Planetary transmission, drive train and wind turbine with improved lubricant supply

Abstract

The invention relates to a planetary transmission (10) comprising a first and a second planetary stage (20, 30), at least one transmission component (11) and a double-walled tube (60). An outlet point (63) for distributing lubricant (35) into the transmission component (11) is formed on the double-walled tube in a central portion (50). The double-walled tube (60) is received into a guide bearing (45), a bushing (66) being arranged in the region of the outlet point (63), wherein a gap (80) is formed between the bushing (66) and the transmission component (11). The invention also relates to a drive train (81) with a generator (86) which is connected to a transmission (84) which is designed as a planetary transmission (10) according to the invention. The invention also relates to a wind turbine (90) with such a drive train (81). Furthermore, the invention relates to a computer program product (70) with which the operating behavior of such a planetary transmission (10) can be simulated.

Description

Technical Field

[0001] This invention relates to a planetary gear transmission with improved lubricant supply. The invention also relates to a transmission system having a corresponding planetary gear transmission and a wind turbine equipped with such a transmission system. Background Technology

[0002] A device for transmitting a supply medium through a drivetrain of a wind turbine is known from EP 2 597 307 A1. It comprises a double-walled conduit having an inner tube and an outer tube. The inner and outer tubes form an annular channel for lubricating oil. The inner and outer tubes are pushed onto an end member, through which a wall spacer is provided between the inner and outer tubes.

[0003] DE 10 2010 060 147 A1 discloses a planetary gearbox with a central distributor designed as an annular channel. Lubricant is supplied through an inlet point arranged on the output side, and the lubricant is delivered to a planetary gearbox located further on the drive side at an outlet point. A PTFE sealing ring is positioned at the outlet point and contacts the central distributor.

[0004] WO 2020 / 001942 A1 discloses a planetary transmission having three planetary groups connected in series. The planetary groups can be equipped with at least four, five, or even up to ten planetary gears.

[0005] A planetary transmission with two planetary levels is known from EP 3 396 203 A1, which includes a connecting shaft, a guide bearing, and a bearing flange.

[0006] A bushing is known from US 2017 / 356493 A1, which is arranged in a planetary gear at the exit point and is rotatably fixed to the planetary gear bolt, wherein a gap is formed between the bushing and the transmission component.

[0007] Planetary drives are used in a variety of technical applications, with increasingly stringent requirements for performance, reliability, service life, and cost-effectiveness. Furthermore, the efficient use of lubricants is a key objective. This is particularly true for planetary drives in wind turbines. Summary of the Invention

[0008] The object of the present invention is to provide a planetary transmission device that provides technical improvements in at least one of the above aspects.

[0009] This objective is achieved by a planetary transmission according to the invention. The planetary transmission has at least first and second planetary segments connected in series. The planetary transmission also has a double-walled tube attached to the main rotational axis region of the planetary transmission. This double-walled tube comprises an inner tube and an outer tube, through which an annular channel for lubricant is formed. For example, the inner tube can be configured as a pitch tube through which lines can be routed through the planetary transmission. When viewed along the main rotational axis, the double-walled tube has an outlet point in its central portion, configured to distribute lubricant from the double-walled tube to the transmission components. For this purpose, a bushing is arranged at the outlet point. Thus, when the lubricant is distributed to the transmission components, the lubricant passes through the bushing. The bushing enables the lubricant to be delivered to the transmission components in a low-leakage, virtually leak-free manner. The bushing is particularly durable, leak-resistant, and economical to manufacture. This allows for an increase in lubricant throughput, which can be ensured, for example, by increasing the delivery pressure in the lubricant. Due to the leak-resistant effect of the bushing, any lubricant loss occurring in this manner is minimized and therefore remains technically acceptable. As a result, improved lubrication and / or cooling of transmission components can be achieved, such as spray lubrication of the friction bearings or teeth of planetary gears. This, in turn, allows the planetary transmission to withstand increased operating loads. Therefore, the bushing according to the invention is used to improve the performance of the planetary transmission according to the invention. The bushing itself can have a relatively small size, thus allowing the economical use of a suitable material, such as bronze from which the bushing can be manufactured. Alternatively, the bushing can also be made of a non-slip material, such as steel alloys, cast iron, aluminum, aluminum alloys, or fiber composites, such as glass fiber reinforced plastics, carbon fiber reinforced plastics, aramid fiber reinforced plastics, or combinations thereof.

