Fluid delivery device for transferring a lubricant

Abstract

The invention relates to a fluid delivery device (26) for transferring a lubricant, comprising a first component (28), a second component (30) able to rotate relative to the first component (28), an annular chamber (32), which is formed on an end face (34) of the first component (28) that faces towards the second component (30), for receiving the lubricant, at least one hollow pin (38), which is connected to the second component (30) and plunges axially into the annular chamber (32), for fluidic communication between the annular chamber (32) and a fluid channel (36) of the second component (30), and a cover (46), which is connected to the first component (28), for captively retaining the hollow pin (38) in the annular chamber (32), wherein the cover (46) forms a first sliding bearing surface (66), and the hollow pin (38) is axially supported on the first sliding bearing surface (66) via a second sliding bearing surface (68). By virtue of the hollow pin (38) plunging into the annular chamber (32) and of the axially spaced-apart sealing on the first sliding bearing surface (66), good and long-term sealing of the annular chamber (32) can be effected even in the case of installation tolerances, thus allowing maintenance-free and / or leakage-free fluid delivery between components (28, 30) rotating relative to each other.

Description

[0001] Fluid transfer device for transferring a lubricant

[0002] Description

[0003] The invention relates to a fluid transfer device with the aid of which a lubricant can be transferred between components that are rotatable relative to one another, in particular within a wind turbine gearbox for an industrial wind turbine.

[0004] From WO 2006 / 053940 A1 it is known to form an annular chamber filled with a lubricant with the aid of a prestressed flange, wherein the prestressed flange presses against a plain bearing surface in which openings of fluid channels are formed in the radius region of the annular chamber, so that an axial lubricant transfer from the annular chamber into the fluid channels can take place within a planetary gear.

[0005] US 2007 / 0049448 A1 discloses a fluid transfer device formed in a planetary gear system, in which a planet carrier is rotationally fixedly coupled to a distributor body, wherein an annular chamber formed in the distributor body is fluidly connected via an axially extending oil pipe to a planetary gear pin located in a lubrication channel of a planetary gear pin fixed in the planet carrier. To compensate for positional tolerances between the distributor body and the planet carrier, the particularly flexible oil pipe can be accommodated in its end-side receiving openings so that it can be axially displaced and / or tilted. There is a constant need to implement a fluid transfer between components rotating relative to one another with as little maintenance as possible.

[0006] The object of the invention is to provide measures that enable low-maintenance fluid transfer between components rotating relative to one another. Preferably, the object of the invention is to provide measures that enable high efficiency of fluid transfer with low leakage losses.

[0007] The object is achieved by a fluid transfer device having the features of claim 1, a wind turbine gearbox having the features of claim 13, a drive train 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, each of which, individually or in combination, can represent an aspect of the invention, 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.

[0008] One aspect of the invention relates to a fluid transfer device for transferring a lubricant, in particular within a wind turbine gearbox for an industrial wind turbine, comprising a first component, a second component rotatable relative to the first component, an annular chamber formed on an end face of the first component facing the second component for receiving the lubricant, at least one hollow pin connected to the second component and axially immersed in the annular chamber for fluidic communication between the annular chamber and a fluid channel of the second component, and a cover connected to the first component for captively retaining the hollow pin in the annular chamber, wherein the cover forms a first sliding bearing surface and the hollow pin is axially supported on the first sliding bearing surface via a second sliding bearing surface.

[0009] Since the lubricant is transferred between the relatively rotating components in an axial direction rather than a radial direction, it is easily possible to provide the lubricant fluid transfer over a particularly large diameter. Particularly if the fluid transfer device is to be used in a wind turbine gearbox for an industrial wind turbine, it makes it easier to design the wind turbine gearbox particularly large and dimension it for particularly large power ranges, such as those that can occur in offshore wind turbines at high wind speeds. This simplifies or even enables the scaling up of the wind turbine gearbox to ever larger power classes with such a fluid transfer device.

