planetary gear

Abstract

Planetary gear (10), in particular for a wind turbine, with at least one planetary stage (11), comprising a ring gear (12), a sun gear (13) arranged within the ring gear (12), and a planet carrier (14) with two support webs (16) spaced apart from each other and connected to each other by webs (15), wherein the planet carrier (14) has at least one bearing pin (17) arranged between the first (16.1) and the second support web (16.2) and on which a planet gear (18) is mounted, wherein the ring gear (12) can be brought into operative contact with the sun gear (13) by means of the planet gear (18), wherein the bearing pin (17) has a compensating means (19) whereby an inclination of the planet gear (18) relative to the ring gear (12) and / or the sun gear (13) is adjustable, wherein the bearing pin (17) is formed by a hollow pin (20) and a core pin (21) arranged at least partially in the hollow pin (20), and the compensating means (19) is arranged on the hollow pin (20) and / or the core pin (21), and wherein the core pin (21) and the hollow pin (20) each have a head section (26) and a longitudinal section (27), wherein the longitudinal section (27) of the core pin (21) is arranged at least partially within the longitudinal section (27) of the hollow pin (20). and wherein the head section (26) of the core bolt (21) is arranged at least section by section in a first support cheek (16.1) and the head section (26) of the hollow bolt (20) is arranged at least section by section in a second support cheek (16.2) and wherein the core bolt (21) and the hollow bolt (20) have at least one common radial contact zone (22), characterized by that the core bolt (21) and the hollow bolt (20) have at least one common axial contact zone (23).

Description

[0001] The present invention relates to a planetary gear, in particular for a wind turbine, with at least one planetary stage according to the preamble of independent claim 1. Planetary gears with at least one planetary stage are known, for example, from EP 0 054 280 B1, US 2015 / 0 240 915 A1, and JP S57-18 838 A, which have a ring gear and a sun gear arranged inside the ring gear. A planet carrier has at least one bearing pin arranged between two carrier webs, on which the planet gear is movably mounted. In planetary gears of this type, a force flow in the planetary stage leads to twisting of the planet carrier. If the torsional moment is transmitted from the planet carrier to the sun gear, the components deform elastically under the influence of the forces. The planet carrier thereby undergoes a twisting, which in turn causes the bearing pins and / or the planet gear to tilt.The solar wave is subjected to a torsional moment, which, analogous to the planetary support structure, leads to a twisting. Due to the kinematic conditions, the twisting in the solar wave is in the same direction as that in the planetary support structure.

[0002] The object of the invention is to at least partially overcome the aforementioned disadvantages known from the prior art. In particular, the object of the present invention is to at least partially compensate for the tilt of the planet under load.

[0003] The foregoing problem is solved by a planetary gear unit having the features of claim 1.

[0004] Further features and details of the invention will become apparent from the dependent claims, the description, and the drawings. The measures listed in the dependent claims enable advantageous further developments and improvements of the subject matter of the invention specified in the independent claim.

[0005] According to the invention, the planetary gear, particularly for a wind turbine, has at least one planetary stage, wherein the planetary stage comprises at least one ring gear and a sun gear arranged within the ring gear, as well as a planet carrier with two support webs spaced apart from each other and connected to each other by webs. The planet carrier includes at least one bearing pin, which is arranged between the first and the second support web and is mounted on one of the planet gears, wherein the ring gear can be brought into operative contact with the sun gear by means of the planet gear. The bearing pin has a compensating element, whereby an misalignment of the planet gear relative to the ring gear and / or relative to the sun gear can be adjusted. The compensating element according to the invention thus enables at least a partial load balancing function, whereby the position of the load engagement in the toothing between the ring gear and the planet gear can be adjusted.The planetary gear and sun gear are adjustable under load. This can reduce edge pressure in the tooth mesh, thereby improving the tooth flank load-carrying capacity of the planetary, sun, and ring gears. Corrective grinding of the tooth flanks of the planetary, ring, and / or sun gear can thus be at least reduced.

[0006] Particularly with regard to the increasingly compact design of planetary gearboxes and the associated thin-walled structures, which deform more under load, a correction and / or compensation of the misalignment is required.