[0010] Furthermore, the planetary gearbox has a guide bearing in the central portion of the outlet region, configured to create a clearance on the bushing. The guide bearing can be designed, for example, as a roller bearing, and positioned such that it is supported on the transmission components, where lubricant will be distributed through the outlet point. For this purpose, the guide bearing can be positioned close to the bushing. Specifically, the bushing and guide bearing can be arranged in the region inside the hub of the planetary carrier of the second planetary gearbox. Such guide bearings are readily available in various sizes and provide high alignment accuracy for the double-walled tubes, particularly their outer tubes. Simultaneously, such guide bearings allow relative rotation between the double-walled tubes and the corresponding transmission components relative to the main axis of rotation. When the planetary gearbox is subjected to increased stress, bending stress may occur in the central region of the double-walled tubes. This can damage the clearance at the bushing. In particular, the clearance may narrow radially on one side and widen radially on the opposite side, which in turn leads to increased lubricant loss. The closer the guide bearing is axially to the bushing, the less displacement, such as axial or radial offset that could damage the clearance, can be avoided. This allows for a simple increase in the load capacity of the planetary gearbox being protected.

[0011] According to the invention, the clearance is positioned at the outlet point between the bushing and the transmission component. During normal operation, lubricant enters the clearance, preventing direct contact between the transmission component and the bushing. The clearance has a minimized clearance height, i.e., a radial dimension. This minimum clearance height reduces lubricant loss at the clearance. Because the bushing has a relatively small outer diameter, the tolerances that must be maintained to achieve the minimum clearance are more favorable relative to the overall dimensions, particularly the outer diameter of the bushing. This allows the bushing to be manufactured cost-effectively. Furthermore, this method can compensate for relative movement between the transmission component and the bushing in the axial direction.

[0012] In one embodiment of the claimed planetary gear, the clearance can be configured on the outer surface of the bushing. Therefore, the bushing is rotate-fixed to the double-walled tube, particularly its inner tube. This simplifies bushing assembly. In particular, assembly by interference fit of the bushing onto its outer surface can be avoided. As a result, the maintenance and repair friendliness of the claimed planetary gear is increased.

[0013] Additionally, a bearing bushing can be installed on the outer tube of the double-walled tube. The bearing bushing surrounds the double-walled tube and has a substantially radially aligned opening that allows lubricant to pass through. The bearing bushing can be rotatably fixed to the double-walled tube, thus achieving a rotatably fixed connection between the bushing and the double-walled tube. The bearing bushing can be structurally adjusted in a simple manner, particularly in terms of radial dimensions. As a result, the bushing can be designed to save material. The radial spacing between the double-walled tube and the transmission components can be at least partially bridged by the bearing bushing, allowing lubricant to be distributed from the outlet point into the transmission components. Therefore, the use of expensive materials such as bronze for the bushing can be minimized. The bearing bushing can be constructed to be releasable, that is, substantially releasable in a non-destructive manner. This makes it possible to manufacture bearing bushings with higher precision in a simple manner. Furthermore, the bearing bushing can be configured to be axially movable, such that axial misalignment of, for example, the double-walled tube can be compensated for during the operation of the planetary transmission.

[0014] Furthermore, the bearing bushing can be received within the inner ring of the guide bearing. Correspondingly, the outer ring of the guide bearing can be mounted on the transmission component, and lubricant will be distributed to the transmission component from the outlet point. In the area where the inner ring of the guide bearing is located, the bearing bushing can be easily adjusted in the radial direction. Consequently, the radial position of the bushing can be selected independently of the size of the guide bearing. Therefore, in interaction with the transmission component, the bearing bushing can be adapted to the size of existing guide bearings. Thus, the guide bearing can be configured as a series of standard parts with fixed predetermined dimensional increments. As a result, cost-effective standard parts can be used as guide bearings, while the bushing can be designed independently of the clearance requirements between the bushing and the transmission component. This achieves increased sealing at the clearance while simultaneously increasing cost-effectiveness. Furthermore, the guide bearing can be releasably fastened to the transmission component, for example, by a retaining ring. Therefore, shrink fitting or bonding of the guide bearing is unnecessary, allowing for simplified assembly and maintenance. Moreover, the double-walled tube can be selected substantially independently of the size of the guide bearing. Compared to prior art solutions, the size of the double-walled tube is not determined by the available sizes and dimensional increments of the guide bearing.

