face 98 formed on the planet carrier 64. In the present embodiment, the second end faces 98 of the first axial sliding bearing 90 are each formed by a first shim 100 arranged on the first web 68 and axially adjacent to the planet gear 74. Similarly, the second end faces 98 of the second axial sliding bearing 92 are each formed by a second shim 102 arranged on the second web 70 and axially adjacent to the planet gear 74. In other embodiments, the second end faces 98 are formed integrally on the webs 68, 70.
[0061] The first end faces 96 are designed as planar surfaces. In operation, the first end faces 96 do not extend orthogonally to the axis of rotation of the planet gear set 60 and a longitudinal axis of the planet pins 72, since the planet gears 74 are inclined due to the helical gearing. The second end faces 98 are designed as planar surfaces and always extend orthogonally to the axis of rotation of the planet gear set 60 and the longitudinal axis of the planet pins 72. The first end faces 96 and the second end faces 98 each ZF Friedrichshafen AG File 304496 Friedrichshafen 2024-12-19
[0062] The axial sliding bearings 90, 92 are therefore not aligned parallel to each other during the operation of the wind turbine 10.
[0063] Figure 4 shows the first and second end faces 200, 202 of a conventional axial sliding bearing 204 in radial view from the outside and in unwound form. The first end face 200 is again formed by a planet gear 206. The second end face 202 is also formed by a shim 208 on a web. In the design of this conventional axial sliding bearing 204, it was assumed that the planet gear 206 would not tilt. To promote the formation of a lubricating film and separation of the two end faces 200, 202 during operation, the second end face 202 has shoulders 210 in the shim 208. Alternatively or additionally, the second end face 202 has inclined areas 212. This causes the gap between the two end faces 200, 202 to narrow in the circumferential direction in the direction of rotation of the planet gear 206 in certain areas. The direction of rotation is illustrated by arrow 214 in Fig. 4.By rotating the planetary gear 206, lubricating oil is pumped through the narrowing gap, resulting in a pressure increase.
[0064] Fig. 5, in contrast, illustrates in a radially external and unwound view how the present embodiments of the axial sliding bearings 90, 92 utilize the tilting of the planet gears 74 during operation. Due to the tilt, a tapered gap also results in an area between the two end faces 96, 98. This tapering is independent of the direction of rotation of the planet gears 74, which is illustrated in Fig. 5 for normal operation of the wind turbine 10 by arrow 104. The second end faces 98 can be manufactured cost-effectively as flat surfaces. The axis of rotation of the planet gears 74 in Figs. 4 and 5 extends from top to bottom in the plane of the image.
[0065] Fig. 3 shows a first embodiment in a radial section plane extending orthogonally to the central axis of rotation of the planetary gear set 60. As can be seen, the shims 100, 102 are ring-shaped and ZF Friedrichshafen AG File 304496 Friedrichshafen 2024-12-19
[0066] They extend circumferentially around the respective associated planetary bolt 72. Manufacturing and assembly are therefore very simple.
[0067] Fig. 6 shows a second embodiment in the radial section plane, which extends orthogonally to the central axis of rotation of the planetary gear set 60. As can be seen, two shims 120 are provided for each of the two axial sliding bearings 90, 92, which extend only over a partial area in the circumferential direction. The shims 120 are arranged only in the area where the planetary gear 74 axially approaches the webs 68, 70, thus forming the tapered gap. The shims 120 therefore form only a division in the form of a ring segment and are spaced apart from each other in the circumferential direction. The second end faces 98 thus also have partial surfaces spaced apart from each other in the circumferential direction. The shims 120 are arranged in one plane.The partial surfaces of the second end faces 98 are also planar and extend in the same plane, which extends orthogonally to the central axis of rotation of the planetary gear set 60.
