Wear-resistant transmission

Abstract

The invention relates to a transmission (18) having: a first transmission stage (26); a second transmission stage (28) directly downstream of the first transmission stage (26) in the torque flow direction; a casing tube (48) which radially outwardly delimits a lubricating channel (34); and a bearing assembly (42) for mounting the casing tube (48), which bearing assembly is provided in a transition region (40) between the first transmission stage (26) and the second transmission stage (28); wherein: the bearing assembly (42) has a first bearing (60) and a second bearing (61) which is axially offset with respect to the first bearing (60); the first bearing (60) and the second bearing (61) are fastened to a common bearing bushing (58) for conjoint rotation; and a supply channel (68) which extends in the radial direction and which fluidically communicates, through the bearing bushing (58), with the lubricating channel (34) is provided in the axial direction between the first bearing (60) and the second bearing (61) for the purpose of supplying lubricant from the lubricating channel (34) to the first transmission stage (26) and / or to the second transmission stage (28). Owing to the axially mutually spaced bearings (60, 61) for the casing tube (48), it is possible to dispense with a contact seal between the lubricating channel (34) and the supply channel (68), making it possible to implement a wear-resistant, lubricated transmission (18).

Description

[0001] Description

[0002] The invention relates to a gearbox, in particular a wind turbine gearbox for an industrial wind turbine, with the aid of which a torque and a speed can be converted with low wear.

[0003] WO 2012 / 055832 A1 discloses a wind turbine gearbox for a wind turbine with a first planetary stage and a second planetary stage, wherein an annular lubrication channel is formed between a pitch tube and a cladding tube. The lubrication channel can fluidically communicate via a transverse bore with an annular channel of a lubrication channel formed in an input-side hub of a planet carrier of the second planetary stage. Sealing between the cladding tube and the hub is achieved by rotary seals inserted into sealing grooves in the hub, against which the cladding tube slides in a relatively rotatable manner.

[0004] There is a constant need to prevent wear in transmissions.

[0005] The object of the invention is to show measures that enable a low-wear lubricated gear.

[0006] The object is achieved by a transmission having the features of claim 1, a drive train having the features of claim 12, an industrial application having the features of claim 14, and a data agglomerate having the features of claim 15. Preferred embodiments are specified in the subclaims and the following description, which can each represent an aspect of the invention individually or in combination, wherein the scope of protection is determined by the claims. If a feature is presented in combination with another feature, this only serves to simplify the representation of the invention and is in no way intended to imply that this feature cannot also be a further development of the invention without the other feature.

[0007] One aspect of the invention relates to a gearbox, in particular a wind turbine gearbox for an industrial wind turbine, having a first gear stage for converting a rotational speed, a second gear stage immediately following in a torque flow of the first gear stage for converting a rotational speed introduced by the first gear stage, a cladding tube radially outwardly delimiting a lubrication channel, and a bearing arrangement provided in a transition region between the first gear stage and the second gear stage for at least indirectly supporting the cladding tube, in particular on the first gear stage and / or on the second gear stage, wherein the bearing arrangement has a first bearing and a second bearing axially offset from the first bearing, wherein the first bearing and the second bearing are rotationally fixed to a common bearing bush,wherein in the axial direction between the first bearing and the second bearing, a supply channel is provided which extends in the radial direction and communicates fluidically with the lubrication channel through the bearing bush for supplying the first gear stage and / or the second gear stage with lubricant from the lubrication channel.

[0008] Since the cladding tube is supported not by a single bearing but by two bearings in the transition area, the axial alignment of the cladding tube can be specified very precisely. In addition, the first bearing and the second bearing are spaced apart from one another in the axial direction, at least over the extent of the supply channel in the axial direction of a main axis of rotation of the gearbox, so that the first bearing and the second bearing engage with the cladding tube at a correspondingly large distance. Tilting of the cladding tube relative to the main axis of rotation of the gearbox due to tolerances can thus be avoided or at least minimized. This makes it possible to dispense with a contact seal subject to wear and, if necessary, replace it with a non-contact seal, since the axially spaced bearings can prevent the sealing surfaces, which are spaced apart from one another via a sealing gap, from coming into contact.The height of the sealing gap can be very small and the length very large without fear of the sealing surfaces of the sealing gap hitting each other. This means that even at high lubricant delivery pressures, especially lubricating oil, only very minimal and negligible leakage can be expected. The axially spaced bearings for the cladding tube eliminate the need for a contact seal between the lubrication channel and the supply channel, thus enabling a low-wear lubricated gearbox.

[0009] Since an axial area unblocked by the bearings must be provided for the supply channel anyway, the installation space requirement is not significantly increased by the axial distance between the bearings. It is even possible for the bearings themselves to contribute to sealing the fluid transfer between the lubrication channel and the relatively rotatable supply channel, for example by the bearings forming a gap seal and / or a labyrinth seal for any lubricant leaking into the respective bearing. In addition, the respective bearing can use lubricant entering the bearing as a leak to lubricate the affected bearing, so that even if lubricant leaks due to the contactless sealing of the cladding tube, the lubricant can still be used for a beneficial function.

