PLANETARY CARRIER ASSEMBLY, PLANETARY GEARBOX, DRIVETRAIN, WIND TURBINE

Description

[0001] The invention relates to a planetary carrier arrangement that can be used in a planetary gear set, and to such a planetary gear set. The invention also relates to a drive train that includes such a planetary gear set.

[0002] The invention also relates to a wind turbine that has such a drive train.

[0003] US Patent 8,636,615 B2 discloses a planetary gearbox for a wind turbine, comprising an input-side planetary stage with a planet carrier. The planet carrier is rotatably mounted on both sides in a planet carrier bearing and is provided with a lubricant applicator on a generator-side hub. The lubricant applicator is positioned immediately adjacent to the generator-side planet carrier bearing. Sealing rings are arranged on the outer surface of the lubricant applicator, which interact with a lubricant dispensing mechanism.

[0004] From publication EP 1 488 139 B1, a planet carrier in a wind turbine gearbox is known, which is supplied with oil via a housing wall. In the area of ​​one cheek of the planet carrier, oil is transferred from the housing wall into the planet carrier via a ring with a U-profile attached there.

[0005] Document WO 2020 / 001942 A1 discloses a planetary gearbox suitable for a wind turbine, comprising three planetary stages. These planetary stages may contain five or more planet gears.

[0006] From EP 3 056 763 A1 a planetary carrier arrangement with a lubricant dispensing unit for dispensing lubricant into a planetary carrier is known, wherein the lubricant dispensing unit has a rubber-elastic pressure ring.

[0007] Planetary gearboxes are used in a wide variety of applications where increasing rated power and torque must be transmitted. This requires lubrication systems that function reliably even under operating conditions with high torques. This is particularly true for the lubrication of planetary carriers. At the same time, there is a desire for maintenance-friendly planetary gearboxes that are cost-effective to manufacture. The invention is based on the objective of providing a planetary carrier arrangement that offers an improvement in at least one of the described aspects.

[0008] The problem is solved by a planetary carrier arrangement having the features of claim 1. Preferred embodiments are specified in the dependent claims and the following description, each of which, individually or in combination, can represent an aspect of the invention. When a feature is presented in combination with another feature, this serves only to simplify the presentation of the invention and is in no way intended to imply that this feature cannot also be a further development of the invention without the other feature.

[0009] The planet carrier arrangement comprises a lubricant dispensing unit for dispensing lubricant into a planet carrier, wherein the lubricant dispensing unit has an axially elastically movable pressure ring to compensate for an axial offset of the planet carrier, wherein at least one lubricant pocket is formed on a side of the axially elastically movable pressure ring facing the planet carrier, which serves as a buffer during the transfer of the lubricant (45).

[0010] The planet carrier can be rotatably mounted in a housing. The lubricant delivery unit is designed to deliver a lubricant, such as oil, to the planet carrier and can be connected to the housing for this purpose. Alternatively, the lubricant delivery unit can be connected to the planet carrier. The lubricant can be conveyed within the planet carrier to supply lubricant to other components that are connected to or interact with the planet carrier. Such components are also referred to as consumers in a lubrication system. The lubricant delivery unit includes the axially elastically movable pressure ring, which will be referred to simply as the pressure ring in the following. Axial elasticity means that the pressure ring returns to its initial position due to a restoring force generated by moving the pressure ring along an axial direction.The axially elastically movable pressure ring is designed to compensate for axial misalignment of the planet carrier. This axial misalignment can be caused by operating loads and / or tolerance variations. By compensating for this axial misalignment, lubricant loss between the axially elastically movable pressure ring and the planet carrier is minimized or prevented. The planet carrier arrangement according to the invention is suitable for use in planetary gearboxes that permit axial misalignment of the planet carrier while simultaneously requiring minimal lubricant loss. Furthermore, the planet carrier arrangement according to the invention also allows for radial misalignment and / or tilting of the planet carrier.The axially elastically movable pressure ring allows for increased tolerances in the axial direction during manufacturing of the planet carrier and the lubricant delivery unit without impairing the sealing effect between them. This, in turn, enables cost-effective manufacturing of the planet carrier arrangement according to the invention.