[0015] In another embodiment of the claimed planetary gear, the bushing can be attached to the bearing bushing, i.e., substantially on its outer surface. In this case, the bushing can be attached to the bearing bushing, for example, by a shrink fit. This connection between the bushing and the bearing bushing provides an increased sealing effect between them. Similarly, variations in the roundness of the bearing bushing, particularly the roundness of its outer surface, can be at least partially compensated for in this way. In this case, the bushing can also be disassembled, and the bearing bushing, together with the bushing, can be replaced by replacement parts in a substantially modular manner.

[0016] Furthermore, the transmission components may include a mating bushing that substantially surrounds the bushing. Therefore, a clearance on the bushing is configured between the bushing and the mating bushing. Additionally, the guide bearing, particularly its outer ring, can be received within the mating bushing. Thus, the bearing bushing, bushing, and mating bushing can be individually fitted to each other and together form a lubricant transport module. This allows for precise and cost-effective production. In particular, the bushing and / or mating bushing can be manufactured with higher precision in a targeted manner in the clearance region. Wider tolerances can be selected for other regions, which still provides sufficient ease of installation. Complex surface finishing operations that can be used to minimize lubricant loss at the clearance can be performed in a locally defined manner, thus being cost-effective. Therefore, the principle of demand-based production is further realized. The lubricant transport module can be installed as a standalone entity, i.e., in a modular manner. This further simplifies the manufacture and maintenance of the claimed planetary gear. Furthermore, this mating bushing allows for simplified lubricant routing and further simplifies the production of the claimed planetary gear.

[0017] Furthermore, the claimed planetary drive can have at least five planetary gears in the first planetary group, preferably five to twelve, more preferably seven to ten. Alternatively or additionally, the second planetary group can have at least four planetary gears, preferably six or seven. The more planetary gears arranged in the planetary carrier of a planetary group, the more lubricant is required in the corresponding planetary group. The use of bushings according to the invention allows for minimizing lubricant loss while increasing lubricant throughput. In particular, this allows for an increase in lubricant throughput without increasing the delivery pressure or the total volume of lubricant delivered. The fact that foaming occurs if the delivery pressure is too high, for example on a flat jet nozzle, essentially limits the delivery pressure. The amount of lubricant delivered is essentially limited by the delivery rate of the lubricant pump. Therefore, increasing the number of planetary gears in the planetary group can make the planetary drive more powerful. A corresponding planetary drive is disclosed in European Patent Application EP 3 587863A1, the disclosure of which is incorporated herein by reference.

[0018] Furthermore, the second planetary gear can be positioned between the first and third planetary gears, with the outlet point located in the central region of the double-walled tube within the region of the second planetary gear. The claimed solution enables a reliable, low-leakage, and efficient lubricant supply to the planetary gears located in the axially inner region of the planetary gear. Because the bushings used do not directly contact the transmission components, there is no need for frequent inspection of the outlet point due to technically related wear and tear. Therefore, the claimed planetary gear can have three or more planetary gears or additional spur gear stages through which the second or additional inner planetary gears are difficult to access. As a result, complex planetary gears with an increased number of planetary gears can be manufactured technically and operated economically.