[0010] The first gear stage and / or the second gear stage can be designed, for example, as a planetary gear or spur gear stage. Preferably, a gear ratio other than i = 1.0 takes place in the gear stage. In particular, a step-up gear ratio is provided from a designated input side of the respective gear stage to a designated output side of the gear stage. Particularly preferably, a torque flow from the transmission occurs unbranched via the first gear stage and the second gear stage, such that the gear stages transmit essentially the full power. The transmission can, in particular, have more than two gear stages, such that a third gear stage or even an additional fourth gear stage and so on can be provided.Particularly preferably, a pair of successive gear stages, which are different from the first and second gear stages, is also designed analogously to the first and second gear stages. For example, with regard to the fluidic connection of the lubrication channel to the supply channel and the bearing arrangement, the input-side gear stage of this pair is designed analogously to the first gear stage, and the output-side gear stage is designed analogously to the second gear stage.

[0011] The lubrication channel can be supplied with fluid from a pressure source, such as a pump. The flow cross-section of the lubrication channel is specifically dimensioned for a known required mass flow of lubricant. The flow cross-section of the lubrication channel is largely annular in a common axial area with the cladding tube.

[0012] At least a portion of the supply channel can lead radially outward away from the bearings. Various channels can branch off from the supply channel to supply the respective downstream lubrication points with lubricant. The supply channel can open into a space between the bearings radially or at an angle to a radial direction and receive lubricant that is led away from the bearing arrangement exclusively or partially in the radial direction.

[0013] The lubricant to be transferred into the gearbox is, in particular, a lubricating oil, although in principle other fluids, particularly liquids, suspensions, or emulsions, can also be transferred using the fluid transfer device. Additionally or alternatively, the lubricant can also perform a cooling function, meaning that the lubricant can also be a coolant.

[0014] The cladding tube can have a substantially cylindrical shape. Preferably, the cladding tube has at least one mounting bevel to enable the cladding tube to be inserted into the bearing arrangement and / or a component of the first and / or second gear stage. The cladding tube can have a radially oriented opening on the input side, i.e., on the rotor side when installed, leading to the lubrication channel and / or on the output side, i.e., on the generator side when installed, leading to the lubrication channel in the transition region, in order to fluidically connect the lubrication channel provided inside the cladding tube with the supply channel provided outside the cladding tube. In particular, the cladding tube is closed on at least one axial end face by means of an end piece to prevent the lubricant from leaking out of the lubrication channel and / or to allow a significant delivery pressure within the lubrication channel.

[0015] The transition region is an axially extending region in which a torque-transmitting coupling of the first gear stage with the second gear stage takes place. If the first gear stage and the second gear stage are designed as planetary gears, the transition region can be defined as an axial region defined by the axial distance between the planetary gears of the first gear stage and the planetary gears of the second gear stage.

[0016] The bearing assembly can support the cladding tube and is supported for this purpose on the first gear stage and / or on the second gear stage. The bearing assembly preferably supports a transmission component that contributes to speed conversion and is, in particular, designed to be rotatable for this purpose. The bearing assembly is preferably supported with its first bearing and / or its second bearing on a sun shaft of the first gear stage configured as a planetary gear and / or a hub of a planet carrier of the second gear stage configured as a planetary gear. The sun shaft and the hub can also be designed as a single piece in the transition region.

[0017] The first bearing and / or the second bearing of the bearing arrangement can be designed in particular as rolling bearings, preferably deep groove ball bearings. The respective bearing can have an inner ring rotatable at the speed of the cladding tube and an outer ring, wherein the outer ring can be directly or indirectly fastened in a rotationally fixed manner to a component of the first gear stage and / or the second gear stage. The inner ring can be fastened to the cladding tube directly or indirectly, in particular via the bearing bush. The bearing bush can establish a mechanical connection between the first bearing and the second bearing and thereby hold the bearing arrangement together in particular as a separate subassembly. The bearing arrangement can thus be kept and installed as a common structural unit.The bearing bush can interact with the two outer rings of the bearings and the two inner rings of the bearings in such a way that the bearing bush is fastened to one of the bearing rings and mounted relative to the other bearing rings. Preferably, the respective inner ring is fastened to the common bearing bush in a rotationally fixed manner, wherein the bearing bush can be rotationally fixedly coupled to the cladding tube. The bearing bush facilitates the precise alignment of the cladding tube and enables easier assembly of the cladding tube. In particular, it is possible for the respective bearing to have a sealing element on an axial side facing away from the other bearing in order to retain lubricant penetrating into the bearing in the bearing for lubrication of the bearing.