[0007] While corrective grinding of the tooth flanks can compensate for the misalignment at selected operating points, the movement of the contact pattern is more pronounced outside these operating points due to the softer structure, which can ultimately lead to overloading of the gear teeth. The compensating device according to the invention can adjust the misalignment of the planet gear relative to the ring gear and / or the sun gear. In particular, the compensating device can influence the deflection curve of the bearing pins or the misalignment of the planet gear and thus counteract the softer structure of the planet carrier. An advantage of the invention is that tooth correction of the planet gear and / or the ring gear can be minimized. The compensating device enables the adjustment and / or tuning of the misalignment of the planet gear relative to the ring gear of the planetary gear set.

[0008] According to the invention, the bearing bolt is formed by a hollow bolt and a core bolt arranged at least partially within the hollow bolt, with the compensating element being arranged on the hollow bolt and / or the core bolt. The core bolt can absorb the majority of any deformation caused by the compensating element according to the invention. The deflection curve of the hollow bolt is opposite in the area of ​​the compensating element. This results in a deformation behavior that differs from the prior art. The bearing bolt designed according to the invention and the compensating element result in two overlapping deflection curves: the deflection curve of the core bolt and the deflection curve of the hollow bolt.The deflection curve of the bolts, or the misalignment of the planet gear, can be influenced by the compensating element in the bearing bolt designed according to the invention, so that a common optimum for the engagement of the planet gear and the sun gear, or of the planet gear and the ring gear, can be set. According to the invention, the planet gear can be movably mounted on the hollow bolt. The degree of misalignment transmitted from the hollow bolt to the planet gear can be controlled structurally by the dimensions of the two bolts.

[0009] Furthermore, it is provided that the core bolt and the hollow bolt have at least one common radial contact zone and at least one common axial contact zone. The hollow bolt and the core bolt are thus axially supported by each other and are in radial contact over a partial section, the contact zone preferably being provided with a fit. In contrast to a solid bolt, the common radial contact zone and the common axial contact zone only form a partial section of the common stop surface of the bearing bolt. The core bolt and the hollow bolt can support each other along the contact zones. The area without contact zones contains the compensating element, so that mutual support of the hollow bolt and the core bolt is not provided in this area.Accordingly, no forces can be transmitted from the core bolt to the hollow bolt or vice versa in this contact-free area. Therefore, even a force resulting from an applied torsional moment cannot, at least partially, cause a displacement of the planet gear, allowing for adjustment of the planet gear's misalignment relative to the ring gear and / or sun gear, particularly under load. The degree of misalignment transmitted from the hollow bolt to the planet / planet gear can be structurally influenced or adjusted by the length of the radial contact zone, the type of connection, and / or the dimensions of the hollow bolt and / or the core bolt.

[0010] Within the scope of the invention, the compensating means can be designed such that the core bolt and the hollow bolt are movable relative to each other, at least in sections. In the event of a force being applied to the core bolt, it can deform and move, at least in sections, relative to the core bolt. In this process, the core bolt undergoes elastic deformation, allowing the compensating means to adjust the misalignment of the planet gear relative to the ring gear and / or the sun gear, particularly under load.

[0011] The compensating element can advantageously be designed as a cavity between the hollow bolt and the core bolt. In particular, a wall of the hollow bolt and / or the core bolt can have a linear profile or a logarithmic curvature, thereby forming the cavity. The compensating element in the form of a cavity thus allows play between the hollow bolt and the core bolt, enabling them to be movable relative to each other, at least partially, preferably in the region of the cavity. According to the invention, the region of the cavity between the hollow bolt and the core bolt can be radially and / or axially free. If the planet carrier is subjected to a torsional moment, for example via a moment application at the planet carrier shaft, a reaction force is generated in the bearing bolts. The force flow between the bearing loads and the torsional moment in the planet carrier produces a twisting of the assembly.The compensating element according to the invention, which is preferably designed as a cavity, can absorb a large portion of the deformation, for example, from the core bolt, while the hollow bolt experiences significantly less deformation. The misalignment transmitted from the hollow bolt to the planet can be adjusted via the geometry of the cavity, particularly in conjunction with the dimensions of the axial and / or radial contact zone and / or the dimensions of the hollow bolt and / or the core bolt. The geometry of the cavity can fulfill certain sub-functions. The dimensions can assume any desired profile, for example, a linear or quadratic profile. The sub-functions can, for example, influence the edge stress at the transition to the radial contact zone or adjust the stiffness behavior of the bearing bolt depending on the applied load.According to the invention, the cavity can be formed in the hollow bolt and / or the core bolt. Within the scope of the invention, the term "cavity" can also be understood as an isolated area.