[0011] Furthermore, at least one lubricant pocket is formed on the axially elastically movable pressure ring on a side facing the planet carrier. This lubricant pocket can be located in the end region of a lubricant channel. This ensures a reliable and continuous lubricant supply to the planet carrier, similar to the lubrication pocket in a sliding bearing disc. The axially elastically movable pressure ring offers sufficient space on its end face to form multiple lubricant pockets. These pockets can be produced by simple machining, such as milling. The advantages of the planet carrier assembly can thus be realized to an even greater extent. Alternatively or additionally, such lubricant pockets can also be formed on the sealing ring and / or the planet carrier.Multiple lubricant pockets can be interconnected, i.e., merge seamlessly, on the pressure ring, sealing ring, or planetary carrier. These lubricant pockets are typically located within a common radius. The multiple lubricant pockets are spaced circumferentially, meaning that between two circumferentially consecutive lubricant pockets, a portion of the pressure ring or sealing ring remains unmachined to form the lubricant pockets. In contrast to a completely closed lubrication groove, a mass flow from a lubricant dispensing opening to a substantially opposite opening can be precisely defined, thus preventing bypass flow to an opening offset in the circumferential direction.This makes it easier to connect different consumers via the lubricant pocket with different lubricant dispensing openings and to ensure an adequate supply of lubricant.

[0012] In one embodiment of the claimed planetary carrier arrangement, the lubricant dispensing unit comprises a stator that is rigidly connected to the housing and through which the lubricant is guided. The stator is understood to be a stationary and non-rotating part of the lubricant dispensing unit, which is particularly multi-part. The lubricant dispensing unit may also have a rotating part referred to as a rotor. At least one spring element may be arranged between the axially elastically movable pressure ring and the stator, which imparts its axially elastic mobility to the pressure ring. Any component that offers technically usable elasticity and restoring force can serve as the spring element. Alternatively or additionally, the spring element may also be a lubricant-filled hydraulic device that utilizes existing lubricant pressure for spring action and / or damping.Spring elements provide sufficient restoring force over an extended service life, ensuring consistently reliable operation. Spring elements are readily available in a wide variety of sizes and spring rates, allowing for precise adjustment of the restoring force. In a further embodiment, multiple spring elements can be arranged between the axially elastically movable pressure ring and the stator. This allows the claimed planetary carrier arrangement to be scaled to different sizes where increased restoring forces on the axially elastically movable pressure ring are required. The spring elements can also be spaced apart along a circumferential direction of the stator, particularly with uniform spacing, thus ensuring continuous contact between the axially elastic pressure ring and the planetary carrier. In particular, spring elements can compensate for tilting of the pressure ring.

[0013] Furthermore, a sealing ring can be arranged on the planet carrier, designed to receive lubricant from the axially elastically movable pressure ring. For this purpose, the sealing ring can be positioned between the planet carrier and the axially elastically movable pressure ring. The sealing ring creates a contact area between the planet carrier and the axially elastically movable pressure ring, allowing for radial misalignment and / or tilting between them. The sealing ring can be easily designed to ensure reliable lubricant transport into the planet carrier, even with increased radial misalignment. The sealing ring can be made of a material that exhibits favorable wear properties in contact with the axially elastically movable pressure ring, for example, a sliding material, particularly a copper alloy, or a plastic.The choice of material for the axially elastically movable pressure ring, the sealing ring, the stator, and / or the planet carrier is therefore largely unrestricted. Consequently, particularly suitable materials can be selected for these components, resulting in increased service life and reliability for the stressed planet carrier assembly. Furthermore, only the surfaces on the axially elastically movable pressure ring and the sealing ring require precise machining to ensure sufficient sealing and / or sliding action. Compared to the housing or the planet carrier, the axially elastically movable pressure ring and the sealing ring are relatively small and lightweight components, making them significantly easier to handle. This reduces the manufacturing effort for the stressed planet carrier assembly. The sealing ring can be rotationally fixed to the planet carrier or rest loosely against it.

[0014] In a further embodiment of the claimed planetary carrier arrangement, the lubricant dispensing unit can comprise at least one fastening means by which the axially elastic movable pressure ring is secured against rotation relative to the stator. The fastening means can, for example, be designed as a screw or bolt that blocks rotation of the axially elastic movable pressure ring. The fastening means can be positioned circumferentially adjacent to an axial lubricant channel in the axially movable pressure ring or between such channels. Similarly, the fastening means can also be arranged circumferentially adjacent to a spring element or between such channels. The claimed planetary carrier arrangement allows for the minimization or prevention of rotation of the axially elastic movable pressure ring, even against increased forces, by using a plurality of fastening means.Alternatively, the fastening device can be designed to allow rotation of the axially elastic movable pressure ring and only to limit its movement in the axial direction.