[0010] In the fluid transfer device, the annular chamber can be recessed into the first component. Relative to the end face of the first component facing the second component, the annular chamber can be formed entirely in an axial region of the first component facing away from the end face in an axial region of the first component. The annular chamber can, for example, have a substantially U-shaped cross-section that is, in particular, substantially constant in the circumferential direction and, in the plane of the end face of the first component, is open toward the second component. A fluid line provided in or on the first component can open into the annular chamber to supply and / or discharge lubricant. Since the hollow pin, which is connected to the second component and is, in particular, screwed, projects into the annular chamber, an opening of the hollow pin can be positioned axially offset into the first component relative to the end face of the first component.The mouth opening of the hollow pin can be recessed into the annular channel. The fluid transfer of the lubricant between the annular channel and the hollow pin, which moves relatively in the circumferential direction, can thus take place within the first component and does not have to be provided in a gap between the first component and the second component. This can save installation space. In addition, the fluid transfer of the lubricant between the annular channel and the hollow pin can be significantly spaced from the separating surfaces to be sealed between the components that rotate relative to one another, making it significantly easier to create a reliable and long-lasting seal between the first component and the second component. In particular, the seal between the two components that rotate relative to one another can be relocated to the interior of the annular channel, thereby reducing the axial installation space required.

[0011] Once the hollow pin, which is inserted into the annular chamber, has been installed, the cover can be fastened to the first component. For example, the hollow pin can have a collar that projects radially outwards relative to the longitudinal axis of the hollow pin, which could come into direct or indirect contact with the cover after the cover has been installed. This ensures that the hollow pin is retained captively in the inserted state in the annular chamber after the cover has been installed. By captively retaining the hollow pin in the annular chamber, axial withdrawal of the hollow pin on the annular chamber is positively blocked, so that the mouth of the hollow pin always remains immersed in the annular chamber during normal operation.

[0012] At the same time, the cover can form the first plain bearing surface in a radius area that covers a radius area occupied by the annular chamber. The first plain bearing surface can therefore both perform the function of forming an axial plain bearing together with the second plain bearing surface and also assume the function of delimiting part of the annular chamber. This exploits the knowledge that the extension of the first plain bearing surface in the radial direction can be adjusted to protrude slightly beyond the radial extension of the annular chamber, making it particularly easy to form the largest possible first plain bearing surface over a generously and / or large-sized annular chamber. This simultaneously leads to a good sealing effect within the axial plain bearing formed by the first plain bearing surface and the second plain bearing surface and low pressure losses caused by flow losses within the fluid transfer device.The amount of viscous friction within the annular chamber can be reduced.

[0013] The second plain bearing surface that can slide on the first plain bearing surface can in principle be formed by the hollow pin, in particular a collar that projects outwards from the hollow pin, so that direct contact between the cover and the hollow pin can be provided to form the axial plain bearing. However, it is preferably also possible to utilize the axial extension of the hollow pin within the annular chamber by providing the axial support of the hollow pin on the first plain bearing surface of the cover only indirectly via a further component, so that automatic alignment of the adjoining plain bearing surfaces can take place even in the event of an angular deviation and / or an offset in the radial direction of the hollow pin to a main axis of rotation of the first and / or second component, and good sealing in the axial plain bearing can be ensured even with installation tolerances.Leakage of lubricant, especially through the axial plain bearing, can thus be easily minimized.

[0014] The hollow pin that penetrates into the annular chamber and the axially spaced seal on the first plain bearing surface ensure a good and long-lasting seal of the annular chamber even with installation tolerances, thus enabling low-maintenance and / or low-leakage fluid transfer between components that rotate relative to one another.

[0015] The fluid transfer device can, in principle, be used for all lubrication arrangements in which a transfer is to take place between components that rotate relative to one another and / or rotate relative to one another in the axial direction. In particular, the fluid transfer device is intended where a fluid transfer of the lubricant can take place over a large radius and / or where there is insufficient installation space and / or sufficient accessibility near the main axis of rotation. The fluid transfer device is preferably suitable for pressure lubrication, in particular of bearing points and / or gear meshes, in a wind turbine gearbox intended for use in an industrial wind turbine.

[0016] Industrial wind turbines are primarily designed to generate energy from wind power. The electrical energy generated from wind power can be fed into a public power grid, in particular, to supply energy consumers with renewable energy. A wind turbine gearbox designed for an industrial wind turbine is designed specifically for an output of over 1.0 MW, preferably over 5.0 MW, and particularly preferably over 7.5 MW, and is accordingly robust and large-volume.

[0017] The lubricant to be transferred in the fluid transfer device is, in particular, a lubricating oil, although in principle other fluids, in particular 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.