[0019] In another embodiment of the claimed planetary gear, the transmission component to which the lubricant is to be distributed can be a planet carrier, such as a second-planetary planet carrier. When the planetary gear is in operation, relative rotation is possible between the planet carrier and the double-walled tube, which serves as, for example, a pitch tube. The bushing according to the invention allows the lubricant to be transmitted with minimal leakage, which allows for efficient supply of lubricant to the planetary gear bearings, such as friction bearings or planet carrier bearings, also known as lubricant consumers. The planet carrier can have multiple bores that allow the lubricant to be delivered substantially without loss to the respective lubricant consumers. Alternatively, the transmission component can also be the sun gear of the planetary gear, thus supplying lubricant, for example, to the gear mesh between the sun gear and the planetary gears meshing with it. The larger the outer diameter of the sun gear, the more pronounced the technical advantages discussed become. Therefore, in the claimed planetary gear, and thus in complex lubrication systems, lubricant can be reliably supplied to multiple lubricant consumers.

[0020] Furthermore, the outlet point can be formed in the region at the first end of the double-walled tube in the planetary gear drive that is claimed to be protected. The outlet point at the first end of the double-walled tube is configured to supply lubricant to the first planetary gear, such as a planetary gear bearing (which can be configured as a friction bearing or roller bearing in the planet carrier), the teeth in the first planetary gear, and / or the bearing in which the planet carrier is mounted, i.e., the planet carrier bearing. For this purpose, the outer and / or inner tubes of the double-walled tube can be rotatably fixed to the planet carrier of the first planetary gear. Alternatively, the double-walled tube can also be rotatably fixed to any other rotating or stationary transmission component. As another alternative, the double-walled tube can also be designed so that it can be loosely rotated in the planetary gear drive. As a result, there is no relative rotation between the planet carrier of the first planetary gear and the double-walled tube. Therefore, the outlet point can be sealed at the first end via at least one grooved sealing ring. The grooved sealing ring applies only reduced restoring forces in the axial and radial directions, so the guide bearing only experiences reduced mechanical stress during operation. The reduced restoring force applied in this way can be generated by the gravity of the transmission components and acts substantially continuously on the planetary transmission for which protection is sought. As a result, a minimum load can be provided for the roller bearing. This, in turn, allows the use of a simple guide bearing with reduced load capacity. Therefore, the at least one grooved sealing ring serves to reduce the axial load on the guide bearing and / or increase the usable service life of the guide bearing.

[0021] Furthermore, an inlet bushing can be disposed on a second end of the double-walled tube. This second end can be located at the end of the double-walled tube opposite to the first planetary gear. Lubricant flows in through the inlet bushing and is supplied to the planetary gear through an outlet point in the central portion (optionally, at the first end). According to one embodiment of the bushing, the inlet bushing can be formed at the outlet point of the central portion. The inlet bushing is disposed between the outer tube and the housing wall of the planetary gear, wherein an inlet orifice for the lubricant is formed in the housing wall. In particular, a gap can be formed between the inlet bushing and the double-walled tube. Therefore, a reliable and low-leakage supply of lubricant to the double-walled tube is achieved.

[0022] The transmission system according to the invention also achieves the basic objective. The transmission system includes a main shaft, which is connectable to a multi-bladed rotor of a wind turbine. The main shaft is coupled to a transmission device in a torque-transmitting manner, and the transmission device is in turn connected to a generator in a torque-transmitting manner. As a result, the rotation of the multi-bladed rotor can be converted into the rotation of the generator, and electricity can be generated. The transmission system is configured to be received in the nacelle of the wind turbine. According to the invention, the transmission device in the transmission system is configured as a planetary transmission device according to at least one of the above embodiments.

[0023] Similarly, the objective of this invention is achieved by a wind turbine according to the invention. The wind turbine has a nacelle to which a multi-bladed rotor is rotatably secured. A drive system connected to the multi-bladed rotor in a torque-transmitting manner is received in the nacelle. This drive system is configured according to one of the above embodiments.

