Planet carrier, planetary gearing, powertrain and wind turbine

Abstract

The present invention relates to a planet carrier (10) which comprises a first and a second side wall (12, 14) interconnected by a plurality of webs (16). At least one of the webs (16) has a curved outer surface (32). According to the invention, the curved outer surface (32) is reciprocally curved in at least one region (35). The invention also relates to a planetary gear unit (60) equipped with a corresponding planet carrier (10) and a drive train (70) comprising a planetary gear unit (60) of the type described. Similarly, the invention relates to a wind turbine (80) in which a corresponding drive train (70) is used. Similarly, the invention relates to an industrial application (90) having a planetary gear unit (60) in which the claimed planet carrier (10) is used.

Description

Field of the Invention

[0001] The present invention relates to a planet carrier for a planetary gear unit. The present invention further relates to a corresponding planetary gear unit and a powertrain equipped with such a planetary gear unit. The present invention also relates to a wind turbine having such a powertrain. Background Art

[0002] German Published Application DE 10 2014 203 587 A1 discloses a planet carrier for a motor vehicle, which includes two planet carrier halves mounted on top of each other. The first planet carrier half has a first side wall for receiving planet gear pins, between which an integrally formed web is arranged. The integrally formed web is connected to a substantially flat second side wall on the second planet carrier half.

[0003] EP 2 677 209 A1 discloses a planet carrier for a planetary gear unit, which includes two opposite side walls that are connected to each other via a plurality of webs. A transition portion to the side walls is formed on the webs. For weight and strength optimization, the transition portion is designed as a spherical cup.

[0004] EP 3 587 863 A1 discloses a multi-stage planetary gear unit having a first and a second transmission stage. Both the first transmission stage and the second transmission stage are designed as planetary stages and each has a planet carrier. In this case, the planet carrier of the first planetary stage has at least five planet gears.

[0005] Planetary gear units are used in a variety of technical fields, in which increasingly high requirements are placed on their performance and economy. Therefore, increasingly high requirements are also placed on the individual components of the planetary gear unit, that is, also on the planet carrier. The basic object of the present invention is to improve the planetary gear unit in the outlined points and to provide at least one suitable component for this purpose. Summary of the Invention

[0006] This object is achieved by means of a planet carrier according to the invention, which has a first side wall and a second side wall. The side walls are arranged opposite one another and are connected to one another by means of a plurality of webs, such that rotation of the first side wall about the main axis of rotation can be transmitted to the second side wall. The webs have a curved outer surface which points substantially radially outwards and belongs to the lateral surface of the web. According to the invention, the curved outer surface has a reciprocal curvature design in at least one region, i.e. in the form of a saddle-shaped surface. The curved outer surface of the web is thus designed to be curved in opposite directions about two separate curvature axes. The reciprocal curvature curved outer surface of the web provides a high mechanical strength while reducing the use of material, i.e. reducing the weight. The reciprocal curvature curved outer surface of the web can form a web with an increasing radius. In this case, the radius can be designed to be constant or variable. This can avoid small-radius shapes which can lead to an increase in mechanical stress. Overall, this improves the material utilization rate and also implements the principle of lightweight construction. In addition, such a shape is easy to remove from the mould, allowing the production of the planet carrier according to the invention to be simple and economical, for example by casting.

[0007] In one embodiment of the claimed planet carrier, the web also includes a transition to the first side wall and / or the second side wall of the planet carrier. Correspondingly, the outer surface of the web also continues onto the first and / or second side wall at this transition. At the transition to the first side wall or the second side wall, the reciprocal curvature outer surface also provides a favourable shape, thereby avoiding an increase in mechanical stress due to shrinkage on the planet carrier. Thus, an increase in material utilization rate is also achieved on the first side wall and the second side wall of the planet carrier, and the principle of lightweight construction is implemented.