[0018] Industrial wind turbines are primarily designed to generate energy from wind power, whereby electrical energy generated from wind power can be fed into a public power grid in particular to supply energy consumers with renewably generated energy. A wind turbine gearbox designed for an industrial wind turbine is designed in particular for an output of more than 1.0 MW, preferably more than 5.0 MW, and particularly preferably more than 7.5 MW, and is designed accordingly robust and large-volume. In particular, it is provided that the first bearing communicates fluidically with the supply channel only via a first leakage gap for lubricating the first bearing and / or the second bearing communicates fluidically with the supply channel only via a second leakage gap for lubricating the second bearing.In principle, it is possible to replace the omitted contact seal between the lubrication channel and the supply channel with a gap seal designed for the lowest possible leakage. However, it has been recognized that the lubricant can also be used to lubricate the first bearing and / or the second bearing. This makes it possible to dimension the gap height and / or the gap length of the gap seal between the lubrication channel and the supply channel for deliberate lubrication of the respective bearing. Instead of replacing the omitted contact seal with a non-contact gap seal designed for the lowest possible leakage, the contact seal is replaced by the leakage gap that deliberately allows a specific leakage flow.In contrast to a non-contact gap seal, the gap height and gap length of the leakage gap are not dimensioned to ensure that the sealing surfaces of the gap seal only just barely stop from hitting each other when leakage is as minimal as possible, but rather to ensure that, at the delivery pressure expected during operation in the lubrication channel and in the supply channel, there is a sufficient lubricant flow through the leakage gap to lubricate the respective bearing. Compared to a non-contact gap seal, this can lead to a larger gap height and / or shorter gap length for the leakage gap. The respective bearing can use lubricant entering the bearing as a leak to lubricate the affected bearing, so that automatic lubrication of the bearings can be provided during ongoing gearbox operation, without the need for separate lubrication of the bearings.This can reduce the installation space required.

[0019] Preferably, the cladding tube is attached to at least one inner ring of the bearing arrangement via at least one sealing unit that is elastic in the radial direction, wherein the sealing unit is particularly dimensioned to elastically compensate for a radial offset between the first gear stage and the second gear stage. The sealing unit can seal the lubrication channel taking into account a radial offset of the cladding tube and compensate for this offset. The elasticity of the sealing unit can also simplify the assembly of the cladding tube in the bearing arrangement and prevent damage to the front end of the cladding tube during assembly. Furthermore, it can be taken into account that, due to manufacturing and assembly tolerances, a radial offset can easily occur between the first gear stage and the second gear stage, which can be compensated for by the elasticity of the sealing unit, which is in particular annular.

[0020] Particularly preferably, the cladding tube comprises a first partial cladding tube extending largely in the first gear stage and a second partial cladding tube extending largely in the second gear stage, wherein the first partial cladding tube and the second partial cladding tube are arranged at a distance from one another in the axial direction to form an annular groove that communicates fluidically with the supply channel. The cladding tube can, for example, be designed in two parts, wherein the first partial cladding tube and the second partial cladding tube can be connected to one another via the bearing arrangement. The bearing arrangement can preferably provide a plug-in connection of the partial cladding tubes to the common cladding tube, for example via a bearing bush.Due to the axial distance between the facing end faces of the partial cladding tubes, an annular groove is automatically created in the axial area between the partial cladding tubes, with which the supply channel can communicate fluidically without the need for a separate annular groove in the bearing assembly. A transverse bore, to be created in a separate manufacturing step, is required in the cladding tube to establish a fluid connection between the lubrication channel provided inside the cladding tube and the supply channel.

[0021] In particular, a first partial lubrication channel defined by the first partial cladding tube and a second partial lubrication channel defined by the second partial cladding tube are fluidly connected via an annular chamber maintained between the first bearing and the second bearing. Since the first bearing and the second bearing are intended to be axially spaced from each other anyway, the space created between the two bearings can be used as an annular chamber into which an opening of the supply channel can open. This facilitates the formation of a rotary feedthrough and / or a fluid transfer between two components rotating relative to each other.

[0022] Preferably, the cladding tube, in particular the first partial cladding tube and the second partial cladding tube, is connected in a rotationally fixed manner to the bearing bush, which is preferably supported by the first bearing and the second bearing. The bearing bush can, in particular, provide a plug-in connection between the first partial cladding tube and the second partial cladding tube. The bearing bush can, in particular, engage both inner rings of the bearings and thereby achieve a highly precise axial alignment. The bearing bush preferably extends in the axial direction beyond the first bearing and / or the second bearing, so that a correspondingly precise axial alignment can be specified for the cladding tube, which may be multi-part and is inserted into the bearing bush.

[0023] Particularly preferably, the cladding tube and a pitch tube for the passage of lines of a blade pitch control ("pitch control") for a wind rotor are fastened in a rotationally fixed manner to a common transmission component, in particular the first transmission stage, wherein in particular a radially outer circumferential surface of the pitch tube delimits the lubrication channel radially inward at least over an axial partial region. The pitch tube can be provided radially centrally along the main axis of rotation of the transmission stages. Directional specifications such as radial, axial and tangential are used in relation to the main axis of rotation. The lubrication channel delimited radially outward by the cladding tube is thus provided radially outside the pitch tube, wherein in particular the outer circumferential surface of the pitch tube can delimit the lubrication channel radially inward at least over an axial partial region. The material expenditure for forming the lubrication channel can thereby be minimized.Since the cladding tube and the pitch tube are connected to the same gearbox component, the cladding tube and the pitch tube rotate at the same speed, meaning the relative speed between the cladding tube and the pitch tube is essentially zero. This makes it possible to keep the radial extent of the lubrication channel small without unnecessary fluid friction effects occurring in the circumferential direction, which would lead to an unnecessarily high pressure loss when pumping the lubricant through the lubrication channel. This takes advantage of the fact that, for precise axial alignment of the cladding tube, a bearing for the cladding tube is provided in the transition area between the gear stages and thus closer to the interior of the gearbox, and that both the cladding tube and the pitch tube can be easily attached to one axial end of the gearbox.