[0012] Advantageously, the cavity can be designed such that the distance between a wall of the hollow bolt and a wall of the core bolt is between approximately 0.01% and approximately 30%, preferably between approximately 0.1% and approximately 25%, and most preferably between approximately 1% and approximately 20% of the outer diameter of the hollow bolt. Depending on the expected load and desired compensation, the cavity can be geometrically adapted. A larger distance between the wall of the hollow bolt and a wall of the core bolt allows for greater deformation of the hollow bolt. It is conceivable that the distance within the cavity varies, i.e., exhibits a contour.

[0013] Furthermore, it is conceivable that at least three, and in particular four, bearing pins are provided, each with a planet gear. The number of planets and their respective bearing pins can influence the compact design of the planetary gear set, with increasing the number of planets enabling more compact planetary gear sets. Simultaneously, the more compact design of the planetary gear sets leads to significantly thinner-walled structures, for example, of the planet carrier, which exhibit greater compliance with applied loads. The bearing pin according to the invention, together with the compensating element according to the invention, can influence the deflection curve of the bearing pin or the misalignment of the planet, thus counteracting twisting of the planet carrier even in a compact design.

[0014] Within the scope of the invention, the radial and / or axial contact zone can have at least one fit. Furthermore, the core bolt and / or the hollow bolt can have a radius in the region of the axial contact zone. According to the invention, the radial contact zone can thus have an interference fit and / or the compensating element a clearance fit. The stiffness in the connected area of ​​the hollow bolt and the core bolt can vary depending on the connection parameters, for example, interference fit or clearance fit, whereby the stiffness in the area of ​​the interference fit is at most that of a solid bolt.

[0015] It is conceivable that the compensating element incorporates overload protection. The compensating element, which is primarily designed as a cavity, can be constructed such that under a specific load, the core bolt and the hollow bolt come into contact within the compensating element. This abruptly changes the system's stiffness, thus providing overload protection.

[0016] Furthermore, the core bolt and the hollow bolt each have a head section and a longitudinal section, with the longitudinal section of the core bolt being located at least partially within the longitudinal section of the hollow bolt. A large portion of the deformation resulting from the application of torque to the planetary gear can be absorbed by the longitudinal section of the core bolt, while the hollow bolt experiences correspondingly significantly less deformation.

[0017] According to the invention, the head section of the core bolt is arranged at least partially in a first front support web, and the head section of the hollow bolt is arranged at least partially in a second rear support web. The planetary bearings can be arranged on the hollow bolt, which is connected to the rear support web of the planet carrier, in particular via a press fit. The hollow bolt is also supported by the core bolt, which is connected to the front support web of the planet carrier. The hollow bolt and the core bolt are preferably axially supported by each other and are in radial contact over a partial section, the contact zone preferably being provided with a fit. Due to the introduction of a moment at the planet carrier shaft, the first support web leads the second support web as a result of elastic deformation / twisting.Thus, a large part of the deformation is absorbed by the core bolt, while the hollow bolt experiences significantly less deformation. Furthermore, it is conceivable to exchange the core bolt and the hollow bolt, so that the head section of the hollow bolt is located, at least partially, in a rear second beam web, and the head section of the hollow bolt is located, at least partially, in a front first beam web.

[0018] Advantageously, the core bolt and the hollow bolt can have a bore in the area of ​​the second support web, with the bore extending along the longitudinal axis of the bolts. This bore can, for example, serve to reduce mass or to facilitate the removal of the bearing bolts from the planet carrier. Furthermore, the bore allows the bearing bolt to be attached to the planet carrier, particularly in a reversible manner. Thus, the bearing bolt and the planet carrier can be replaced as needed. Especially with a large number of planet carriers and / or geometrically smaller planet carriers, removal can be facilitated by a bore that allows a fastener to be positioned on the bearing bolt.