[0008] In one embodiment of the claimed planet carrier, the curved outer surface is designed to be convexly curved about a first curvature axis at the transition. Here, the term "convex" refers to an external view of the planet carrier. The first curvature axis is oriented in the tangential direction of the planet carrier and is thus substantially inclined with respect to the main axis of rotation of the planet carrier. Thus, the first curvature axis passes through the corresponding web of the planet carrier. When observed in a longitudinal section, i.e. a section along the main axis of rotation of the planet carrier, at least the transition has a substantially arcuate shape on the outer surface. Such an arcuate shape follows the stress distribution on the planet carrier which occurs during correct operation between the pin holes in the first side wall and the second side wall. This avoids mechanical stress peaks, thus achieving a high mechanical stability with reduced material consumption.

[0009] In addition, the curved outer surface can be designed to be concave-curved about a second curvature axis. In the present context, the term "concave" refers to an external view of the planet carrier. The second curvature axis extends substantially parallel to the main rotation axis of the planet carrier. Thus, the second curvature axis passes through the first side wall and the second side wall. The concave-curved outer surface at the transition portion follows the stress distribution between the hub and the pin hole in the first side wall or the second side wall. As a result, an increased material utilization rate is achieved. Also by this measure, an increase in mechanical stress is avoided, and an improvement in the material utilization rate is achieved.

[0010] In addition, the curved outer surface can have different radii of curvature relative to the second curvature axis at different axial positions, that is to say, when viewed along the main rotation axis of the planet carrier. In at least one axial edge portion of the web, that is, in the region of the first side wall or the second side wall, the curved outer surface can have a first radius of curvature relative to the second curvature axis. In the axial central portion located between the axial edge portions, the curved outer surface can have a second radius of curvature relative to the second curvature axis. In this case, the first radius of curvature is smaller in magnitude than the second radius of curvature. As a result, there is a shape in the axial central portion of the web that allows for the advantageous absorption of mechanical tensile stress. At the axial edge portions, the web and the transition portion again follow the stress distribution that occurs in the planet carrier during proper operation. In addition, the second radius of curvature with a small magnitude also allows for an increase in the material recesses at the first and second side walls without unduly impairing the mechanical load-bearing capacity of the planet carrier. Overall, an improved material utilization rate of the web is thus achieved, which in turn allows for a weight-reducing construction of the planet carrier.

[0011] In another embodiment of the claimed planet carrier, the web has a substantially constant third radius of curvature about a first curvature axis. In this case, the web continuously merges into the transition portion to the first side wall or the second side wall. The third radius of curvature that is constant relative to the first curvature axis is produced in a simple manner and provides a high load-bearing capacity between the first side wall and the second side wall via the corresponding web.

[0012] In addition, the claimed planet carrier can be of one-piece design. For this purpose, the planet carrier can be manufactured, for example, as a casting. In the case of a one-piece planet carrier, the first side wall, the second side wall, and the web form a single component. The one-piece designed planet carrier can further include at least one integrally formed hub. Alternatively, the hub on the planet carrier can also be mounted on the first side wall or the second side wall. This can be achieved, for example, according to the solution of the unpublished European patent application EP 19171876.6. The disclosure of EP 19171876.6 is incorporated herein by reference.

[0013] The one-piece designed planet carrier can be manufactured as a blank quickly and inexpensively and then requires only a minimum number of further processing steps, especially further machining operations. In addition, in the case of a one-piece planet carrier, mechanical stress peaks at the interfaces between different components are avoided. In particular, the one-piece planet carrier can be made of a single material, at least as a blank, so that the material properties are substantially the same throughout the planet carrier. This further improves the achievable material utilization. In addition, the corresponding manufacturing process, such as casting, is cost-effective and reliable.

[0014] In addition, the claimed planet carrier can have a convex transition to the circumferential web on the curved outer surface in the region of the first side wall and / or the second side wall. Here, the circumferential web is a part of the first side wall or the second side wall that extends substantially in the circumferential direction and is radially adjacent to the pin hole. On the first side wall and the second side wall, the circumferential web belongs to the tooth window located between two opposite pin holes, through which at least one tooth of the planet gear mounted there in the assembled state passes. In the end view, the first side wall or the second side wall thus substantially has a surrounding, undulating contour with alternately convex and concave curvatures. Due to the convex transition from the web to the first side wall or the second side wall, stress peaks are also avoided there. This achieves a high load capacity and low weight of the planet carrier.