[0018] The first component and / or the second component can be designed as a rotating component, wherein the other component can be an immovably stationary component or a component that can rotate at a different speed. In any case, during normal operation, a relative speed can occur between the first component and the second component. The first and / or second component can, for example, be part of a gearbox, in particular a wind turbine gearbox, so that bearing points of the gearbox can be lubricated with the aid of the fluid transfer device. The first and / or second component can, for example, be a planet carrier of a planetary gearbox. The other component can, for example, be part of another gear stage or part of a stationary housing of the gearbox.The end face of the first component lies in particular in a radial plane spanned perpendicular to a main axis of rotation of the first component and / or the second component, which preferably coincides with a longitudinal center line of the first component and / or the second component. Apart from the cover attached to the first component, the end face preferably forms an axial end of the first component facing the second component in a radius region occupied by the second component. The end face can in particular form a flange side of the first component, with the aid of which the cover can be flange-mounted to the first component.

[0019] The hollow pin can be shaped to create a fluidic connection between the first component and the second component via a cavity formed in the hollow pin. The hollow pin can dip into the annular chamber at one end with its mouth opening and be fluidly connected to a fluid channel leading to a lubrication point at its other end. Alternatively, the hollow pin can also open into an annular channel of the second component, wherein the annular channel can already be part of the fluid channel. For this purpose, the hollow pin can have an interior space designed in the manner of a hollow cylinder. Preferably, the hollow pin is designed to be able to transmit forces occurring in a tangential direction without being sheared off, so that the hollow pin can support torques imposed, for example, by viscous friction on the second component and / or on the first plain bearing surface of the cover.The hollow pin can be designed to be axially movable relative to the first component, whereby the kinematic reversal is also possible, in which the hollow pin is designed to be axially movable relative to the second component.

[0020] The cover can be designed, in particular, as an annular lid, wherein a plurality of cover segments can also be provided, following one another in the circumferential direction. The cover can be provided on the axial side facing the annular chamber, at least in the region of the first plain bearing surface, with a plain bearing material, for example bronze, in particular by coating or additive manufacturing. The first plain bearing surface and the second plain bearing surface can bear against one another, preferably be pressed against one another, in order to form an axial plain bearing. The axial plain bearing designed in this way is, in particular, additionally designed for a sealing function, for example by dimensioning the radial extent of the first plain bearing surface and the second plain bearing surface larger than would be necessary to support the expected axial forces.This minimizes lubricant leakage from the axial plain bearing and significantly extends maintenance intervals, for example, for refilling lubricant. This makes the fluid transfer device particularly low-maintenance and / or minimizes wear. Furthermore, compared to a gap seal, the axial plain bearing designed in this way can prevent particles or other contaminants from penetrating the annular chamber. Damage to a bearing lubricated with the lubricant, particularly a plain bearing, caused by entrained contaminants can thus be avoided, which in turn makes the fluid transfer device particularly low-maintenance.

[0021] In particular, the second plain bearing surface is formed by a support ring that is axially movable relative to the hollow pin, wherein the support ring is preferably coupled to the hollow pin via a spring element. Alternatively, the hollow pin can be immovably connected to the support ring and designed to be axially relatively movable within a fluid channel of the second component, wherein in particular the spring element is provided in the second component, preferably in the fluid channel. The hollow pin can be fixed in its axial relative position by its attachment to the second component. For the fluid transfer device to function properly, it is sufficient that the hollow pin is immersed in the annular chamber, wherein an axial offset and / or an angular offset of the hollow pin relative to the annular chamber can be permitted without impairing the transfer of lubricant between the annular chamber and the hollow pin.In order to form a sufficiently tight axial plain bearing, however, the hollow pin is not pressed directly against the first plain bearing surface of the cover, but rather the hollow pin is indirectly supported on the cover via the support ring. The support ring can be pulled or pressed against the first plain bearing surface with the aid of the spring element in order to be able to apply a sealing contact force between the first plain bearing surface of the cover and the second plain bearing surface formed by the support ring. In this case, the support ring can be supported on the hollow pin, in particular via the spring element. The hollow pin can be guided through the support ring in a relatively movable manner in order to immerse itself in the annular chamber. The support ring can be supported on a part of the hollow pin immersed in the annular chamber via the spring element and can be pressed against the cover with a spring preload of the spring element.A gap in the cover can be closed with the help of the support ring and sealed off from the cover. An opening in the annular chamber facing the second component can be partially covered by the cover and largely covered by the support ring in another part, with the at least one hollow pin intentionally providing fluid communication through the support ring. The support ring can therefore contribute to sealing the annular chamber. If the internal pressure in the annular chamber should increase, the lubricant within the annular chamber can press with the increased internal pressure against a rear side of the support ring facing away from the second component, thereby increasing the contact force of the support ring on the cover.By means of the support ring, which is pre-tensioned by means of the spring element and axially movable relative to the hollow pin, a self-reinforcing seal is achieved in the axial plain bearing formed by the first plain bearing surface of the cover and the second plain bearing surface of the support ring, whereby a particularly low-loss fluid transfer is realized due to the good sealing of the annular chamber.