[0024] The described objective is also achieved by a computer program product according to the invention, which is designed to simulate the operating behavior of a planetary gear train, i.e., specifically for this purpose. According to the invention, the planetary gear train to be simulated is designed according to one of the embodiments described above. The computer program product may have a physical module for simulation purposes, wherein the planetary gear train is mapped, and, for example, its mechanical or thermal behavior can be reproduced under adjustable operating conditions. Adjustable operating conditions include, for example, speed, lubricant temperature, pressure in the lubricant or its thermal behavior, such as, in particular, temperature-dependent viscosity characteristics, and / or axial and / or radial displacement of the double-walled tube. For this purpose, the computer program product may have a data interface through which corresponding data can be defined by user input and / or other simulation-oriented computer program products. The computer program product may also have a data interface for outputting simulation results to the user and / or other simulation-oriented computer program products. For example, using the computer program product, the plausibility of measurement data from sensors on a planetary gear train, associated transmission system, or wind turbine can be verified. This particularly allows for the identification of defective sensors. The computer program product can be configured as a so-called digital twin, for example, as described in more detail in published document US 2017 / 286572 A1. The disclosure of US 2017 / 286572A1 is incorporated herein by reference. The computer program product can be a monolithic configuration, meaning it can execute entirely on a hardware platform. Alternatively, the computer program product can be a modular configuration and include multiple subroutines that can execute on separate hardware platforms and interact via a communication data connection. Such a communication data connection can be a network connection or an Internet connection. Specifically, the computer program product can be configured to execute in a computer cloud. Furthermore, the computer program product according to the invention can be used to test and / or optimize planetary carrier arrangements through simulation. Attached Figure Description

[0025] The invention will now be discussed in more detail based on the various embodiments shown in the accompanying drawings. These drawings should be viewed in a complementary manner, provided that the same reference numerals in different drawings have the same technical meaning. Features of the various embodiments can also be combined with each other. Furthermore, the embodiments shown in the drawings can be combined with the features described above. Specifically, in the figures:

[0026] Figure 1 A first embodiment of the claimed planetary transmission is schematically shown in a longitudinal cross-sectional view;

[0027] Figure 2 A detailed view of the first embodiment of the claimed planetary transmission is schematically shown in a longitudinal sectional view.

[0028] Figure 3 A detailed view of the second embodiment of the claimed planetary transmission is schematically shown in a longitudinal sectional view.

[0029] Figure 4 A detailed view of the third embodiment of the claimed planetary transmission is shown in longitudinal sectional view; and

[0030] Figure 5 The structure of an embodiment of the claimed wind turbine is schematically shown in a partial oblique view. Detailed Implementation

[0031] The first embodiment of the claimed planetary transmission 10 is in Figure 1 The image is shown in longitudinal section. The planetary gear 10 is configured to deliver drive output 25 from drive side 24 to output side 26 by rotating about a main rotation axis 15. For this purpose, the planetary gear 10 includes a first planetary group 20 and a second planetary group 30, which are arranged in series along the axial direction 43. A third planetary group 39 (not shown in detail) follows. The first and second planetary groups 20, 30 each have a transmission component 11 received in the housing 12. The transmission component 11 includes a planet carrier 14, in which planetary gears are rotatably received, and the planet carrier interacts with a sun gear 18 for each planetary group 20, 30. The sun gear 18 in the first planetary group 20 is connected to the planet carrier 14 of the second planetary group 30. In addition, the transmission component 11 also includes a ring gear (not shown in detail) for each planetary group 20, 30, in which planetary gears 16 can roll. A double-walled tube 60 is arranged in the region of the main rotation axis 15, extending through the planetary gear 10 along the axial direction 43, and serves as a so-called pitch tube. The double-walled tube 60 includes an outer tube 62 and an inner tube 64, through which an annular channel 65 is disposed, through which lubricant 35 is delivered during operation. The lubricant 35 is supplied to the transmission component 11 to ensure long-term low-wear operation. For this purpose, the outer tube 62 has an outlet point 63 that allows the lubricant 35 to escape substantially radially outward 47. The outlet point 63 is located in the central portion 50 of the double-walled tube 60, where a first planetary segment 20 adjoins a second planetary segment 30.