[0015] Furthermore, at least one sealing element can be arranged between a radial outer surface of the axially elastically movable pressure ring and the stator. The sealing element can, for example, be designed as an elastomer ring, in particular as an O-ring. The sealing element minimizes or prevents lubricant loss between the stator and the axially elastically movable pressure ring. Due to its positioning on the radial outer surface, the sealing element is suitable for reliably producing a sealing effect even when the pressure ring moves along the axial direction. In a further embodiment of the claimed planetary carrier arrangement, at least two axially spaced sealing elements can also be arranged on the radial outer surface of the axially elastically movable pressure ring.A dispensing opening can be formed between the at least two sealing elements, through which lubricant can be conveyed from the stator into the axially elastically movable pressure ring. Similarly, the at least one sealing element can also be arranged on a radial inner surface of a stator of the lubricant dispensing unit. This provides an essentially equivalent alternative. Combinations of these are also possible. Furthermore, O-rings also allow for radial misalignment and / or tilting of the planet carrier.

[0016] Furthermore, the planet carrier of the claimed planet carrier arrangement can be mounted in the housing without bearings on at least one of its sides. The claimed planet carrier arrangement allows for compensation of axial misalignments of the planet carrier due to the axially elastic movement of the pressure ring. The contact between the axially elastically movable pressure ring and the planet carrier allows for compensation of radial misalignments between them. Accordingly, bearings, such as rolling bearings or plain bearings, that fix the planet carrier in the housing on the side facing the lubricant dispensing unit are unnecessary. This makes it possible to accommodate an increased number of planet gears in the planet carrier, in particular five or more, which are mounted on plain bearings and require a continuous and adequate supply of lubricant. In such planet carriers, a self-adjusting load distribution between the planet gears is achievable.This, in turn, allows for improved material utilization in the claimed planetary carrier arrangement. Preferably, the planetary carrier of the claimed planetary carrier arrangement is also mounted without bearings in the housing on one side facing away from the lubricant dispensing unit. This results in a greater degree of the outlined advantages, in particular increased cost efficiency and ease of maintenance.

[0017] In a further embodiment of the claimed planetary carrier arrangement, the axially elastically movable pressure ring can be arranged opposite a hub of the planetary carrier. In particular, the axially elastically movable pressure ring can be supported axially against an end face of the hub, either directly or via a sealing ring. This ensures that the axially elastically movable pressure ring reliably bears against the planetary carrier due to the installation situation, thereby creating a continuous sealing effect during operation. The hub of the planetary carrier can represent the area of ​​the planetary carrier with the smallest diameter. The axially elastically movable pressure ring can thus be designed with a reduced diameter. This also increases the reliability of the sealing effect between the axially elastically movable pressure ring and the planetary carrier or the sealing ring.The hub, opposite which the axially elastically movable pressure ring is located, can be a hub on a generator side, i.e., an output side, of the planet carrier. This allows for shorter lengths of external oil lines on the planetary gear. If the planet carrier is mounted without bearings in the housing, at least on the side facing the lubricant delivery unit, the hub on this side can be shortened in the axial direction. This results in additional weight and space savings in the axial direction.

[0018] Similarly, in the claimed planet carrier arrangement, the axially elastically movable pressure ring can have a clear inner diameter of at least 150 mm. This also results in a corresponding clear inner diameter of the planet carrier in the area of ​​the axially elastically movable pressure ring, particularly at its hub on the side facing the lubricant delivery unit, of at least 130 mm. Due to such a clear inner diameter, the planet carrier is suitable for accommodating sun gears and / or sun shafts with increased outer diameters. This, in turn, allows the use of an increased number of planet gears in the planet carrier. The more planet gears are arranged in the planet carrier, the higher their lubricant requirement and the more important a reliable lubricant supply becomes. Overall, the claimed planet carrier arrangement allows the design of particularly advantageous planetary stages in planetary gearboxes.