[0022] The spring element can be designed, in particular, as a helical spring, which, as a compression spring or tension spring, can preload the support ring relative to the hollow pin with a spring force in order to provide a sufficiently tight contact pressure between the first sliding bearing surface of the cover and the second sliding bearing surface of the support ring. The spring element can be made, for example, from spring steel. In principle, however, it is also possible to manufacture the spring element from an elastomeric and / or rubber-elastic material and / or to design it as a compressible, solid block. Alternatively, the contact force can be provided springlessly by a separate hydraulic pressure via a cylinder and / or by the weight of the support ring's mass.

[0023] Preferably, a receiving chamber encapsulated by the support ring and the hollow pin is formed between the support ring and the hollow pin, wherein in particular the spring element is at least largely received in the receiving chamber, wherein in particular the receiving chamber is sealed against the lubricant in the annular chamber. For example, the support ring can slide on the hollow pin during its axial relative movement. A fit provided between the support ring and the hollow pin can be selected to be so tight that the lubricant cannot pass through the fit due to its rather high viscosity. In a preferred embodiment, a clearance is formed between the hollow pin and the support ring, in particular so that the support ring can align itself with the cover.This allows both the hollow pin and the support ring to remain movable within a predefined range, allowing angular misalignments to be easily compensated for without compromising the sealing effect of the axial plain bearing. In particular, a gap seal is formed between the support ring and the hollow pin. This allows a free space to be created between the support ring and the hollow pin, which provides the receiving chamber for the spring element. If the spring element breaks, the fragments can be retained in the receiving chamber, preventing them from being flushed out with the lubricant and reaching locations along with the lubricant where they could cause damage to transmission components.

[0024] Particularly preferably, the support ring has a through opening for at least part of the hollow pin, wherein at least one axially extending annular gap, preferably at least two axially spaced-apart annular gaps, is formed between the support ring and the hollow pin, wherein in particular the annular gap is dimensioned to permit an angular deviation Aa of the hollow pin, wherein in particular 0.01° < Aa < 2.0°, preferably 0.02° < Aa < 1.0° and particularly preferably 0.05° < Aa < 0.5° applies. The support ring preloaded with the spring element can automatically align itself with the first sliding bearing surface of the cover, so that the first sliding bearing surface of the cover and the second sliding bearing surface of the support ring lie flat against one another. In this case, the at least one annular gap between the support ring and the hollow pin can be dimensioned large enough to permit limited tilting of the hollow pin relative to the support ring.Preferably, the annular gap is dimensioned so small that the lubricant cannot pass through the annular gap due to the viscosity of the lubricant, in particular lubricating oil. The appropriately dimensioned lubrication gap allows for the possibility that, due to installation tolerances, an angular deviation of the second component relative to the first component may occur, which is reflected in the relative position of the hollow pin to the first component, the cover, and / or the support ring. Jamming and / or damage to the hollow pin within the through-opening of the support ring can thus be avoided.

[0025] In particular, the hollow pin is sealed to the support ring by means of an annular seal or membrane that is elastically deformable in the radial direction. The annular seal is preferably provided in at least one annular gap between the support ring and the hollow pin. If two or more annular gaps are provided, it is possible for the annular seal to be provided in all annular gaps or only in some of the annular gaps, in particular only in exactly one annular gap. The annular seal or the membrane can achieve sufficient sealing of the annular channel in order to prevent leakage of lubricant between the support ring and the hollow pin through the through-opening of the support ring. The membrane can be designed to be able to absorb the expected relative movements.This makes it possible to permit a particularly large angular deviation of the hollow pin relative to the support ring and the first component without having to risk leakage, since the ring seal can be compressed to slightly different degrees in the circumferential direction without losing its sealing effect. The support ring is preferably composed of several support ring segments arranged one after the other in the circumferential direction, wherein the support ring segments in particular form a sealing gap chicane, in particular a labyrinth seal, on their tangential sides facing one another. The respective support ring segment can in particular cover a partial circle. The segmented structure of the support ring simplifies the manufacture of the support ring and reduces manufacturing costs. A seal, for example in the form of a flat cover element, can be provided at the connection points of the support ring segments.The cover element can, for example, encompass a tangential joint between two support ring segments following one another in the circumferential direction in a U-shape, resulting in a T-shaped gap between the tangential joint of the support ring segments and the cover element, which provides an improved sealing effect compared to the tangential joint between the support ring segments. Preferably, a potential leakage path is deliberately extended by a non-planar design of the tangential sides. The sealing effect of a gap seal formed between the tangential sides by a remaining joint can thereby be improved. The sealing gap chicane formed in this way can fulfill the function of a labyrinth seal. Despite the segmented structure of the support ring, impairment of the sealing function is avoided or at least reduced.