[0032] Bearing bushing 40 is disposed in the region of outlet point 63 and is rotatably fixed to outer tube 62, thereby connecting to double-walled tube 60. Bearing bushing 40 has bearing bushing opening 41 to allow lubricant 35 to pass through. Bearing bushing 40 is also rotatably received in guide bearing 45, which is attached to the surrounding transmission component 11, namely the planet carrier 14 of the second planetary star 30. The planet carrier 14 of the second planetary star 30, like the double-walled tube 60, rotates about the main axis of rotation 15 during operation. During operation, there is relative rotation between the double-walled tube 60 and the transmission component 11, and the guide bearing 45 is arranged on the transmission component 11, following this relative rotation. Bushing 66 is rotatably fixed to the outer surface 42 of bearing bushing 40 and is designed to correspond to bearing bushing 40 to allow lubricant 35 to pass through to transmission component 11. A clearance 80 is configured between the bushing 66 and the transmission component 11 (i.e., the planetary carrier 14 of the second planetary gear 30) in which the guide bearing 45 is arranged. Therefore, there is no direct contact between the outer surface 67 of the bushing 66 and the planetary carrier 14 of the second planetary gear 30. The clearance 80 is sized in a manner that minimizes the loss of lubricant 35. The transmission component 11 is provided with a plurality of lubricant channels 22, which are hydraulically connected to the clearance 80, the bushing 66, the bearing bushing 40, and the annular channel 65 in the double-walled tube 60. Lubricant 35 can be routed via the lubricant channels 22 to other transmission components 11 (e.g., planetary gears 16) for lubrication and / or cooling.

[0033] The guide bearing 45 guides the bearing bushing 40 in the radially outward and inward directions 47, 49 relative to the transmission component 11 (i.e., the planet carrier 14 of the second planetary gear 30), thus setting the clearance 80. The bearing bushing 40 can be easily adjusted within the area of ​​the guide bearing 45, allowing the guide bearing 45 to be selected substantially independently of the dimensions of the double-walled tube 60. Therefore, an optimized guide bearing 45 can be selected for the planetary gear 10, ensuring reduced lubricant loss in the clearance 80. Furthermore, the planetary gear 10 is further depicted in a computer program product 70 (not shown in detail), which is designed to simulate the planetary gear 10.

[0034] exist Figure 2 The detailed images show more details based on... Figure 1 An example of this. Therefore, Figure 1 and Figure 2These will be studied in a complementary manner. A groove 44 is disposed on the outer tube 62 of the double-walled tube 60, in which a sealing element 53 configured as an O-ring is arranged. The seal between the bearing bushing 40 and the double-walled tube 60 is achieved by the sealing element 53, which substantially prevents the lubricant 35 from escaping. The sealing element 53 allows axial displacement 52 between the bearing bushing 40 and the double-walled tube 60. As a result, the mechanical stress on the guide bearing 45 in the axial direction 43 is reduced, leading to an increase in the usable service life of the guide bearing 45. Therefore, the bearing bushing 40 is further releasably connected to the double-walled tube 60, that is, it can be removed in a substantially non-destructive manner. The bearing bushing opening 41 is configured opposite to the outlet point 63 of the double-walled tube 60 and allows lubricant 35 to pass radially outward from the annular channel 65 in the double-walled tube 60 in the radially outward direction 47. A bushing 66 is disposed on the outer surface 42 of the bearing bushing 40, and the bushing 66 may be made of a sliding material such as bronze. Because of the bearing bushing 40, the bushing 66 can be structurally designed substantially independently of the dimensions of the double-walled tube 60. Specifically, the bushing 66 can only be designed to meet the clearance 80 between the bushing 66 and the inner surface 51 of the transmission component 11, on which the guide bearing 45 is arranged. Therefore, the bushing 66 has a reduced wall thickness 68. The bushing 66 is releasably arranged on the outer surface 42 of the bearing bushing 40 and is form-fitted onto the bearing bushing 40 by means of a stop 58 and a retaining element 54 with a fastening device 56. The clearance 80 between the outer surface 67 of the bushing 66 and the planetary carrier 14 of the transmission component 11, i.e., the second planetary star 30, is set by the guide bearing 45 arranged adjacent to the bushing 66. The guide bearing 45 includes an outer ring 46 supported on the transmission component 11 and an inner ring 48 supported on the bearing bushing 40, thus allowing relative rotation between the bearing bushing 40 and the transmission component 11. The dimensions of the outer surface 42 of the bearing bushing 40 adjacent to the bushing 66 can be determined in such a way that the guide bearing 45 is essentially independently selectable. The guide bearing 45 is thus selected in an optimized manner to minimize lubricant loss at the clearance 80. The guide bearing 45 is positioned by a retaining element 54 with a fastening device 56 and is therefore releasably connected to the transmission component 11, meaning it can be released in a substantially non-destructive manner. The retaining element 54 also serves as an anti-rotation protection device. As a result, the guide bearing 45 can be disassembled in a simple manner. The bearing bushings 40 and 66 are included in a lubricant delivery module 55, which is also interchangeable. This further simplifies the maintenance of the planetary gear 10. The operating behavior of the planetary gear 10, particularly the flow behavior of the lubricant 35 in the areas of the bearing bushings 40 and / or bushings 66, and / or the axial offset 52 between the double-walled tube 60 and the transmission component 11, can be simulated by a computer program product 70 (not shown in detail).