[0015] In a further embodiment of the claimed planet carrier, at least one lubricant passage is formed in the first side wall and / or the second side wall. For example, the lubricant passage is designed as a hole in the first side wall and / or the second side wall. The lubricant passage can be designed as a radial hole or an axial hole. In the present context, the terms "axial" and "radial" refer to the main rotational axis of the planet carrier. Due to the reciprocally curved outer surface on the web, there are material recesses at the first side wall or the second side wall. As a result, the radial holes in the first side wall or the second side wall can have a shortened design. This simplifies and accelerates the production of the radial holes. In addition, the lubricant passage can also be designed as an axial hole which extends through the first side wall and / or the second side wall and the web. The material recesses on the first side wall or the second side wall caused by the reciprocally curved outer surface of the web also allow the axial hole to have a reduced length. In this way, the manufacturing costs for the axial hole, i.e., the lubricant passage, are also reduced. In addition, at least one intersecting radial hole and one axial hole can together form the lubricant passage. The lubricant passage represents a structural weakening of the planet carrier, for which sufficient load capacity reserves must be provided structurally. The reciprocally curved outer surface of the web provides an increased degree of mechanical load capacity, which allows multiple lubricant passages to be formed in the planet carrier in a simple and cost-effective manner. As a result, an improved lubricant supply can be achieved in the planet carrier, for example for sliding bearings or planetary gears. Alternatively or additionally, the lubricant passage can have an increased diameter, so that the throughput of the lubricant can be increased. In summary, the reciprocally curved outer surface thus allows an improved lubricant supply in the planet carrier. This in turn makes it possible to have a planet carrier with an increased number of planetary gears.

[0016] Furthermore, the claimed planet carrier can be designed to receive at least four planetary gears. Preferably, the planet carrier can be designed to receive at least five, more preferably at least seven, particularly preferably ten planetary gears. The more planetary gears there are in the planet carrier, the narrower its webs are and the lower their ability to withstand mechanical stresses. By means of the reciprocally curved outer surface of at least one web, an increase in mechanical load capacity is thus achieved, which in turn makes it possible to manufacture a compact and weight-reduced planet carrier for at least five planetary gears. Accordingly, the corresponding planetary gear transmission can advantageously be used, for example, in the drivetrain of a wind turbine.

[0017] In a further embodiment of the claimed planet carrier, the planet carrier has a mass-specific torque density of from 200 Nm / kg to 1600 Nm / kg, preferably from 400 Nm / kg to 1200 Nm / kg, particularly preferably from 450 Nm / kg to 850 Nm / kg. The mass-specific torque density is the ratio of the maximum rated torque that can be introduced into the planet carrier to the mass of the planet carrier itself. In this case, the mass of the planet carrier is based on the machined blank without additional attachments such as planet gear pins or planet gears. Here, the mass of the planet carrier also includes the mass of the hubs connected to the first side wall or the second side wall. When considering the mass-specific torque density of the planet carrier without hubs, this can be correspondingly higher. Thus, the claimed planet carrier provides a high degree of mechanical stability with low weight. In the case of a planetary gear unit to be used in the drivetrain of a wind turbine, this allows for simplified installation on the nacelle of the wind turbine.

[0018] Furthermore, the claimed planet carrier can have a relative planet gear width of from 0.50 to 0.85, preferably from 0.55 to 0.80, particularly preferably from 0.60 to 0.75. Herein, the relative planet gear width is understood to represent the ratio of the axial dimension of the net space between the first side wall and the second side wall to the axial outer dimension of the planet carrier from the first side wall to the second side wall. Here, the axial dimension of the net space between the first side wall and the second side wall substantially corresponds to the axial length of the axial central part of the web. Taking into account, for example, bearing and mounting tolerances, the net space between the first side wall and the second side wall substantially defines the maximum width of the planet gears to be installed in the planet carrier. The higher the relative planet gear width, the higher the utilization rate of the available installation space in the planet carrier. The wider the planet gears, the higher the torque that can be transmitted in the corresponding planetary stage. Thus, the claimed planet carrier provides a high degree of compactness and increased rated torque. Therefore, the claimed planet carrier can be advantageously used, for example, in applications such as wind turbines.