[0024] In particular, a non-contact gap seal is provided at a fluid transfer point between the cladding tube and a relatively rotatable component, said fluid transfer point being axially spaced from the bearing arrangement. Since the axial alignment of the cladding tube is predetermined by the bearing arrangement with such high precision that a contact seal between relatively rotating components in the transition region can be eliminated, this can also be provided at the other end of the lubrication channel, where the lubricant is transferred to the lubrication channel through or past the cladding tube. Due to the precise alignment of the cladding tube, it is also possible to replace a contact seal with a non-contact gap seal at a point axially spaced from the transition region, which in turn can prevent wear.

[0025] Preferably, an inner tube is provided for the radially inner boundary of the lubrication channel, wherein the inner tube is connected in a rotationally fixed manner to the cladding tube and / or to the bearing bush of the bearing arrangement via an end piece that axially closes the lubrication channel. The end piece can form an axial closure for the lubrication channel. At the same time, the end piece can be used to connect the cladding tube and the inner tube or alternatively the pitch tube at a defined radial distance. In addition, it is possible to mount the cladding tube on the one hand and the inner tube or pitch tube on the other hand in the bearing arrangement via the end piece and / or to connect them to a mounted component, in particular the bearing bush.Preferably, the inner tube is a different tube from the pitch tube, so that the position of the lubrication channel is not predetermined by the pitch tube and it is easier to adapt the flow cross-section of the lubrication channel formed between the cladding tube and the inner tube to the lubrication requirements of the transmission without this placing design requirements on the pitch tube.

[0026] The first gear stage and the second gear stage are particularly preferably designed as planetary gears, wherein in particular the bearing arrangement is mounted on a sun shaft of the first gear stage and / or on a planet carrier of the second gear stage. The gear stages designed as planetary gears can provide a particularly high gear ratio. In particular, the sun shaft of the first gear stage is connected to a hub of the planet carrier of the second gear stage. This connection leads to a transition region that is comparatively long in the axial direction and is essentially shaped like a hollow shaft with a comparatively large inner diameter, thus providing sufficient installation space in the axial direction for the bearing arrangement with the bearings that are deliberately spaced far apart in the axial direction.

[0027] In particular, the supply channel leads to at least one transmission component of the first gear stage and to a transmission component of the second gear stage. Since the supply channel branches off radially outwards in the transition region provided between the two adjacent gear stages, it is easily possible to have the supply channel run or branch off against the direction of torque flow into the first gear stage and along the direction of torque flow into the second gear stage. For example, the supply channel can be used for the lubrication of a tooth mesh between a sun gear and the planet gears of the first gear stage and / or for a rotatable lubrication of planet gears of the second gear stage on associated planet pins.

[0028] A further aspect of the invention relates to a drive train for an industrial wind turbine with a gearbox, which can be designed and developed as described above, for converting a rotational speed introduced by wind power. Preferably, an input side of the first gearbox stage facing away from the second gearbox stage is coupled to a wind-powered wind rotor, wherein an output side of the second gearbox stage facing away from the first gearbox stage is directly or indirectly coupled to a rotor of an electrical machine for generating electrical energy from wind power. Due to the axially spaced bearings for the cladding tube, a contact seal between the lubrication channel and the supply channel in the gearbox can be omitted, thus enabling a low-wear drive train.

[0029] A further aspect relates to an industrial application with a drive means, a transmission connected to the drive means in a torque-transmitting manner, which can be designed and further developed as described above, and a mechanical application connected to the transmission in a torque-transmitting manner. The drive means can be designed, for example, as an electric machine, internal combustion engine, hydraulic motor, or wind-powered rotor. The drive means can be coupled to the transmission for converting a torque and a speed of the power generated by the drive means. The transmission of the industrial application is, in turn, coupled to the mechanical application in a torque-transmitting manner, in which mechanical energy introduced via the transmission can be used. The mechanical application is, for example, a mill, vertical mill, sugar mill, cement mill, rock crusher, conveyor belt, pump, roller press, apron conveyor, tube mill,Rotary kiln, rotating gear, agitator, lifting device, waste compactor, scrap compactor, shredder for recyclable materials from, possibly previously separated and / or sorted, waste, or the like. The industrial application can be designed and developed in particular as explained above with reference to the other aspects. Due to the axially spaced bearings for the cladding tube, a contact seal between the lubrication channel and the supply channel can be eliminated, thus enabling a low-wear, lubricated industrial application. One aspect of the invention further relates to a data agglomerate with data packets summarized in a common file or distributed across various files for mapping the three-dimensional shape and / or the interactions of all components provided in the transmission, which can be designed and developed as described above.wherein the data packets are prepared to carry out an additive production of the components of the fluid transfer device, in particular by 3D printing, when processed by a data processing device for operating a machine tool for the additive manufacturing of devices, and / or to carry out a simulation of the functioning of the fluid transfer device when processed by a data processing device for carrying out a technical simulation and to output the simulation results generated thereby for further use,in particular for the purpose of providing proof of fatigue strength as a function of variable loads and / or variable temperature loads and, if necessary, comparing it with measurement data determined on a real-life device according to the invention and / or on a prototype of the device according to the invention. The data packets of the data agglomerate are specifically adapted to the inventive design of the respective device according to the invention described above in order to be able to adequately represent the inventive interaction of the components of the device according to the invention during processing in the data processing device. The data packets can, in particular, be stored spatially distributed, but adapted to one another in such a way that, in the event that all data packets are combined in a common data processing device,The data agglomerate thus assembled provides all the necessary data for additive manufacturing and / or a technical simulation with the aid of the data processing device for the device according to the invention. For example, the data packets are each separate parts of a data library (“library”), which are combined to form the data agglomerate and are adapted to each other with regard to their relative dimensions and / or absolute dimensions and / or material properties corresponding to the respective device according to the invention. The data agglomerate can represent a virtual embodiment of the respective device according to the invention in the manner of a so-called “digital twin,” which enables a virtual investigation in the form of a simulation or a real objectification with the aid of an additive manufacturing process. Such a digital twin is described, for example, in US 2017 / 286572 A1.the disclosure of which is hereby incorporated by reference as part of the invention.