[0026] Particularly preferably, the support ring is fastened to the second component and / or guided in translation via at least one fastening element, in particular a relief pin corresponding to the outer contour of the hollow pin, wherein the relief pin in particular allows axial relative mobility. In comparison to the hollow pin, the fastening element can be solid, i.e. not hollow, so that the fastening element can support a higher load than the hollow pin with the same outer dimensions. Preferably, the at least one hollow pin and the at least one fastening element are arranged evenly distributed in the circumferential direction, preferably alternatingly, with essentially the same outer contour. As a result, it is not necessary to maintain a specific relative position in the circumferential direction when mounting the support ring, which simplifies assembly.

[0027] In particular, the cover has an inner ring and an outer ring, wherein the hollow pin, in particular also the relief pin, is guided through a space between the inner ring and the outer ring, wherein in particular a passage area remaining in the space is closed by the support ring. The cover is therefore designed in several parts, in particular in two parts. The space between the inner ring and the outer ring of the cover allows relative rotation of the hollow pin relative to the first component and the cover connected to the first component. This prevents the hollow pin from striking the cover. The space between the inner ring and the outer ring of the cover can be sealed, in particular with the help of the support ring. In this case, it is not necessary to provide a radial bearing and / or a radial seal in the space.Instead, the preloaded support ring, which is pressed against the first sliding bearing surface partially formed by the inner ring and the outer ring, can seal the intermediate space. The inner ring can provide a circumferentially closed first inner sliding surface, and the outer ring can provide a coaxial, circumferentially closed first outer sliding surface that is radially offset from the first inner sliding surface and is closed in the circumferential direction, which together form the first sliding bearing surface of the cover. It is possible for the outer sliding surface and the inner sliding surface to be arranged coplanar or axially offset. Correspondingly, the support ring can provide a circumferentially closed second inner sliding surface and a coaxial, circumferentially closed second outer sliding surface that is radially offset from the second inner sliding surface and is closed in the circumferential direction, which together form the second sliding bearing surface.The first plain bearing surface and the second plain bearing surface can be interrupted over the radial extent of the intermediate space between the inner ring and the outer ring. Preferably, the cover is fastened to the first component via a fastening means, wherein the fastening means, in particular a screw, is guided from an axial side facing away from the second component through an opening in the first component to the cover. For example, the cover has a fastening opening with an internal thread. The cover can therefore be easily installed because it is not necessary to maintain a large axial installation space between the first component and the second component.Instead, it is sufficient to position the cover, or rather the inner ring and the outer ring, with a tool acting in a radial direction and to fasten the cover, in particular by screwing it, from the rear side of the first component facing away from the second component. The first component can have suitable holes for this purpose, through which the fastening means can be guided to the cover to be fastened.

[0028] Particularly preferably, the first plain bearing surface and / or the second plain bearing surface is / are positioned entirely within the annular chamber extending to the end face of the first component. The axial plain bearing formed by the first plain bearing surface and the second plain bearing surface can be offset from the end face within the first component, in particular within a volume otherwise occupied by the annular chamber. This results in a compact and space-saving design. Furthermore, the axial plain bearing is provided in a protected area where the first and / or second plain bearing surface is less likely to be damaged during assembly.

[0029] In particular, the cover is centered on the annular chamber via a centering bevel. For example, the cover projects slightly into the annular chamber with a centering lug that can slide along the centering bevel, and / or a centering lug of the first component that can slide along the centering bevel formed by the cover projects into the cover. This simplifies the assembly of the cover and prevents damage to the first and / or second plain bearing surface during assembly. Preferably, the first plain bearing surface begins at an end of the centering lug that axially penetrates the annular chamber and extends radially from the centering lug.