[0019] In a further embodiment of the claimed planet carrier, a tooth window is formed between at least two webs, for example between two adjacent webs. In the assembled state, the planet gears extend radially out of the tooth window, enabling meshing with the ring gear. Radially inside the tooth window, pin holes are formed in the first side wall and / or the second side wall. The maximum planet gear diameter is determined by the radial position of the pin holes and the shape of the webs. Relative to the main rotational axis of the planet carrier, the dimension of the tooth window in the circumferential direction is defined by the window angle. In relation to the planet carrier diameter, the window opening coefficient is defined by the window angle and the maximum planet gear diameter. Here, the window coefficient corresponds to the equation

[0020]

[0021] where,

[0022] F := window opening coefficient;

[0023] D 架 := diameter of the planet carrier at the contact point between the web and the side of the window opening angle;

[0024] D 行星齿轮 _ 最大 := maximum planet gear diameter;

[0025] α := window angle.

[0026] In the claimed embodiment, the planet carrier can have a window opening coefficient of 0.3 to 1.5, preferably 0.4 to 1.2, particularly preferably 0.5 to 1.0. Thus, the claimed planet carrier enables the net space provided between the first side wall and the second side wall to be used for the planet gears. Thereby, cavities that have no function for the operation of the planetary gear drive mechanically are avoided. Overall, this makes it possible for the planetary gear drive belonging to the planet carrier to be powerful and at the same time structurally compact. The window opening coefficient should be determined in the axial center region of the planet gear meshing.

[0027] The object on which the present invention is based is also achieved by a planetary gear drive according to the present invention. The planetary gear drive has at least one planetary stage. The planetary stage includes a ring gear and a planet carrier, and at least one planet gear is rotatably arranged in the planet carrier. The planetary gear drive also has a sun gear, wherein the at least one planet gear meshes with the sun gear and the ring gear. The planetary stage can include stationary components or only rotatable components. For example, a planetary stage that only includes rotatable components can be used as a coupling stage of a coupling drive, for example. According to the present invention, the planet carrier is designed according to one of the above embodiments. The technical advantages of the planet carrier are thus transferred to the planetary gear drive according to the present invention.

[0028] In one embodiment of the claimed planetary gear drive, a line for lubricant can be formed on the outer side of the planet carrier. In this case, the line for lubricant can be arranged on the web. Through the reciprocally curved outer surface, space savings in the radial direction are achieved. The installation space saved in this way enables the lubricant line to be installed there. This makes it possible to avoid complex holes in the planet carrier. In particular, a planet carrier with an increased width, i.e., an increased axial dimension, can be obtained, for which it is not possible to achieve sufficiently precise lubricant channels in the form of holes in the planet carrier. The performance range of the planetary gear drive is thus extended in a simple manner by the planet carrier according to the present invention.

[0029] The above object is likewise achieved by a drive train according to the invention. The drive train includes a rotor shaft which can be driven, for example, by the rotor of a wind turbine. The rotor shaft is connected in a torque-transmitting manner to a transmission which is in turn connected in a torque-transmitting manner to a generator. According to the invention, the transmission in the drive train is designed as a planetary transmission according to one of the above-described embodiments.

[0030] Furthermore, the outlined object is achieved by a wind turbine according to the invention. The wind turbine includes a rotor rotatably mounted on a nacelle. The rotor is connected to the rotor shaft of the drive train and thus supplies a driving force to the rotor shaft. According to the invention, the drive train is designed according to one of the above-described embodiments.