[0030] When the data processing device of the machine tool processes the data agglomerate, the device according to the invention is produced, so that after processing the data agglomerate in the data processing device, the device according to the invention is obtained, at least in the form of a prototype. In particular, each data packet can represent a separately implemented component of the respective associated device according to the invention, so that the individual components can easily be assembled, actually and / or virtually, in terms of their relative position and / or relative mobility in order to realize the interactions essential to the invention. In particular, it is possible to produce the various components of the respective device separately and, if necessary, from different materials by additive manufacturing with the aid of the respective data packets and subsequently assemble them to form a prototype of the respective device.The division of the data of the data agglomerate into different data packets thus enables a simple sequential additive production of components of the respective device that are movable relative to one another in the form of a kit (“kit of parts”), which is designed to only be assembled in a meaningful way for the inventive interaction of the components of the prototype for the solution of the problem underlying the invention.

[0031] Additionally or alternatively, it is possible to use the data packets of the data agglomerate in a virtual environment during a technical simulation to calculate and / or predict the individual components of the respective device, their interactions, the physical state, and / or the change in physical parameters as a function of various boundary conditions and / or over time of the associated device according to the invention, and to further use them to check whether the device according to the invention is sufficiently suitable for the intended purpose based on the assumed design and taking into account the assumed simulated influences. If the data agglomerate is processed by a data processing device that maps the simulation environment, it is possible to examine the behavior of the device according to the invention taking into account boundary conditions, in particular changing ones.This makes it possible, for example, to investigate centrifugal force effects on individual components of the device according to the invention as a function of various static and / or dynamic loads and / or different operating temperatures, whereby such simulation results can be incorporated into the preparation of a fatigue strength verification. Preferably, the simulation results obtained after processing the data agglomerate in the data processing device for the simulation environment are stored in order to compare them with measurement data determined on an actually produced device according to the invention and / or on a prototype of the device according to the invention. This makes it possible to assess the quality of the simulation results obtained with the aid of the data agglomerate and / or, in particular in the case of particularly significant deviations, to identify measurement errors and / or an erroneous measurement.Non-destructive quality control of the device according to the invention is thereby simplified and improved.

[0032] The data agglomerate enables the cost-effective production of prototypes and / or computer-based simulations to study the functionality of the device under consideration, identify problems in the specific application, and find improvements. The solution to the problem underlying the invention can be easily and cost-effectively verified using the data agglomerate.

[0033] The invention will now be explained by way of example with reference to the accompanying drawings using preferred embodiments. The features presented below may represent an aspect of the invention, both individually and in combination, with the scope of protection being determined by the claims. They show:

[0034] Fig. 1: a schematic perspective view of a wind turbine,

[0035] Fig. 2: a schematic sectional view of a first embodiment of a gearbox for the wind turbine from Fig. 1,

[0036] Fig. 3: a schematic detailed view of a bearing arrangement of the gearbox from Fig. 2, Fig. 4: a schematic rotor-side detailed view of the gearbox from Fig. 2, Fig. 5: a schematic generator-side detailed view of the gearbox from Fig. 2, Fig. 6: a schematic detailed view of a bearing arrangement of a second embodiment of a gearbox for the wind turbine from Fig. 1, Fig. 7: a schematic rotor-side detailed view of the gearbox from Fig. 6, Fig. 8: a schematic generator-side detailed view of the gearbox from Fig. 6, Fig. 9: a schematic sectional view of a third embodiment of a gearbox for the wind turbine from Fig. 1 and

[0037] Fig. 10: a schematic detailed view of the gearbox from Fig. 9.