[0030] Preferably, a seal is pressed between the cover and the end face of the first component. This prevents leakage between the cover and the end face. This can take advantage of the fact that the cover can lie flat against the end face, making it particularly easy to seal any gap remaining between the cover and the end face.

[0031] A further aspect of the invention relates to a wind turbine gearbox for an industrial wind turbine, comprising a gear stage configured as a planetary gear and a fluid transfer device, which can be designed and further developed as described above, wherein, in particular, the second component of the fluid transfer device is formed by a planet carrier of the gear stage and preferably the first component is formed by a stationary housing or a rotating gear component, in particular a further planet carrier, of a further gear stage following in the direction of power flow. The wind turbine gearbox can be designed and further developed, in particular, as explained above with reference to the fluid transfer device.The hollow pin that penetrates into the annular chamber and the axially spaced seal on the first plain bearing surface ensure a good and long-lasting seal of the annular chamber even with installation tolerances, thus enabling low-maintenance and / or low-leakage fluid transfer between components of the wind turbine gearbox that rotate relative to one another.

[0032] A further aspect of the invention relates to a drive train for an industrial wind turbine, comprising a wind turbine gearbox, which can be designed and further developed as described above, for transmitting power along a power flow leading from a wind-driven rotor to a generator, and a lubrication arrangement for lubricating bearing points and / or tooth meshes of the wind turbine gearbox, wherein, in particular, a flow direction of the lubricant transferred from the lubrication arrangement via the fluid transfer device is oriented counter to the power flow direction. The drive train can be designed and further developed, in particular, as explained above with reference to the other aspects.The hollow pin that penetrates into the annular chamber and the axially spaced seal on the first plain bearing surface allow for a good and long-lasting seal of the annular chamber even with installation tolerances, thus enabling low-maintenance and / or low-leakage fluid transfer between relatively rotating components of the drive train.

[0033] A further aspect relates to a wind turbine for the industrial generation of energy from wind power, comprising a tower, a nacelle attached to an upper end of the tower, a wind-driven rotor, an electric machine operable in generator mode, and a drive train accommodated by the nacelle, which can be designed and developed as described above for the torque-transmitting coupling of the rotor to the electric machine and for converting a torque introduced by the rotor. The wind turbine can be designed and developed in particular as explained above with reference to the other aspects.The hollow pin that penetrates into the annular chamber and the axially spaced seal on the first plain bearing surface ensure a good and long-lasting seal of the annular chamber even with installation tolerances, thus enabling low-maintenance and / or low-leakage fluid transfer between relatively rotating components of the wind turbine.

[0034] A further aspect relates to an industrial application. The industrial application can have a drive means, which 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 a transmission for converting a torque and a speed of the power generated by the drive means, wherein the transmission can be designed and developed analogously to the wind turbine transmission as explained above. In particular, the industrial application has a fluid transfer device, which can be designed and developed as described above. The transmission of the industrial application can in turn be coupled in a torque-transmitting manner to a mechanical application in which mechanical energy introduced via the transmission can be used.The mechanical application could be, 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, garbage compactor, scrap press, shredder for recyclable materials from, possibly previously separated and / or sorted, waste, or similar. The industrial application can be designed and developed in particular as explained above with reference to the other aspects. The hollow pin immersed in the annular chamber and the axially spaced seal on the first plain bearing surface enable a good and long-lasting seal of the annular chamber even with installation tolerances, thus enabling low-maintenance and / or low-leakage fluid transfer between relatively rotating components of the industrial application.

[0035] One aspect further relates to a 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 fluid transfer device, 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 manufacture 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 technical simulation with the aid of the data processing device for the device according to the invention.

[0036] 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 respect 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 using 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.

[0037] 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.

[0038] 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.

[0039] The data agglomerate enables the cost-effective production of prototypes and / or computer-based simulations to study the functionality of the rotating body and / or the holding tool, 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.

[0040] The invention will be explained below by way of example with reference to the accompanying drawings using preferred embodiments, wherein the features presented below can represent an aspect of the invention both individually and in combination. They show:

[0041] Fig. 1 : a schematic perspective view of a wind turbine,

[0042] Fig. 2: a schematic sectional view of a fluid transfer device for the wind turbine from Fig. 1,

[0043] Fig. 3: a schematic detailed view of the fluid transfer device from Fig. 2,

[0044] Fig. 4 is a schematic radial plan view of a first embodiment of a support ring of the fluid transfer device from Fig. 2,

[0045] Fig. 5 is a schematic radial plan view of a second embodiment of a support ring of the fluid transfer device from Fig. 2,

[0046] Fig. 6 is a schematic radial plan view of a third embodiment of a support ring of the fluid transfer device from Fig. 2,

[0047] Fig. 7: a schematic perspective view of a further development of the embodiments of the support ring shown in Fig. 4 to Fig. 6 and Fig. 8: a schematic detailed view of an alternative fluid transfer device for the wind turbine from Fig. 1.