[0031] The described object is likewise achieved by an industrial application according to the invention. The industrial application includes a drive unit which can be designed, for example, as an electric motor, an internal combustion engine or a hydraulic motor. The drive unit provides drive power which is fed to a transmission. By converting an existing rotational speed and an existing torque, the drive power is fed to an output unit. The output unit can be designed, for example, as a mechanical application such as a mill, a vertical mill, a sugar mill, a cement mill, a crusher, a conveyor belt, a pump, a roller press, an apron conveyor, a tube mill, a rotary kiln, a rotary mechanism, a stirrer, a lifting device, a waste extruder or a scrap extruder. According to the invention, the drive unit via its transmission connected to the output unit is designed as a planetary transmission according to one of the above-described embodiments. Description of the Drawings

[0032] The invention will now be explained in more detail with reference to the individual embodiments in the drawings. In the different drawings, the same reference numerals have the same technical meaning and in this sense the drawings should be understood as being complementary to each other. The features of the individual embodiments can also be combined with each other. Furthermore, the embodiments shown in the drawings can be combined with the above-described features. More specifically:

[0033] Figure 1 A perspective view of a first embodiment of the claimed planet carrier is schematically shown;

[0034] Figure 2 A detailed view of a first embodiment of the claimed planet carrier is schematically shown;

[0035] Figure 3 A longitudinal section of a first embodiment of the claimed planet carrier is shown;

[0036] Figure 4 An end view of a first embodiment of the claimed planet carrier is shown;

[0037] Figure 5 A second embodiment of the claimed planet carrier is shown in cross-section;

[0038] Figure 6 shows the structure of a first embodiment of the claimed wind turbine;

[0039] Figure 7 shows the structure of a first embodiment of the claimed industrial application. DETAILED DESCRIPTION

[0040] Figure 1 Schematically shows in an oblique view a first embodiment of the claimed planet carrier 10. The planet carrier 10 includes a first side wall 12 and a second side wall 14, which are arranged opposite to each other along the main rotation axis 15 of the planet carrier 10. The planet carrier diameter 17 is defined by the first side wall 12 and the second side wall 16. The planet carrier 10 is a one-piece design integral with the hub 11, and through the hub 11, the drive power 25 can be introduced into the planet carrier 10. The first side wall 12 and the second side wall 14 are interconnected via a plurality of webs 16, and the webs 16 extend substantially in the axial direction, i.e., along the main rotation axis 15. Between the webs 16, the first side wall 12 and the second side wall 14 each have tangential webs 28 arranged opposite to each other. Adjacent to the tangential webs 28, pin holes 18 are respectively formed in the first side wall 12 and the second side wall 14, and are positioned to be aligned and are each designed to receive a planet gear pin 23 not specifically shown. The webs 16 and the tangential webs 28 constitute a tooth window 21. In the assembled state, the teeth of a planet gear 20 not specifically shown arranged on the planet gear pin 23 extend through the tooth window 21. The gear 20 is designed to mesh with a ring gear 62 not specifically shown and a sun gear 64 not specifically shown. The planet carrier 10 is designed as a one-piece, so the first side wall 12, the second side wall 14 and the webs 16 form a single component. The planet carrier 10 can be at least made into a blank by casting.

[0041] The webs 16 each have regions 35 located in the axial center portion 42 and / or the axial edge portion 44. The combination of the axial center portion 42 and the axial edge portion 44 substantially defines the axial dimension 40 of the planet carrier 10. The webs 16 each include a transition portion 30 to the first side wall 12 and the second side wall 14, and have an outer surface 32, and the outer surface 32 substantially corresponds to the radially outwardly directed side of the web 16. The radially outward direction is shown by an arrow 33 in Figure 1 In the specified region 35, the outer surface 32 of the corresponding web 16 is designed as a saddle surface, i.e., a reciprocal curved surface.