[0019] Furthermore, in the claimed planetary carrier assembly, the spring element can be designed as a helical spring, disc spring, ring spring, volute spring, or elastomer body. Helical springs are readily available in a wide range of sizes and spring rates. Disc springs can be precisely combined into disc spring assemblies with virtually any desired spring characteristics by suitable stacking. Additionally, disc springs are compact. Due to their high spring rate, ring springs can also be used in compact designs in the claimed planetary carrier assembly. This applies analogously to a volute spring. Elastomer bodies offer a high degree of cost-effectiveness, making them readily suitable as wear parts in the claimed planetary carrier assembly. The elastomer body can also be manufactured using additive manufacturing, for example, 3D printing. This allows for a high degree of customization.When using multiple spring elements in the claimed planetary carrier arrangement, combinations of several embodiments of spring elements are also possible. The underlying problem is also solved by a planetary gear according to the invention, which has at least one planetary stage. The planetary stage has at least one planetary carrier arrangement, which is arranged in a housing of the planetary gear. According to the invention, the planetary carrier arrangement is designed according to one of the embodiments sketched above. The technical advantages of the planetary carrier arrangement are thus transferred to a planetary gear.

[0020] In one embodiment of the claimed planetary gear, the planetary gear has at least three planetary stages. The three planetary stages can be arranged in series. Such planetary stages are described in more detail in publication WO 2020 / 001942 A1.

[0021] Furthermore, a planet carrier assembly can be arranged in the claimed planetary gear system, in which at least three planet gears are arranged. In particular, five or more planet gears can also be arranged in the planet carrier assembly. The higher the number of planet gears in a planetary stage, i.e., a planet carrier, the more demanding it is to ensure a reliable and uniform supply of lubricant. The planet carrier assembly according to the invention provides a particularly suitable solution for this. In particular, seven, eight, or nine planet gears can also be arranged in the planet carrier. This allows for a more even load distribution across multiple power branches, which in turn enables the construction of more powerful and simultaneously more compact planetary gear systems.

[0022] The problem described above is also solved by a drive train according to the invention. The drive train is designed for use in a wind turbine and includes a gearbox. The gearbox can be connected to a rotor shaft for torque transmission, through which the rotary motion of a multi-blade rotor is transmitted. The drive train also includes a generator, which is connected to the gearbox for torque transmission. According to the invention, the gearbox is designed as a planetary gearbox according to one of the embodiments described above. The technical advantages of the invention outlined above are thereby transferred to an entire drive train, which offers increased performance overall, particularly electricity generation capacity, while simultaneously exhibiting increased reliability and service life. The drive train according to the invention is therefore suitable, for example, for use in offshore wind turbines.Furthermore, the gearbox and generator can be housed in a single unit, thus forming a gearbox generator. Such arrangements are also known as hybrid drives.

[0023] The problem described at the outset is similarly solved by a wind turbine according to the invention. The wind turbine comprises a nacelle to which a multi-bladed rotor is rotatably attached and which is connected to a drive train for torque transmission. According to the invention, the drive train is designed according to one of the embodiments described above.

[0024] The task is also solved by an unclaimed computer program designed to simulate the operating behavior of a planetary carrier assembly. This computer program can include a physics model in which the planetary carrier assembly is at least partially represented. The computer program can also have a data interface through which operating conditions can be specified, such as rotational speed, movement of a planetary carrier, applied forces, offsets and / or tilts, lubricant supply flow rate, and specifications of a lubricant or its thermal, rheological, or similar properties. Material properties of components, such as their modulus of elasticity, stiffness, or surface finish, can also be specified via the data interface. Measurement data from sensors can also be input into the physics model via the data interface.Simulating operational behavior can include determining lubricant loss in the planetary carrier assembly resulting from a given operating situation. Furthermore, the computer program can have a data interface for outputting simulation results to a user and / or other simulation-oriented computer programs. The computer program can be designed as a so-called digital twin, which can model the operational behavior of the planetary carrier assembly. Digital twins are described in more detail in US 2017 / 286572 A1, among other sources. The computer program can be monolithic, meaning it can be executed entirely on a single hardware platform. Alternatively, the computer program can be modular and comprise multiple subprograms that can be executed on separate hardware platforms and interact via a communicative data connection.Such a communicative data connection can be a network connection or an internet connection. In particular, the computer program product can be designed to be executable in a computer cloud. Furthermore, by way of an example not covered by the scope of the attached claims, a planetary carrier assembly can be tested and / or optimized by simulation using the computer program product. Additionally, measurement data from sensors on a planetary carrier assembly and / or the associated planetary gear can be checked for plausibility using the computer program product. This allows, for example, the detection of a defective sensor in the planetary carrier assembly and / or the corresponding planetary gear. Alternatively or additionally, the computer program product can also be used to detect a defective component in the planetary carrier assembly and / or the planetary gear.To detect the defective sensor and / or component, the computer program product may also have so-called artificial intelligence, for example a self-learning algorithm.