[0019] The compensating element can advantageously have a length between approximately 1% and approximately 50%, preferably between approximately 3% and approximately 35%, and most preferably between approximately 5% and approximately 25% of the tooth width. The stiffness can be adjusted by the size of the compensating element and thus the dimensions of the cavity or the exposed area. The length of the compensating element can influence the edge stress at the transition to the radial contact zone or establish a non-linear stiffness behavior depending on the applied load. A longer compensating element can therefore be more elastic than a smaller / shorter one, with the stiffness increasing with a smaller compensating element.

[0020] It is further conceivable that the compensating means includes a damping element, particularly in the compensating zone. A damping element can be made of an elastic material, especially plastic. According to the invention, the damping element can, for example, absorb vibrations and / or reduce the amplitudes of movement during impacts or when passing through resonance zones.

[0021] It can be advantageous for the hollow bolt and / or the core bolt to have at least one sensor element, enabling the detection of deformation of the core bolt and / or the hollow bolt. In particular, the sensor element can be configured such that contact between the radial contact zone and / or the axial contact zone of the core bolt and the hollow bolt is detectable. Thus, maximum deformation of the core bolt relative to the hollow bolt in the area of ​​the compensating element can be detected. Specifically, the sensor element can detect the number of contacts between the hollow bolt and the core bolt, thereby providing information about the load conditions. According to the invention, a sensor element can be designed capacitively, inductively, and / or as an electromechanical switch.

[0022] Within the scope of the invention, at least the planet gear, the ring gear and / or the sun gear can have helical or straight teeth.

[0023] Advantageously, the teeth of the ring gear are arranged at an angle to each other and to the teeth of the planetary gear, with an angle β in the rest state. k between approximately 0.001° and approximately 1°, preferably between approximately 0.005° and approximately 0.5°, particularly preferably between approximately 0.01° and approximately 0.1°.

[0024] Further improvements to the invention will become apparent from the following description of some exemplary embodiments of the invention, which are schematically illustrated in the figures. All features and / or advantages arising from the claims, the description, or the drawings, including design details and spatial arrangements, can be essential to the invention, both individually and in various combinations. It should be noted that the figures are for descriptive purposes only and are not intended to limit the invention in any way.

[0025] In the following figures, identical reference numerals are used for the same technical features even for different embodiments. They show: Fig. 1 a first embodiment of a planetary gear according to the invention, Fig. 2 a three-dimensional sectional view of a possible embodiment of the planetary gear according to the invention, Fig. 3a a first possible embodiment of a bearing bolt according to the invention, Fig. 3b another possible embodiment of a bearing bolt according to the invention, Fig. 4a a first possible embodiment of a compensating agent according to the invention, Fig. 4b another possible embodiment of a compensating agent according to the invention, Fig. 4c another possible embodiment of a compensating agent according to the invention, Fig. 4d another possible embodiment of a compensating agent according to the invention, Fig. 4e another possible embodiment of a compensating agent according to the invention, Fig. 5 Arrangement of the toothing of the ring gear to the planet gear.

[0026] The Fig. Figure 1 shows a first possible embodiment of a planetary gear 10 according to the invention, which is designed in particular for use in a wind turbine. The planetary gear 10 comprises at least one planetary stage 11, having a ring gear 12, a sun gear 13 arranged inside the ring gear 12, and a planet carrier 14 with two support webs 16.1 and 16.2 spaced apart from each other and connected to each other by webs. The planet carrier 14 has at least one bearing pin 17, which is arranged between the first 16.1 and the second support web 16.2 and on which a planet gear 18 is mounted. The ring gear 12 can be brought into operative contact with the sun gear 13 by means of the planet gear 18. The bearing pin 17 has in Fig. A compensating element 19 is provided, allowing for adjustment of the planet gear 18's misalignment relative to the ring gear 12 and / or the sun gear 13. The bearing pin 17 is formed by a hollow pin 20 and a core pin 21 arranged at least partially within the hollow pin 20. The compensating element 19 is formed as a cavity 19 on the hollow pin 20. The planet gear 18 is rotatably mounted on the hollow pin 20. The core pin 21 and the hollow pin 20 have common radial contact zones 22 and a common axial contact zone 23. The hollow pin 20 and the core pin 21 are supported against each other via the radial contact zone 22 and the axial contact zone 23. In the area of ​​the compensating element 19, the core pin 21 and the hollow pin 20 are designed to be movable relative to each other, at least partially. The cavity 19 allows for deformation of the core bolt 21, at least in the area of ​​the cavity 19.The cavity 19, which is formed as a cylindrical hollow space, can be configured such that a distance of approximately 0.01% to 30%, preferably approximately 0.1% to 25%, and particularly preferably approximately 1% to 20% of the outer diameter of the hollow bolt is formed between the wall 24 of the hollow bolt 20 and the wall 24 of the core bolt 21. Accordingly, the longitudinal section 27 of the hollow bolt 20 extends at least partially into the area of ​​the compensating element 19, thereby circumferentially limiting the cavity 19. The head section 26 of the core bolt 21 is arranged at least partially in the first front support flange 16.1, with the head section 26 of the hollow bolt 20 being arranged at least partially in a second rear support flange 16.2. The compensating element 19 is located in . Fig. 1 essentially formed as a cylindrical cavity 19 in the hollow bolt 20.