[0042] Figure 2 shows according to Figure 1 a detailed view of a first embodiment of the claimed planet carrier 10. Thus, Figure 1 and Figure 2shall be interpreted as complementary to each other. At least in region 35, the outer surface 32 of the web 16 has a reciprocal curved shape. Thus, the outer surface 32 is convexly curved about the first curvature axis 34. The first curvature axis 34 is oriented substantially tangentially with respect to the main rotation axis 15 of the planet carrier 10, extends through the web 16 and follows the planet carrier 10 in a curved manner in the circumferential direction. At least in region 35, the outer surface 32 of the web 16 also has a second curvature axis 36, and the outer surface 32 is designed to be concavely curved about the second curvature axis 36. In the region of the first side wall 12 and the second side wall 14, i.e., substantially in the axial edge portion 44, the outer surface 32 has a first radius of curvature 37 about the second curvature axis 36. Between the first side wall 12 and the second side wall 14, i.e., substantially in the axial center portion 42, the outer surface 32 of the web 16 has a second radius of curvature 39 about the second curvature axis 36. In this case, the second radius of curvature 39 is lower than the first radius of curvature 37. The first radius of curvature 37 and the second radius of curvature 39 are Figure 2 observed in the radial direction. In the axial center portion 42, the outer surface 32 and thus the corresponding web 16 have a shape with an increasing radius. As a result, in the case of the force flow 35 from the tangential web 28 on the first side wall 12 to the tangential web 28 on the second side wall 14, this is promoted in a manner that avoids reaching a mechanical stress peak in the web 16. Such a force flow 35 can be generated by the planet gear pins 23, which are arranged in the corresponding pin holes 18, i.e., the first pin hole 24 on the first side wall 12 and the second pin hole 26 on the second side wall 14. In the region of the first side wall 12 and the second side wall 14, the reciprocal curved outer surface 32 forms a material recess 38, which results in a weight reduction of the planet carrier 10. In addition, the reciprocal curved outer surface 32 has a convex transition portion 43 to the adjacent tangential web 28. Thus, the reciprocal curved outer surface 32 can be easily removed from the mold, thereby simplifying the production of the planet carrier 10 by casting.

[0043] Figure 3 A first embodiment of the claimed planet carrier 10 is schematically shown in a longitudinal section. Thus, Figure 1 、 Figure 2 and Figure 3 shall be interpreted as complementary to each other. Figure 3 One of the webs 16 connecting the first side wall 12 and the second side wall 14 of the planet carrier 10 is shown. The planet carrier 10, i.e., the first side wall 12, the second side wall 14 and the web 16, is of one-piece design. At least in region 35, the outer surface 32 of the web 16 has a convex curvature about the first curvature axis 34, and the first curvature axis 34 extends to Figure 3in the drawings. The outer surface 32 is curved about a first curvature axis 34 from the first side wall 12 to the second side wall 14 with respect to a substantially constant third radius of curvature 49. The third radius of curvature 49 is designed in such a way that in the regions of the first side wall 12 and the second side wall 14, i.e., in the axial edge portions 44 of the web 16, a material recess 38 is formed. Thus, a weight reduction is also achieved on the planet carrier 10. In addition, a radial hole 46 serving as a lubricant passage 45 is formed in the first side wall 12. Due to the material recess 38 in the region of the first side wall 12, the radial hole 46 has a reduced length in the radial direction 33. Similarly, an axial hole 48 is formed in the web 16, which hole 48 also serves as a lubricant passage 45 and intersects the radial hole 46, and thus forms a continuous lubricant passage 45. Due to the reciprocally curved outer surface 32, an increased load capacity is achieved at the web 16. Thus, the web 16 provides an increased load capacity, which allows an increase in the aperture diameter 47 of the radial hole 46 and / or the axial hole 48. This allows an increase in the throughput of the lubricant passage 45. In addition, the lubricant passage 45 as Figure 3 can be formed in a plurality of webs 16, and thus an improved lubricant supply can be achieved for the planet gears 20 to be arranged in the planet carrier 10. In addition, Figure 3 shows the axial edge portions 44 of the web 16 located on the first side wall 12 and the second side wall 14. Formed between the axial edge portions 44 is an axial central portion 42, which substantially radially delimits the clear space 31 located between the first side wall 12 and the second side wall 14. The axial dimension 40 of the planet carrier 10 substantially corresponds to the sum of the axial edge portions 44 and the axial central portion 42. The axial central portion 42 substantially corresponds to the maximum planet gear width 29 that the planet gears 20 to be mounted in the planet carrier 10 can have. The dimension of the axial central portion 42 based on the axial dimension 40 of the planet carrier 10 thus defines the relative planet gear width of the planet carrier 10. The reciprocally curved outer surface 32 on the web 16 results in an increased material utilization, and thus the planet carrier 10 has a relative planet gear width ranging from 0.50 to 0.85, preferably from 0.55 to 0.80, and particularly preferably from 0.60 to 0.75.