[0038] The industrial wind turbine 10 shown in Fig. 1 can be used to generate electrical energy from wind power. For this purpose, the wind turbine 10 has a wind rotor 12 that can be rotated by wind power. The wind rotor 12 is coupled to a drive train 14. For this purpose, the wind rotor 12 is connected to a wind rotor shaft 16, which is coupled within the drive train 14 to a gearbox 18 in order to convert the torque introduced via the wind rotor 12 and the wind rotor shaft 16. The torque converted in the gearbox 18 is fed to an electrical machine 20 operated in generator mode. The electrical energy generated by the electrical machine 20 can be fed to a rechargeable battery and / or a power grid. In the illustrated embodiment, the drive train 14 is entirely housed in a nacelle 22, which is attached to an upper free end of a tower 24.The exemplary embodiment of the gearbox 18 shown in Fig. 2 has a first gear stage 26 which can be connected to the wind rotor shaft 16 of the wind rotor 12 and is coupled to a second gear stage 28 which follows in the direction of torque flow and which in turn is coupled to a third gear stage 30. In the exemplary embodiment shown, the gear stages 26, 28, 30 are designed as planetary gears. Depending on the application, the third gear stage 30 can also be omitted. The gearbox 18 is traversed over its entire axial extent by a centrally arranged pitch tube 32, wherein the pitch tube 32 runs coaxially to a main axis of rotation 33 of the gearbox 18. Directional terms such as radial, axial, and tangential are used in relation to the main axis of rotation. The pitch tube 32 forms a radially inner boundary of a lubrication channel 34 which is fed from a third planet carrier 35 of the third gear stage 30.If no gear stage 30 is provided, the lubrication channel can be fed from a stationary gear housing. The lubrication channel 34 can open, at its end facing the wind rotor 12, into a first hub 36 of a first planetary carrier 38 of the first gear stage 26 and, in a transition region 40 between the first gear stage 26 and the second gear stage 28, penetrate a bearing arrangement 42 radially outward to convey lubricant into a second planetary carrier 44 of the second gear stage 28 and / or into a first sun shaft 46 of the first gear stage 26.

[0039] As shown in Fig. 3, the lubrication channel 34 is delimited radially on the outside by a sleeve tube 48, which in the illustrated embodiment is composed of a first partial sleeve tube 50 and a second partial sleeve tube 52. The first partial sleeve tube 50 and the second partial sleeve tube 52 are spaced from one another at their mutually facing end faces, so that an annular groove 54 is formed between the partial sleeve tubes 50, 52. The first partial sleeve tube 50 and the second partial sleeve tube 52 are each connected to a bearing bush 58 via radially elastic sealing units 56, for example radial shaft seals. The first partial sleeve tube 50 and the second partial sleeve tube 52 can each be inserted into the bearing bush 58 in the axial direction and thereby come into contact with the associated sealing unit 56.Preferably, at least two sealing units 56 are provided for each partial cladding tube 50, 52 in order to achieve the best possible sealing of the lubrication channel 34 and the annular groove 54.

[0040] The bearing bush 58 and thus also the cladding tube 48 are mounted on a hub 62 via a first bearing 60 and a second bearing 61, which is spaced significantly apart in the axial direction from the first bearing 60 and is preferably designed as rolling bearings, in particular deep groove ball bearings. In the illustrated embodiment, the hub 62 is part of both the second planet carrier 44 of the second gear stage 28 and the first sun shaft 46 of the first gear stage 26. The bearing bush 58 has a passage 64 which, radially inward, is in fluid communication with the annular groove 54 between the partial cladding tubes 50, 52. The bearing bush 58 extends radially outside the passage 64 in the vicinity of the respective bearing 60, 61, wherein an annular chamber 66 which is in fluid communication with the passage 64 is kept free.The annular chamber 66, in turn, can fluidically communicate with a supply channel 68 beginning in the hub 62, so that the supply channel 68 can fluidically communicate with the lubrication channel 34 through the bearing bush 58. Between the bearing bush 58 and the hub 62, a first leakage gap 70 leading to the first bearing 60 and a second leakage gap 71 leading to the second bearing 61 are formed. In contrast to a gap seal, these gaps allow a sufficiently large lubricant flow to pass through in order to lubricate the bearings 60, 61. A wear-prone contact seal for sealing the fluid transfer between the bearing bush 58 and the relatively rotating hub 62 of the first and second gear stages 26, 28 is thus avoided.

[0041] Additionally or alternatively, the bearing arrangement 42 can also be provided in a transition region between the second gear stage 28 and the third gear stage 30. In this case, the above and following statements would apply analogously in whole or in part. As shown in Fig. 4, the cladding tube 48 or the first partial cladding tube 50 can be fastened, in particular screwed, to the first planet carrier 38 of the first gear stage 26 at its end pointing away from the second gear stage 28. In addition, it is possible for the pitch tube 32 to also be connected, for example pressed in, to the first planet carrier 38 in a rotationally fixed manner. The cladding tube 48 and the pitch tube 32 therefore always have the same rotational speed, so that fluid friction effects in the lubrication channel 34 can be avoided or at least minimized. The pitch tube 32 protrudes from the first partial cladding tube 50 in the axial direction towards the wind rotor 12.This creates a further annular groove 72 between a wall of the first planet carrier 38 extending radially up to the pitch tube 32 and an axial end face of the first partial cladding tube 50, which communicates fluidically with a further supply channel 74 of the first planet carrier 38. The rotationally fixed connection of the pitch tube 32 and the cladding tube 48 to the first planet carrier 36 eliminates the need for components that rotate relative to one another, so that a wear-prone contact seal between components that rotate relative to one another is also unnecessary.