[0027] The Fig. Figure 2 shows another possible embodiment of a planetary gear 10 according to the invention, wherein the planetary gear 10 has at least three planetary stages 11. The planetary gear 10 is shown in a three-dimensional view and as a partial section. Each planetary stage 11 has a planet gear 18, which is rotatably arranged on the bearing pin 17. The bearing pin 17 has a hollow pin 20 and a core pin 21 arranged at least partially in the hollow pin 20. The head section 26 of the core pin 21 is arranged at least partially in a first front support web 16.1, and the head section 26 of the hollow pin 20 is arranged at least partially in a second rear support web 16.2. Preferably, the head sections 26 of the hollow pin 20 and of the core pin 21 are arranged in the support web 16.1 and 16.2 via an interference fit. Furthermore, the planetary gear 10 has in Fig. 2. A sun gear 13 is arranged inside the ring gear 12, which can be brought into operative connection with a planet gear 18 and, via the planet gear 18, into operative connection with the ring gear 12. The support webs 16.1 and 16.2 are connected to each other by webs 15.

[0028] In the Fig. Figure 3a shows a possible embodiment of a bearing bolt 17 according to the invention. The bearing bolt 17 has a hollow bolt 20 and a core bolt 21 arranged at least partially within the hollow bolt 20. The longitudinal section 27 of the core bolt 21 is completely located within the hollow bolt 20. The head section 26 of the core bolt 21 has a radial contact zone 23 with the hollow bolt 20. Furthermore, the core bolt 21 has a radial contact zone 22. The compensating element 19 is designed as a substantially cylindrical cavity 19 in the hollow bolt 20. In the region of the cavity 19, the hollow bolt 20 and the core bolt 21 therefore do not have a common contact zone. The cavity 19 is also designed in the axial direction such that the hollow bolt 20 has no axial contact zone 23 with the core bolt 21 in the area of ​​the head section 26 of the hollow bolt 20.A sensor element 30 is arranged on the hollow bolt 20 in the area of ​​the compensating medium 19, making it possible to detect deformation of the core bolt 21 and / or the hollow bolt 20. Fig. 3a the sensor element 30 is designed as an electromechanical switch 30, so that contact between the core bolt 21 and the hollow bolt 20 can be detected.

[0029] The Fig. Figure 3b shows a further embodiment of a bearing bolt 17 according to the invention. The bearing bolt 17 has a core bolt 21 and a hollow bolt 20, wherein the core bolt 21 is arranged at least partially in the hollow bolt 20. The compensating element 19 is in Fig. 3b in the longitudinal section 27 of the core bolt 21 is formed as a cavity 19. In comparison to Fig. 3a are in Fig. 3b The core bolt 21 and the hollow bolt 20 are interchanged. Furthermore, in Fig. 3b the compensating element 19 is formed on the longitudinal section 26 of the core bolt 21 and in the area of ​​the head section 26 of the core bolt 21. Thus, no axial contact zone 23 is formed in the area of ​​the head section 26 with the hollow bolt 20, in particular with the longitudinal section 27 of the hollow bolt 20. Furthermore, the bearing bolt 17 has in Fig. 3b on the hollow bolt 20 in the area of ​​the compensating element 19, a damping element 29 is provided. The damping element 29 can, for example, be made of a plastic and, for example, absorb or reduce vibrations. It is also conceivable that a sensor element 30 is formed in the damping element 29. A bore 28 is formed in the head section 26 of the hollow bolt 20, the bore 28 extending through the head section 26 of the hollow bolt 20 into the longitudinal section 27 of the core bolt 21. Fig. 3b the core bolt 21 has an axial contact zone 23 with the hollow bolt 20.