[0048] The wind turbine 10 shown in Fig. 1 can be used for the industrial generation of electrical energy from wind power. For this purpose, the wind turbine 10 has a rotor 12 that can be rotated by wind power. The rotor 12 is coupled to a drive train 14. For this purpose, the rotor 12 is connected to a rotor shaft 16, which is coupled within the drive train 14 to a gearbox 18 in order to convert the torque introduced via the rotor 12 and the 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.

[0049] The fluid transfer device 26 shown in Fig. 2 can in particular be part of the transmission 18. However, it is also possible to use the fluid transfer device 26 for a different transmission, an industrial application or other device in which a fluid is to be transferred between components that can rotate relative to one another. In the illustrated embodiment, the fluid transfer device 26 has a first component 28, which can be a stationary part of a housing of the transmission 18. A second component 30, which can be a planet carrier of a gear stage of the transmission 18, can rotate relative to the first component 28. Formed in the first component 28 is an annular chamber 32 that is closed in the circumferential direction, has a substantially U-shaped cross-section and is open towards an end face 34 of the first component 28.A lubricant, in particular lubricating oil, can be supplied to the annular chamber 32 via a fluid line (not shown), which is to be transferred to a fluid channel 36 for lubrication and / or cooling on the second component 30, in particular bearing points and / or gear engagements.

[0050] A hollow pin 38 is screwed to the second component 30, which communicates fluidically on the one hand with the fluid channel 36 of the second component 30 and on the other hand with the annular chamber 32 of the first component 28. For this purpose, the hollow pin 38 dips into the volume of the annular chamber 32. A cover 46 composed of an inner ring 40 and an outer ring 44 radially spaced apart by a gap 42 can cover part of the annular chamber 30. The cover 46, in particular both the inner ring 40 and the outer ring 44, have a fastening opening 48 with an internal thread, into which a screw can be screwed from a rear side of the first component 28 through an associated bore 50 in order to screw the cover 46 to the first component 28. The bore 50 can alternatively be part of a protruding flange of the first component 28.

[0051] The cover 46 can, in particular, captively retain the hollow pin 38, which passes through the intermediate space 42, in the annular chamber 32. For this purpose, a support ring 52 is provided, which is supported and preloaded on the hollow pin 38 via a spring element 54. As shown in Fig. 3, the hollow pin has an outwardly projecting collar 56 at its end extending into the annular chamber, to which the spring element 54 is supported or fastened, for example by hooking. The support ring 52 can captively engage behind the collar 56 on the side facing the second component 30. In this case, a receiving chamber 58 for the spring element 54 can be left free between the collar 56 and the engaging part of the support ring 52. The spring element 54 can be supported on the engaging part of the support ring 52 or fastened, for example by hooking.In the axial direction outside the receiving chamber 58, an annular gap 60 can be formed between the hollow pin 38 and the support ring 52, the gap height and axial extent of which are dimensioned in particular such that a predefined angular deviation of the hollow pin 38 relative to the first component 28 and indirectly also to the support ring 52 can be permitted, while preferably at least in one of the annular gaps 60, leakage of lubricant into the receiving chamber 58 and / or out of the annular chamber 32 can be avoided. In particular, it is possible to provide an elastically deformable annular seal 62 in at least one of the annular gaps 60, which in the illustrated embodiment is inserted in a sealing groove 64 of the support ring 52.

[0052] The support ring 52 can be pressed against the cover 46 by the spring force of the spring element 54, thereby indirectly supporting the hollow pin 38 on the cover 46 via the spring element 54 and the support ring 52. The cover 46 has a first plain bearing surface 66 on both the inner ring 40 and the outer ring 44, against which a corresponding second plain bearing surface 68 of the support ring 52 is pressed. The first plain bearing surface 66 and the pressed-on second plain bearing surface 68 form an axial plain bearing 70, which, on the one hand, permits a sliding relative movement and, on the other hand, forms a fluid-tight seal for the lubricant, particularly through deliberate oversizing of the plain bearing surfaces 66, 68.The sealing effect of the axial plain bearing 70 can be influenced not only by the size of the surface contact, but also by the contact pressure of the support ring 52. The contact pressure of the support ring 52 depends on the spring force and the spring characteristic of the spring element 54, but also on the internal pressure of the lubricant within the annular chamber 32. The sealing effect of the axial plain bearing 70 is therefore dependent on the internal pressure of the annular chamber 32 to be sealed and is therefore self-reinforcing.