[0035] The second embodiment of the claimed planetary transmission 10 is in Figure 3 The image is shown in a detailed longitudinal section. A bearing bushing 40 is arranged on the outer tube 62 of the double-walled tube 60, and is rotatably fixed to the double-walled tube 60. A groove 44 is provided on the outer tube 62, in which a sealing element 53 formed as an O-ring is arranged. This allows axial displacement 52 between the double-walled tube 60 and the bearing bushing 40. An opening 41 is formed in the bearing bushing 40, allowing lubricant 35 to pass through an annular channel 65 in the double-walled tube 60 into the transmission component 11. A bushing 66 is arranged on the outer surface 42 of the bearing bushing 40 and may be made of a sliding material such as bronze. Adjacent to the bushing 66 is a guide bearing 45, which includes an outer ring 46 and an inner ring 48. The outer ring 46 of the guide bearing 45 is arranged on a mating bushing 36, which has an inner surface 37 positioned opposite to the outer surface 67 of the bushing 66. Clearance 80 is defined by the inner surface 37 of mating bushing 36 and the outer surface 67 of bushing 66, and is set by guide bearing 45. Clearance 80 is configured in a manner that minimizes lubricant loss at clearance 80. Bushing 66 is rotatably fixed to bearing bushing 40 and correspondingly follows the rotation of double-walled tube 60. Matting bushing 36 is rotatably fixed to transmission component 11, i.e., planet carrier 14 of second planetary gear 30. Thus, during operation of planetary transmission 10, there is relative rotation between bushing 66 and mating bushing 36 at clearance 80. Bushing 66 is releasably positioned by a stop 58 on bearing bushing 40 and a retaining element 54 with fastening device 56. Similarly, mating bushing 36 is releasably connected to transmission component 11 by retaining element 54 with fastening device 56. Matting bushing 36 is also designed for further passage of lubricant 35, such that lubricant 35 can be delivered through lubricant channel 22 in transmission component 11. Bearing bushing 40, together with bushing 66 and mating bushing 36, forms a lubricant delivery module 55 that can be easily replaced. Therefore, it simplifies the process according to... Figure 3 Maintenance of planetary transmission 10. According to... Figure 3 The operation of the planetary transmission 10 can also be simulated by a computer program product 70, which is not shown in detail.

[0036] The third embodiment of the claimed planetary transmission 10 is in Figure 4 The detailed view of the longitudinal section is shown schematically. Figure 4A double-walled tube 60 with an outer tube 62 and an inner tube 64 is shown in the region of the first end 61 facing the drive side 24. In the region of the first end 61, the double-walled tube 60 is coupled to a cover 19, which is considered the transmission component 11. The cover 19 is connected to the planet carrier 14 of the first planetary gear 20. In the region of the first end 61, the outer tube 62 has an outlet point 63 through which lubricant 35 can be dispensed into the cover 19. Adjacent to the outlet point 63, a groove 44 is configured on the outer tube 62, in which a grooved ring 57 is arranged. The seal between the cover 19 and the outer tube 62 of the double-walled tube 60 is formed by the grooved ring 57. The grooved ring 57 is also configured to allow axial offset 52 and / or radial offset between the outer tube 62 and the cover 19. As a result, the mechanical stress on the guide bearing 45 (not shown in detail) during operation of the planetary gear 10 is reduced. Consequently, the claimed technical advantages of the planetary gear 10 are realized to a greater extent. The behavior of the outer tube 62, particularly the axial offset 52 that occurs thereon, is part of the operating behavior of the planetary gear 10, which can be simulated by a computer program product 70, which is not shown in more detail.