[0025] In particular, the computer program product features a data agglomerate with data packages, either combined in a single file or distributed across various files, for representing the three-dimensional shape and / or the interactions of all components provided in the planetary support arrangement. These data packages are configured to enable a simulation of the planetary support arrangement's functionality when the computer program product is processed by a data processing unit. This allows for computer-based simulation to study the planetary support arrangement's functionality, identify problems in specific applications, and find improvements.

[0026] The invention is explained in more detail below with reference to individual embodiments shown in the figures. The figures are to be read as complementary to one another, such that identical reference numerals in different figures have the same technical meaning. The features of the individual embodiments can also be combined with one another. Furthermore, the embodiments shown in the figures can be combined with the features outlined above. Specifically, the figures show: FIG 1 schematically shows a first embodiment of the claimed planetary support arrangement in a longitudinal section; FIG 2 the first embodiment in a further longitudinal section; FIG 3 the first embodiment in yet another longitudinal section; FIG 4 schematically shows an oblique view of an embodiment of an axially elastically movable pressure ring; FIG 5 schematically shows the structure of an embodiment of the claimed wind turbine in a sectional oblique view.

[0027] In FIG 1 The diagram schematically depicts the structure of a first embodiment of the claimed planetary carrier arrangement 30, which is arranged in a housing 23 of a planetary gearbox 20. The planetary carrier arrangement 30 is arranged in a first planetary stage 11, which is located on a rotor side 27 of the planetary gearbox 20. A second planetary stage 21 is positioned further towards a generator side 29 of the planetary gearbox 20, which interacts with the first planetary stage 11. The planetary carrier arrangement 30 comprises a planetary carrier 10, which is rotatable about a main axis of rotation 15. A plurality of planet gear pins 12 are received in the planetary carrier 10, on which planet gears 14 are rotatable via sliding bearings 13. A torque 25 can be transmitted to the planetary carrier 10 via a rotor shaft 62 (not shown in detail), by which a generator 64 (not shown in detail) can be driven via the planetary gearbox 20.The planetary carrier assembly 30 also includes a lubricant dispensing unit 40, which is connected to a housing 23 of the planetary gear unit 20. The lubricant dispensing unit 40 comprises a stator 41, which is connected to a wall 26 of the housing 23 and remains stationary during operation. Through channels (not shown) in the wall 26 of the housing 23, a lubricant 45 is conveyed to the stator 41, which is then directed to the planetary carrier 10.

[0028] The lubricant dispensing unit 40 also includes an axially elastically movable pressure ring 42, which is arranged in a radially inner region of the stator 41. A radially inner and radially outer direction are defined in FIG 1 The main axis of rotation 15 is referenced and symbolized by arrows 33 and 35. At least one spring element 44 is arranged between the axially elastically movable pressure ring 42 and the stator 41, by which a restoring force 36 is exerted on the axially elastically movable pressure ring 42. Sealing elements 22 are arranged on a radial outer surface 47 of the axially elastically movable pressure ring 41, which are arranged axially adjacent to a supply groove 46 in the region of the stator 41. During operation of the planet carrier assembly 30, lubricant 45 can be directed from the stator 41 into the supply groove 46. From there, the lubricant 45 can be directed into the axially elastically movable pressure ring 42. Through this, the lubricant 45 can be directed substantially in the axial direction 31 via at least one lubricant discharge opening 54 into a sealing ring 18 and the planet carrier 10.