[0068] In a further embodiment, only one of the shims 120 is used per axial sliding bearing 90, 92, provided that the planet gears 74 always rotate in the same direction during operation and thus always tilt in the same direction. This is typically the case with wind turbines. For example, the rotor 12 of the wind turbine 10 can always rotate in such a direction that the tilt of the planet gears 74 illustrated in Fig. 2 results. In the first axial sliding bearing 90, only the shim 120 arranged radially outward with respect to the central axis of rotation of the planet gear set 60 is provided, since the planet gears 74 approach each other radially outward at the first web 68 due to tilting.In the second axial sliding bearing 92, only the shim 120, arranged radially inwards with respect to the central axis of rotation of the planetary gear set 60, is provided, since the planet gears 74 approach each other radially inwards when tilting on the second web 70. ZF Friedrichshafen AG File 304496.
[0069] Friedrichshafen 2024-12-19
[0070] Reference sign
[0071] 10 wind turbines
[0072] 12 Rotor
[0073] 14 hub
[0074] 16 Rotor shaft
[0075] 18, 38 rolling bearings
[0076] 20 gondolas
[0077] 22 gearboxes
[0078] 24 Generator
[0079] 26 brake
[0080] 28 Tower
[0081] 30 network connection
[0082] 40 rotor bearing housings
[0083] 42 machine bed
[0084] 60 planetary gear set
[0085] 62 Sun wheel
[0086] 64 planetary carriers
[0087] 66 Ring gear
[0088] 68 first cheek
[0089] 70 second cheek
[0090] 72 planetary bolts
[0091] 74, 206 planetary gear
[0092] 76 stationary component
[0093] 78 Oil guide ring
[0094] 80 Oil line
[0095] 90 first axial plain bearing 92 second axial plain bearing 96, 200 first end face
[0096] 98, 202 second front face
[0097] 100 first support element 102 second support element 104, 214 arrow
[0098] 120, 208 Underlay element ZF Friedrichshafen AG File 304496
[0099] Friedrichshafen 2024-12-19
[0100] 204 conventional axial plain bearings 210 paragraphs
[0101] 212 areas
Claims
ZF Friedrichshafen AG File 304496 Friedrichshafen 2024-12-19 Patent claims 1. Axial plain bearing (90, 92) for supporting a planet gear (74) on a planet carrier (64) of a planet gear set (60) of a gearbox (22) of a wind turbine (10), wherein the planet gear (74) has helical teeth, wherein the axial plain bearing (90, 92) has a first end face (96) formed on the planet gear (74) and a second end face (98) formed on the planet carrier (64), wherein the second end face (98) extends in a plane in the circumferential direction.
2. Axial sliding bearing (90, 92) according to claim 1 , characterized in that the second end face (98) is formed at least by a support element (100, 102, 120) of the planet carrier (64) which is arranged on a cheek (68, 70) of the planet carrier (64).
3. Axial sliding bearing (90, 92) according to claim 1 or 2, characterized in that the second end face (98) is ring-shaped.
4. Axial sliding bearing (90, 92) according to claim 3, characterized in that the second end face (98) has at least one ring segment which forms a part of a ring shape.
5. Axial sliding bearing (90, 92) according to claim 4, characterized in that the second end face (98) has at least one further ring segment which is arranged spaced apart in the circumferential direction from the other ring segment.
6. Axial sliding bearing (90, 92) according to one of the preceding claims, characterized in that the second end face (98) extends in the radial direction in a plane and orthogonal to the axis of rotation of the planetary gear set (60).
7. Axial plain bearing (90, 92) according to one of the preceding claims, characterized in that the second end face (98) extends in the radial direction in a plane and inclined to an orthogonal of the axis of rotation of the planetary gear set (60). ZF Friedrichshafen AG File 304496 Friedrichshafen 2024-12-19 8. Gearbox (22) for a wind turbine (10), wherein the gearbox (22) comprises a planet gear set (60) with a planet carrier (64) and a planet gear (74) mounted thereon by means of an axial sliding bearing (90, 92) according to one of the preceding claims.
9. Wind turbine (10) with a gearbox (22) according to claim 8 or an axial sliding bearing (90, 92) according to one of claims 1 to 7.