[0037] An embodiment of the claimed wind turbine 90 is in Figure 5 The diagram is schematically shown in partial oblique view. The wind turbine 90 includes a nacelle 94, to which a multi-bladed rotor 92 is rotatably attached, providing a drive output 25. The multi-bladed rotor 92 is arranged on a drive side 24 and connected to a main shaft 82, through which the drive output 25 is supplied to a drivetrain 81 received in the nacelle 94. In addition to the main shaft 82, the drivetrain 81 includes a transmission 84, which is connected to the main shaft in a torque-transmitting manner. The transmission 84 is connected to a generator 86 on an output side 26 in a torque-transmitting manner. The transmission 84 has first and second planetary gears 20, 30 and is configured as a planetary transmission 10 according to one of the embodiments described above. Furthermore, the planetary transmission 10 is depicted in a computer program product 70, which is configured to simulate the operation of the planetary transmission 10 in the wind turbine 90.

Claims

1. A planetary gear train (10) comprising a first planetary group (20) and a second planetary group (30), at least one transmission component (11), and a double-walled tube (60), wherein an outlet point (63) for dispensing lubricant (35) into the transmission component (11) is disposed in a central portion (50) on the double-walled tube, and the double-walled tube is received in a guide bearing (45), characterized in that, A bushing (66) is arranged in the region of the outlet point (63) and a gap (80) is provided between the bushing (66) and the transmission component (11), wherein the bearing bushing is rotatably received in the guide bearing and arranged on the outer tube of the double-walled tube and located between the double-walled tube and the bushing, and the bearing bushing opening communicates with the outlet point.

2. The planetary transmission device (10) according to claim 1, characterized in that, The gap (80) is disposed on the outer surface (67) of the bushing (66).

3. The planetary transmission device (10) according to claim 1, characterized in that, The bearing bushing (40) is received in the inner ring (48) of the guide bearing (45).

4. The planetary transmission (10) according to any one of claims 1 to 3, characterized in that, The bushing (66) is attached to the bearing bushing (40).

5. The planetary transmission (10) according to any one of claims 1 to 3, characterized in that, A mating bushing (36) is arranged on the transmission component (11), and the gap (80) is disposed between the mating bushing (36) and the bushing (66).

6. The planetary transmission (10) according to any one of claims 1 to 3, characterized in that, The first planetary level (20) has at least five planetary gears (14) and / or the second planetary level (30) has at least four planetary gears (14).

7. The planetary transmission (10) according to any one of claims 1 to 3, characterized in that, The second row (30) is arranged between the first row (20) and the third row (39).

8. The planetary transmission (10) according to any one of claims 1 to 3, characterized in that, The lubricant (35) is to be distributed to the transmission component (11), which is the planet carrier (14).

9. The planetary transmission (10) according to any one of claims 1 to 3, characterized in that, Another outlet point (63) sealed by at least one grooved ring (57) is located in the region of the first end (61) of the double-walled tube (60).

10. A transmission system (81) for a wind turbine (100), comprising a main shaft (82), the main shaft (82) being connected to a transmission device (84) in a torque-transmitting manner, the transmission device (84) being connected to a generator (86) in a torque-transmitting manner, characterized in that, The transmission (84) is configured as a planetary transmission (10) according to any one of claims 1 to 9.

11. A wind turbine (90) comprising a multi-bladed rotor (92) rotatably attached to a nacelle (97), wherein a drivetrain (81) is received in the nacelle, characterized in that, The drivetrain (81) is configured as the drivetrain (81) according to claim 10.

12. A computer program product (70) configured to simulate the operating behavior of a planetary gear (10) used in the transmission system (81) of a wind turbine (90), characterized in that, The planetary drive (10) is configured as a planetary drive (10) according to any one of claims 1 to 9.

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