[0029] The axially elastically movable pressure ring 42 presses the planet carrier 41 against the sealing ring 18, which is rotatably mounted on the planet carrier 10. The sealing ring 18 is made of a sliding material, in particular a copper alloy, and forms a sliding sealing surface 28 with an end face 24 facing the stator 41 and an end face 48 facing away from the stator 41 on the axially elastically movable pressure ring 42. The sliding sealing surface 28 is circumferential and allows the planet carrier 10 a radial displacement 37 without impairing the sealing effect between the sealing ring 18 and the axially elastically movable pressure ring 42. Because the pressure ring 42 is elastically movable in the axial direction 31, it is capable of following an axial displacement 39 of the planet carrier 10 during operation and thus compensating for the axial displacement 39.Accordingly, even with an increased axial offset 39 of the planet carrier 10, a reliable lubrication supply to the plain bearings 13 is ensured. The planet carrier 10 can be received in the housing 22 without bearings, at least on the side facing the lubricant dispensing unit 40, in particular at the hub 19 there. In the second planetary stage 21, however, such a bearing 32 is provided, which is unnecessary for the planet carrier 10 of the claimed planetary carrier arrangement 30. The planet carrier 10 has a clear inner diameter 34 of at least 130 mm. Correspondingly, the axially elastically movable pressure ring 42 has a clear inner diameter 43 of at least 150 mm. This allows the sun gear 16 and / or the sun shaft 17, which connects the first planetary stage 11 with the second planetary stage 21, to be designed with correspondingly increased outer diameters.The planet carrier 10 is capable of aligning itself through forces and torques present during operation, thereby automatically achieving a uniform load distribution on the planet gears 14. This allows at least three planet gears 14 to be reliably operated within the planet carrier 10. The planet carrier arrangement 30 is depicted in an unclaimed computer program 80, which is designed to simulate the operating behavior of the planet carrier arrangement 30.

[0030] FIG 2 Figure 1 shows the first embodiment of the claimed planet carrier arrangement 30 in a different section plane in longitudinal section. At least one recess 49 is formed in the axially elastically movable pressure ring 42, in which the at least one spring element 44 is at least partially received. The spring element 44 is designed as a helical spring, which exerts the restoring force 36 on the axially elastically movable pressure ring 42, by which the axially elastically movable pressure ring 42 is pressed against the sealing ring 18. Almost the entire axial width 38 of the axially elastically movable pressure ring 42 is available for the recess 49. The deeper the recess 49 is formed in the axial direction 31, the more precisely the spring element 44 can be guided. The planet gear arrangement 30 according to Figure 1 FIG 2 This allows the use of larger spring elements 44, which are readily available as standardized components. Consequently, the use of compact and simultaneously particularly stiff or resilient spring elements 44 is unnecessary.

[0031] A further longitudinal section through the first embodiment of the claimed planetary carrier arrangement 30 according to FIG 1 and FIG 2 is in FIG 3 The axially elastically movable pressure ring 42 has at least one retaining opening 51 in which a fastening element 52, designed as a bolt, is received. The fastening element 52 holds the axially elastically movable pressure ring 42 on the stator 41 and limits its axial movement in the direction of the restoring force 36 exerted by the at least one spring element 44. The fastening element 52 limits rotation of the axially elastically movable pressure ring 42 in the circumferential direction. The circumferential direction is to be understood with respect to the main axis of rotation 15. This ensures that lubricant 45 can always flow into the planet carrier 10. The embodiment according to FIG 3 It can be pre-assembled, thus avoiding a blind assembly process during final assembly.

[0032] FIG 4 Figure 1 shows an oblique view of an embodiment of an axially elastically movable pressure ring 42, which can be used in different embodiments of the claimed planetary carrier arrangement 30. A circumferential supply groove 46 is formed radially on the outside of the pressure ring 42, through which lubricant 45 can be supplied from a stator 41 (not shown in detail). The supply groove 46 is hydraulically connected to a plurality of lubricant dispensing openings 54, which open onto an end face 48 on a rotor side 27 that, in the assembled state, faces a sealing ring 18 or a planetary carrier 19. The lubricant dispensing openings 54 are regularly spaced in the circumferential direction 55 on the end face 48. Furthermore, a lubricant pocket 56 is formed on the end face 48 in the region of each lubricant dispensing opening 54, which serves as a buffer during the transfer of the lubricant 45.This ensures a uniform and reliable supply of lubricant to the planet carrier 10. A retaining opening 51 is formed between each of the lubricant pockets 56, in which a fastening element 52 can be received. The fastening elements 52 secure the pressure ring 42 against rotation along the circumferential direction 55 during operation. Furthermore, spring elements 44 can be inserted into the pressure ring 42 on one side opposite the end face 48, which are located in... FIG 4 not shown in detail. The insertion of the spring elements 44 from one generator side 29 is shown in FIG 4 The diagram is merely illustrated with arrows. The spring elements 44 allow the pressure ring 42 to move elastically along an axial direction 31 parallel to a main axis of rotation 15 of the planet carrier assembly 30. This enables compensation for an axial offset 39 of the planet carrier 10, with which the pressure ring 42 interacts in the assembled state.