[0030] In the Fig. Figures 4a to 4e show possible embodiments of the compensating element 19 of the bearing bolt 17. Fig. 4a The compensating element 19 is formed as a cavity 19 in the hollow bolt 20, in particular in the longitudinal section 27 of the hollow bolt 20. Furthermore, the compensating element 19 is formed as a cavity 19 in the area between the head section 26 and the longitudinal section 27 of the hollow bolt 20. The hollow bolt 20 has a wall 24, wherein the wall 24 has a cylindrical cavity in the hollow bolt 20, thus forming the cavity 19 as the compensating element 19 in the longitudinal section 27 of the hollow bolt 20.

[0031] The Fig. Figure 4b shows another possible embodiment of a compensating element 19 on the bearing bolt 17. The compensating element 19 is designed as a wedge-shaped recess / cavity 19 in the longitudinal section 27 of the hollow bolt 20. The wall 24 thus has a linearly tapered profile from the head section 26 of the core bolt 21 to the longitudinal section 27 of the hollow bolt 20. Fig. 4c The compensating element 19 is designed as a cavity 19 between the hollow bolt 20 and the core bolt 21, wherein the wall 24 of the hollow bolt 20 has a logarithmic curvature. A common radial contact zone 22 can thus form when the core bolt 21 bends in the direction of the hollow bolt 20. Accordingly, when the core bolt 21 bends, the radial contact zone 22 can extend from the longitudinal section 27 to the head section 26. Fig. 4d The hollow bolt 20 has a first cavity 19 in the region of the longitudinal section 27 of the hollow bolt 20 and the core bolt 21, wherein the cavity in this region has a cylindrical geometry. The cavity 19 in the region of the longitudinal section 27 of the hollow bolt 20 and core bolt 21 has a larger geometric dimension than the cavity 19 in the region of the overload protection 25. In the region of the overload protection 25, the core bolt 21 and the hollow bolt 20 can come into contact under a certain load. This abruptly changes the stiffness of the system, which can thus enable overload protection. Accordingly, different deformation sections of the core bolt 21 can be formed. Fig. Figure 4e shows another possible embodiment of a bearing bolt 17 with a compensating element 19. The cavity 19 of the compensating element 19 is as shown in the Fig. 4a to 4d are formed in the area of ​​the head section 26 of the core bolt 21, so that no axial contact zone 23 is formed between the core bolt 21 and the hollow bolt 20 in the area of ​​the cavity 19 of the head section 26. Fig. 4e, the cavity 19 in the longitudinal section 27 of the hollow bolt 20 and the core bolt 21 is cylindrically formed. The hollow bolt 20 has a comparable geometry to the core bolt 21 in the area of ​​the head section 26 of the core bolt 21. The hollow bolt 20 has a stop surface for a planetary bearing in the area of ​​the cavity 19 and the head section 26 of the core bolt.

[0032] The Fig. Figure 5 shows the arrangement of the toothing 12.1 of the ring gear 12 relative to the toothing 18.1 of the planet gear 18. The toothing 12.1 of the ring gear 12 and the toothing 18.1 of the planet gear 18 can form an angle β in the rest state. kz may have a temperature difference between approximately 0.001° and approximately 1°, preferably between approximately 0.005° and approximately 0.5°, and most preferably between approximately 0.01° and approximately 0.1°.

[0033] The preceding explanation of the embodiments describes the present invention solely by way of examples. Naturally, individual features of the embodiments can be freely combined with one another, provided this is technically feasible, without departing from the scope of the present invention. Reference symbol list 10 planetary gears 11th planetary stage 12 Ring gear 12.1 Toothing of ring gear 12 13 Sun wheel 14 planetary carriers 15 bridges 16 support cheeks 16.1 first anterior cheekbone 16.2 second posterior cheek 17 bearing bolts 18 planetary gear 18.1 Gearing of planetary gear 18 19 Compensating material, cavity 20 hollow bolts 21 core bolts 22 radial contact zone 23 axial contact zone 24 wall 25 Overload protection 26 Head section 27 Longitudinal section 28 bore 29 Damping element 30 sensor elements