[0044] Figure 4 A first embodiment of the claimed planet carrier 10 is shown in an end view of the first side wall 12. Thus, Figure 4 should be interpreted as complementary to Figure 1 , Figure 2 and Figure 3 complementary. Figure 4It shows that a convex transition to the tangential web 28 is formed on the reciprocal curved outer surface 32 of the web 16. In the circumferential direction 41 of the planet carrier 10, the first side wall 12 thus has an end face with a wavy contour, in which the concave curved outer surface 32 of the web 16 and the convex transition to the tangential web 28 are arranged in an alternating manner. Thereby, a favorable distribution of mechanical stress is achieved in the region of the first side wall 12. In addition, splash losses can also be reduced.

[0045] The second embodiment of the claimed planet carrier 10 is shown in Figure 5 in cross section. Figure 5 It shows the first side wall 12 or the second side wall 14 which is cut transversely to the main rotation axis 15 in the region of the web 16 and in which seven pin holes 18 are formed. In Figure 5 it, the cross section through the planet carrier 10 passes through the radial hole 46, and the radial hole 46 serves as the lubricant passage 45. The tooth window 21 with the window angle 55 is formed between each pair of adjacent webs 16. As a result of this and the radial position 19 of the corresponding pin holes 18, the planet gear diameter 27 is predetermined, and the planet gear diameter 27 describes the size of the largest available planet gear 20. The interaction between the largest planet gear diameter 27, the planet carrier diameter 17 and the associated window angle 55 results in the window opening coefficient. Here, the window opening coefficient corresponds to the equation

[0046]

[0047] where, F := window opening coefficient;

[0048] D 架 := the planet carrier diameter at the contact point between the web and the side of the window opening angle;

[0049] D 行星齿轮 _ 最大 := the largest planet gear diameter;

[0050] α := window angle.

[0051] The window opening coefficient is between 0.3 and 1.5, thereby achieving an improved utilization rate of the available space in the planet carrier 10. The window opening coefficient should be determined in the axial center region of the planet gear meshing.

[0052] In addition, Figure 6An embodiment of the claimed wind turbine 80 is shown. The wind turbine 80 has a rotor 82, which is rotatably mounted on a nacelle 84. The rotor 82 is connected to a rotor shaft 72, and a generator 75 is driven by means of the rotor shaft 72 via a transmission 50. The rotor shaft 72, the transmission 50 and the generator 75 belong to the drive train 70 of the wind turbine 80, which is received in the nacelle 84. The transmission 50 is a planetary transmission 60, which has at least one planet carrier 10 according to one of the above embodiments.

[0053] Figure 7 The structure of the claimed industrial application 90 is schematically shown, which has a drive unit 92 and an output unit 94, which are connected to each other in a torque-transmitting manner via a transmission 50. The drive unit 92 is designed to provide the drive power 25 required for the operation of the drive unit 92. For this purpose, the drive unit 92 is designed, for example, as an electric motor, an internal combustion engine, or a hydraulic motor. The output unit 94 is designed for a mechanical application. The output unit 94 is correspondingly designed such that the industrial application 90 is, for example, a mill, a vertical mill, a sugar mill, a cement mill, a crusher, a conveyor belt, a pump, a roller press, an apron conveyor, a tube mill, a rotary kiln, a slewing mechanism, a stirrer, a lifting device, a waste extruder or a scrap extruder. In this case, the transmission 50 is designed as a planetary transmission 60 having at least one planetary stage 61, and the planetary transmission 60 has a planet carrier 10 according to one of the above embodiments.