[0042] As shown in Fig. 5, the lubrication channel 34 can communicate fluidically with a supply line 78 via a through-opening 76 in the second partial cladding tube 52. In the illustrated embodiment, the supply line 78 is provided in the third planet carrier 35 of the third planetary stage 30. The third planet carrier 35 can be designed as a single piece with a second sun shaft 80 of the second gear stage 28. The cladding tube 48 is mounted in the region of the second partial cladding tube 52 via shaft bearings 82, as shown in Fig. 2, adjacent to the bearing arrangement 42 on the second sun shaft 80 and, as shown in Fig. 5, on the third planet carrier 35. The pitch tube 32 is sealed to the cladding tube 48 and to the second partial cladding tube 52 by sealing rings 84.The cladding tube 48 or the second partial cladding tube 52 can be sealed from the third planet carrier 35 via gap seals 86, which also seals the fluid transfer between the supply line 78 and the lubrication channel 34. A wear-prone, contacting seal for sealing the fluid transfer between the supply line 78 and the lubrication channel 34 is thus avoided. Alternatively, the supply line can be provided in a stationary transmission housing of the transmission 18, which can replace the third planet carrier 35 described here.

[0043] In the embodiment of the transmission 18 shown in Fig. 6, in comparison to the embodiment of the transmission 18 shown in Fig. 2 and Fig. 3, the lubrication channel 34 is not delimited radially on the inside by the pitch tube 32, but by a separate inner tube 88 which is arranged in the radial direction between the pitch tube 32 and the cladding tube 48. In the illustrated embodiment, the inner tube 88 is composed, analogously to the cladding tube 48, of a first partial inner tube 90 and a second partial inner tube 92. The first partial cladding tube 50 and the first partial inner tube 90 on the one hand, and the second partial cladding tube 52 and the second partial inner tube 92 are connected to one another in the transition region 40 via an end piece 94 which axially closes the lubrication channel 34.The end piece 94 is preferably designed in multiple parts, in particular in two parts, so that the respective end piece part can be pre-assembled with the respective side of the cladding tube 48 and the inner tube 88 and the end piece parts can be connected to one another during assembly of the cladding tube 48 and the inner tube 88 to form the common end piece 94. In the illustrated embodiment, the first partial cladding tube 50 and the second partial cladding tube 52 have at least one transverse bore 96 which fluidically communicates with the annular groove 54. In this case, the respective annular groove 54 is formed only in the bearing bush 58. The respective annular grooves 54 are fluidically connected via the annular chamber 66, which is correspondingly long in the axial direction.The lubrication channel 34 can thus be divided into a first partial lubrication channel delimited in the region of the first partial cladding tube 50 and a second partial lubrication channel delimited in the region of the second partial cladding tube 52, wherein the first partial lubrication channel and the second partial lubrication channel are fluidically connected to one another via the annular chamber 66.

[0044] As shown in Fig. 7, in comparison to the embodiment of the transmission 18 shown in Fig. 4, the first partial cladding tube 50 is connected to the first partial inner tube 90 via a first outer piece 98 that axially closes the lubrication channel 34. The first partial cladding tube 50 can also have at least one transverse bore 96 to establish a fluidic connection between the lubrication channel 34 and the further supply channel 74.

[0045] As shown in Fig. 8, in comparison to the embodiment of the transmission 18 shown in Fig. 5, the second partial cladding tube 52 is connected to the second partial inner tube 92 via a second outer piece 100 that axially closes the lubrication channel 34. Furthermore, it is possible for the second partial cladding tube 52 to have a further bearing bush 102, with the aid of which the gap seals 86 are formed. Alternatively, the second partial cladding tube 52 can be designed in one piece, as shown in Fig. 5. Furthermore, the second partial cladding tube 52 shown in Fig. 5 can also have the further bearing bush 102, as shown in Fig. 8. If the further bearing bush 102 is provided, the second outer piece 100 can preferably bear against an axial end face of the further bearing bush 102 and can be fastened, in particular by screwing.For this purpose, the further bearing bush 102 can have a greater material thickness in the radial direction than the remaining second partial cladding tube 52.

[0046] In the embodiment of the transmission 18 shown in Fig. 9, the first partial cladding tube 50 and the first partial inner tube 90 are omitted compared to the embodiment of the transmission 18 shown in Fig. 6. In order to adequately lubricate the first gear stage 26, it is not the lubrication channel 34 but the supply channel 68 that extends into the first planet carrier 38. Between the part of the supply channel 68 that runs along the first sun shaft 46 and the further supply channel 74 provided in the first planet carrier 38, a fluid transfer 104 that acts in the axial direction can be provided, as described, for example, in WO 2006 / 053940 A1, the content of which with regard to the fluid transfer that acts in the axial direction is hereby incorporated by reference as part of the invention. As shown in Fig.10, the cladding tube 48 and the inner tube 88 can be connected in a rotationally fixed manner to the component having the supply line 78 via the second outer piece 100, which in particular is at least two-part. In the illustrated embodiment, the supply line 78 is formed by the third planet carrier 35, although alternatively the supply line 78 can be formed by the stationary transmission housing. Relative rotation of the supply line 78 to the lubrication channel 34 is avoided, so that a high level of tightness is ensured for the fluid transfer. Shaft bearings 82 are thus eliminated. The fluid transfer to the supply channel 68 can take place analogously to the design in FIGS. 3 and 6. The inner tube 88 can be fastened to the bearing bush 58 via the end piece 94 and the associated sealing unit 56, while the cladding tube 48 is fastened to the bearing bush 58 via the associated sealing units 56 without an intermediate end piece 94.Depending on the design, in particular the axial length of the cladding tube 48, at least one transverse bore 96 is provided in the cladding tube 48 or the annular groove 54 is formed between the end piece 94 and the axial end face of the cladding tube 48.