Claims

[1] Planetary gear (10), in particular for a wind turbine, with at least one planetary stage (11), comprising a ring gear (12), a sun gear (13) arranged inside the ring gear (12), and a planet carrier (14) with two support webs (16) spaced apart from each other and connected to each other by means of webs (15), wherein the planet carrier (14) has at least one bearing pin (17) arranged between the first (16.1) and the second support web (16.2) and on which a planet gear (18) is mounted, wherein the ring gear (12) can be brought into operative contact with the sun gear (13) by means of the planet gear (18), wherein the bearing pin (17) has a compensating means (19) whereby an inclination of the planet gear (18) relative to the ring gear (12) and / or the sun gear (13) is adjustable, wherein the bearing pin (17) is formed by a hollow pin (20) and a core pin (21) arranged at least partially in the hollow pin (20), and the compensating means (19) is arranged on the hollow pin (20) and / or the core pin (21), and wherein the core pin (21) and the hollow pin (20) each have a head section (26) and a longitudinal section (27), wherein the longitudinal section (27) of the core pin (21) is arranged at least partially within the longitudinal section (27) of the hollow pin (20). and wherein the head section (26) of the core bolt (21) is arranged at least section by section in a first support cheek (16.1) and the head section (26) of the hollow bolt (20) is arranged at least section by section in a second support cheek (16.2) and wherein the core bolt (21) and the hollow bolt (20) have at least one common radial contact zone (22), characterized by , that the core bolt (21) and the hollow bolt (20) have at least one common axial contact zone (23). [2] Planetary gear (10) according to any one of the preceding claims, characterized by , that the compensating means (19) is designed such that the core bolt (21) and the hollow bolt (20) are designed to be movable relative to each other at least section by section. [3] Planetary gear (10) according to any one of the preceding claims, characterized by, that the compensating means (19) is designed as a cavity (19) between hollow bolt (20) and core bolt (21), in particular that a wall (24) of the hollow bolt (20) and / or the core bolt (21) has a linear profile or a logarithmic curvature, thereby forming the cavity (19). [4] Planetary gear (10) according to claim 3, characterized by , that the cavity (19) is designed such that a distance between a wall (24) of the hollow bolt (20) and a wall (24) of the core bolt (21) is formed of approximately 0.01% and approximately 30%, preferably between approximately 0.1% and approximately 25%, particularly preferably between approximately 1% and approximately 20% of the outer diameter of the hollow bolt. [5] Planetary gear (10) according to any of the preceding claims, characterized by , that at least three, in particular four, bearing bolts (17) are provided, each with a planet gear (18). [6] Planetary gear (10) according to any one of the preceding claims, characterized by that the compensating agent (19) has an overload protection (25). [7] Planetary gear (10) according to any of the preceding claims, characterized by , that the core bolt (21) and the hollow bolt (20) have a bore (28) in the area of ​​the second support cheek (16.2), wherein the bore (28) extends in the direction of the longitudinal axis of core bolt (21) and hollow bolt (20). [8] Planetary gear (10) according to any of the preceding claims, characterized by , that the compensating agent (19) has a length between approximately 1% and approximately 50%, preferably between approximately 3% and approximately 35%, most preferably between approximately 5% and approximately 25% of the tooth width. [9] Planetary gear (10) according to any of the preceding claims, characterized by , that the compensating means (19) has a damping element (29), in particular in the compensating zone. [10] Planetary gear (10) according to any of the preceding claims, characterized by , that the hollow bolt (20) and / or the core bolt (21) has at least one sensor element (30) which makes a deformation of the core bolt (21) and / or hollow bolt (20) detectable. [11] Planetary gear (10) according to any of the preceding claims, characterized by , that at least the planet gear (18), the ring gear (12) and / or the sun gear (13) is designed with straight or helical teeth. [12] Planetary gear (10) according to any of the preceding claims, characterized by , that the teeth of the ring gear (12) are arranged at an angle to each other with respect to the teeth of the planet gear (18) and form an angle β in the rest state k between approximately 0.001° and approximately 1°, preferably between approximately 0.005° and approximately 0.5°, most preferably between approximately 0.01° and approximately 0.1°.

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