Claims

1. A planet carrier (10) comprising a first side wall and a second side wall (12, 14), the first side wall and the second side wall (12, 14) being interconnected by a plurality of webs (16), wherein at least one of the webs (16) has a curved outer surface (32), wherein the curved outer surface (32) points outwards in the radial direction and belongs to the transverse surface of the web, wherein the at least one web (16) comprises a transition (30) to the first side wall (12) and a transition (30) to the second side wall (14), and the curved outer surface (32) is designed to be convexly curved around a first curvature axis (34) at the transition (30), wherein the planet carrier (10) is of one-piece design, characterized in that, the curved outer surface (32) has a reciprocal curvature design in at least one region (35) located in an axial central portion (42) and an axial edge portion (44), wherein the combination of the axial central portion (42) and the axial edge portion (44) defines the axial dimension (40) of the planet carrier (10).

2. The planet carrier (10) according to claim 1, characterized in that, The reciprocal curved outer surface on the web at the first side wall or the second side wall is provided by a material recess.

3. The planet carrier (10) according to claim 2, characterized in that, The first curvature axis (34) is oriented in the tangential direction of the planet carrier (10).

4. The planet carrier (10) according to any one of claims 1 to 3, characterized in that, The curved outer surface (32) is designed to be concavely curved around a second curvature axis (36).

5. The planet carrier (10) according to claim 4, characterized in that, The second curvature axis (36) is oriented parallel to the rotation axis (15) of the planet carrier (10).

6. The planet carrier (10) according to claim 4, characterized in that, The first curvature radius (37) that the curved outer surface (32) has around the second curvature axis (36) in the axial edge portion (44) of the web (16) is smaller in magnitude than the second curvature radius (39) in the axial central portion (42) of the web (16).

7. The planet carrier (10) according to any one of claims 1 to 3, characterized in that, The web has a constant third curvature radius around the first curvature axis (34), and the web (16) continuously merges into the transition (30) to the first side wall and / or the second side wall (12, 14).

8. The planet carrier (10) according to any one of claims 1 to 3, characterized in that The curved outer surface (32) has a convex transition (43) to a circumferential web (28) in the region of the first side wall and / or the second side wall (12, 14).

9. The planet carrier (10) according to any one of claims 1 to 3, characterized in that At least one lubricant passage (45) is formed in the web (16) in the first side wall and / or the second side wall (12, 14).

10. The planet carrier (10) according to any one of claims 1 to 3, characterized in that, The planet carrier (10) is designed to receive at least four planet gears (20).

11. The planet carrier (10) according to any one of claims 1 to 3, characterized in that, The planet carrier (10) has a mass-specific torque density ranging from 200 Nm / kg to 1600 Nm / kg.

12. The planet carrier (10) according to any one of claims 1 to 3, characterized in that, The planet carrier (10) has a relative planet gear width ranging from 0.50 to 0.85, wherein the relative planet gear width is the ratio of the axial dimension of the net space between the first side wall and the second side wall (12, 14) to the axial outer dimension of the planet carrier from the first side wall (12) to the second side wall (14).

13. A planetary gearing (60) comprising at least one planetary stage (61) having a ring gear (62), a planet carrier (10) with at least one planet gear (20), and a sun gear (64), characterized in that, The planet carrier (10) is designed as the planet carrier (10) according to any one of claims 1 to 12.

14. A drive train (70) includes a rotor shaft (72) that is connected to a transmission (50) in a torque-transmitting manner, and the transmission (50) is connected to a generator (75) in a torque-transmitting manner, characterized in that, The transmission device (50) is designed as the planetary transmission device (60) according to claim 13.

15. A wind turbine (80) comprising a nacelle (84) on which a rotor (82) is rotatably fixed, wherein a drivetrain (70) is arranged in the nacelle (84), characterized in that, The transmission system (70) is designed as the transmission system (70) according to claim 14.

16. An industrial application (90), comprising a drive unit (92), said drive unit (92) being connected to a transmission (50) in a torque-transmitting manner, and said transmission being further connected to an output unit (94) in a torque-transmitting manner, characterized in that, The transmission device (50) is designed as the planetary transmission device (60) according to claim 13.

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