[0033] In FIG 5 Figure 70 illustrates an embodiment of a claimed wind turbine. The wind turbine 70 comprises a multi-blade rotor 72 rotatably mounted on a nacelle 73. The multi-blade rotor 72 is connected to a rotor shaft 71, which in turn is connected to a drive train 60 for torque transmission. The drive train 60 has a gearbox 62 coupled to a generator 64. The gearbox 62 is designed as a planetary gearbox 20, which has at least one planet carrier assembly 30. The planet carrier assembly 30 is designed according to one of the embodiments sketched above. The planet carrier assembly 30 is further depicted in a computer program 80 (not claimed), so that its operating behavior, particularly during operation of the wind turbine 70, can be simulated.

Claims

1. Planetary carrier arrangement (30), comprising a lubricant dispensing unit (40) for dispensing lubricant (45) into a planetary carrier (10), wherein the lubricant dispensing unit (40) has an axially elastically movable pressure ring (42) for compensating for an axial offset (39) of the planetary carrier (10), characterized in that at least one lubricant pocket (56) is formed on one side of the axially elastically movable pressure ring (42) facing the planetary carrier (10), which lubricant pocket serves as a buffer during the transfer of the lubricant (45).

2. Planetary carrier arrangement (30) according to Claim 1, characterized in that at least one spring element (44) is arranged between the axially elastically movable pressure ring (42) and a stator (41) of the lubricant dispensing unit (40).

3. Planetary carrier arrangement (30) according to Claim 2, characterized in that the at least one spring element (44) is formed as a helical spring, disc spring, annular spring, evolute spring or elastomer body.

4. Planetary carrier arrangement (30) according to Claim 2 or 3, characterized in that the axially elastically movable pressure ring (42) is secured against rotation, in particular with respect to the stator (41), via at least one fastening means (52).

5. Planetary carrier arrangement (30) according to one of Claims 2 to 4, characterized in that at least one sealing element (22) is arranged between a radial outer surface (47) of the axially elastic pressure ring (42) and the stator (41).

6. Planetary carrier arrangement (30) according to either of Claims 1 or 5, characterized in that a sealing ring (18) for receiving lubricant (45) from the axially elastically movable pressure ring (42) is attached to the planetary carrier (10).

7. Planetary carrier arrangement (30) according to one of Claims 1 to 6, characterized in that the planetary carrier (10) is received at least on one of its sides in a bearing-free manner in a housing (23).

8. Planetary carrier arrangement (30) according to one of Claims 1 to 7, characterized in that the axially elastically movable pressure ring (42) is arranged so as to lie opposite a hub (19) of the planetary carrier (10).

9. Planetary carrier arrangement (30) according to one of Claims 1 to 8, characterized in that the axially elastically movable pressure ring (42) has a clear internal diameter (43) of at least 150 mm.

10. Planetary gear (20), comprising at least one planetary stage (11, 21), in which a planetary carrier arrangement (30) according to one of Claims 1 to 10 is arranged.

11. Planetary gear (20) according to Claim 10, characterized in that the planetary gear (20) comprises at least three planetary stages (11, 21).

12. Planetary gear (20) according to Claim 10 or 11, characterized in that at least three planetary gears (14) are rotatably received in the planetary carrier (10) of the planetary carrier arrangement (30).

13. Drive train (60) for a wind turbine comprising a gear (62) which can be connected in a torque-transmitting manner to a rotor shaft (71), and a generator (64) which is connected in a torque-transmitting manner to the gear (62) according to one of Claims 10 to 12.

14. Wind turbine (70), comprising a nacelle (73), to which a multi-blade rotor (72) is attached rotatably, which is connected in a torque-transmitting manner to a drive train (60) according to Claim 13.