Claims

P a t e n t a n s p r ü c h e 1. A gearbox (18), in particular a wind turbine gearbox for an industrial wind turbine (10), comprising a first gear stage (26) for converting a rotational speed, a second gear stage (28) immediately following in a torque flow of the first gear stage (26) for converting a rotational speed introduced by the first gear stage (26), a cladding tube (48) radially outwardly delimiting a lubrication channel (34), and a bearing arrangement (42) provided in a transition region (40) between the first gear stage (26) and the second gear stage (28) for at least indirectly supporting the cladding tube (48), wherein the bearing arrangement (42) comprises a first bearing (60) and a second bearing (61) axially offset from the first bearing (60), characterized in that the first bearing (60) and the second bearing (61) are rotationally fixed to a common bearing bush (58).wherein in the axial direction between the first bearing (60) and the second bearing (61) a supply channel (68) extending in the radial direction and fluidically communicating with the lubrication channel (34) through the bearing bush (58) is provided for supplying the first gear stage (26) and / or the second gear stage (28) with lubricant from the lubrication channel (34).

2. Transmission (18) according to claim 1, wherein the first bearing (60) communicates fluidically with the supply channel (68) only via a first leakage gap (70) for lubricating the first bearing (60) and / or the second bearing (61) communicates fluidically with the supply channel (68) only via a second leakage gap (71) for lubricating the second bearing (60).

3. Gearbox (18) according to claim 1 or 2, wherein the cladding tube (48) is fastened to at least one inner ring of the bearing arrangement (42) via at least one support element (56) which is elastic in the radial direction, wherein the support element (56) is dimensioned for elastic compensation of a radial offset between the first gear stage (26) and the second gear stage (28).

4. Gearbox (18) according to one of claims 1 to 3, wherein the cladding tube (48) has a first partial cladding tube (50) extending for the most part in the first gear stage (26) and a second partial cladding tube (52) extending for the most part in the second gear stage (28), wherein the first partial cladding tube (50) and the second partial cladding tube (52) are arranged spaced apart from one another in the axial direction to form an annular groove (54) fluidically communicating with the supply channel (34).

5. Transmission (18) according to claim 4, wherein a first partial lubrication channel delimited by the first partial cladding tube (50) and a second partial lubrication channel delimited by the second partial cladding tube (52) are fluidically connected via an annular chamber (66) kept free between the first bearing (60) and the second bearing (61).

6. Gearbox (18) according to one of claims 1 to 5, wherein the cladding tube (48) is connected to the bearing bush (58) in a rotationally fixed manner.

7. Gearbox (18) according to one of claims 1 to 6, wherein the cladding tube (48) and a pitch tube (32) for the passage of lines of a blade pitch angle control for a wind rotor (12) are fastened in a rotationally fixed manner to a common gear component, wherein a radially outer surface of the pitch tube (32) delimits the lubrication channel (34) radially inward at least over an axial partial region.

8. Gearbox (18) according to one of claims 1 to 7, wherein at a fluid transfer axially spaced from the bearing arrangement (42) between the cladding tube (48) and a relatively rotatable component is provided with a non-contact gap seal (86).

9. Gearbox (18) according to one of claims 1 to 8, wherein an inner tube (88) is provided for radially inner delimitation of the lubrication channel (34), wherein the inner tube (88) is connected in a rotationally fixed manner to the cladding tube (48) and / or to the / a bearing bush (58) of the bearing arrangement (42) via an end piece (94) axially closing the lubrication channel (34).

10. Transmission (18) according to one of claims 1 to 9, wherein the first gear stage (26) and the second gear stage (28) are designed as planetary gears, wherein the bearing arrangement (42) is mounted on a sun shaft (46) of the first gear stage (26) and / or on a planet carrier (35) of the second gear stage (28).

11. Transmission (18) according to one of claims 1 to 10, wherein the supply channel (68) leads both to at least one transmission component of the first transmission stage (26) and to a transmission component of the second transmission stage (28).

12. Drive train (14) for an industrial wind turbine (10) with a gearbox (18) according to one of claims 1 to 11 for converting a speed introduced by wind power.

13. Drive train (14) according to claim 12, wherein an input side of the first gear stage (26) pointing away from the second gear stage (28) is coupled to a wind power-driven wind rotor (12), wherein an output side of the second gear stage (28) pointing away from the first gear stage (26) is coupled directly or indirectly to a rotor of an electrical machine (20) for generating electrical energy from wind power.

14. Industrial application with a drive means, a transmission (18) according to one of claims 1 to 11 connected to the drive means in a torque-transmitting manner, and a mechanical application connected to the transmission (18) in a torque-transmitting manner.

15. Data agglomerate with data packets summarized in a common file or distributed across different files for mapping the three-dimensional shape and / or the interactions of all components provided in the transmission (18) according to one of claims 1 to 11, wherein the data packets are prepared to carry out an additive manufacture of the components of the transmission (18), in particular by 3D printing, when processed by a data processing device for operating a machine tool for the additive manufacture of devices and / or to carry out a simulation of the functioning of the transmission (18) when processed by a data processing device for carrying out a technical simulation and to output the simulation results generated thereby for further use,in particular for the purpose of providing proof of fatigue strength in dependence on changing loads and / or changing temperature loads.

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