[0053] A plurality of hollow pins 38 can be provided offset in the circumferential direction, which are preferably arranged evenly distributed in the circumferential direction. However, it is also possible to provide a fastening element, in particular designed as a relief pin, offset from the illustrated hollow pin 38, which preferably has essentially the same outer contour as the hollow pin 38 in order to increase stability and strength, whereby in particular breaking and / or shearing of the hollow pin 38 under load can be prevented. The support ring 52 can in particular be composed of a plurality of support ring segments 72 following one another in the circumferential direction to form a circular ring. As shown in Fig. 4, Fig. 5 and Fig. 6, a sealing gap chicane 74 can be formed between the tangential sides of the support ring segments 72, which can form an adequate seal against leakage of the lubricant.Depending on the expected maximum internal pressure in the annular chamber 32 and / or the material properties of the lubricant, the sealing gap baffle 74 can be designed to be more or less complex in order to provide a sufficient sealing effect. A seal (not shown) can also be provided between the cover 46 and the end face 34 of the first component if the contact pressure and surface contact of the cover 46 on the end face 34 are found to be insufficiently tight.

[0054] In the embodiment of the support ring 52 shown in Fig. 7, the sealing gap baffle 74 of the support ring 52 shown, for example, in Fig. 4, Fig. 5 or Fig. 6 is covered by a particularly substantially U-shaped cover element 76. The cover element 76 and the sealing gap baffle 74 to be covered are positioned offset in particular in the circumferential direction relative to the hollow pins 38 and / or relief pins. The cover element 76 can lengthen the sealing gap of the sealing gap baffle 74 and improve the sealing effect. In particular, the cover element 76 is fastened to one support ring segment 72 or to both support ring segments 72, whereby the stability of the support ring 52 composed of the plurality of support ring segments 72 is improved.

[0055] In the embodiment of the fluid transfer device 26 shown in Fig. 8, in comparison to the fluid transfer device 26 shown in Fig. 2, the bore 50 is not designed as a through-bore, but as a blind hole with an internal thread open towards the second component 30. The cover 46 can be screwed to the bores 50 via screws 78, in particular screws that are at least partially countersunk into the material. So that the hollow pin 38 and / or the relief pin can be screwed to the second component 28, the first component 28 can have a passage 80 that communicates with the annular chamber 32 and is provided as an axial extension of the hollow pin 38 or the relief pin, through which a tool can be passed.The tool can be guided through the passage 80 to a head contour 82, for example a hexagon, of the hollow pin 38 or the relief pin, which adjoins the collar 56, in order to screw the hollow pin 38 or the relief pin together. After screwing, the passage 80 can be closed and sealed with a filling material 84, for example a plug or a potting compound.

Claims

P a t e n t a n s p r ü c h e 1. A fluid transfer device (26) for transferring a lubricant, in particular within a wind turbine gearbox (18) for an industrial wind turbine (10), comprising a first component (28), a second component (30) rotatable relative to the first component (28), an annular chamber (32) formed on an end face (34) of the first component (28) facing the second component (30) for receiving the lubricant, at least one hollow pin (38) connected to the second component (30) and axially immersed in the annular chamber (32) for fluidic communication between the annular chamber (32) and a fluid channel (36) of the second component (30), and a cover (46) connected to the first component (28) for captively retaining the hollow pin (38) in the annular chamber (32), wherein the cover (46) forms a first sliding bearing surface (66) and the hollow pin (38) is connected via a second sliding bearing surface (68) to the first Plain bearing surface (66) is axially supported.

2. Fluid transfer device (26) according to claim 1, wherein the second sliding bearing surface (68) is formed by a support ring (52) which is axially movable relative to the hollow pin (38), the support ring (52) being coupled to the hollow pin (38) via a spring element (54).

3. Fluid transfer device (26) according to claim 2, wherein a receiving chamber (58) encapsulated by the support ring (52) and the hollow pin (38) is formed between the support ring (52) and the hollow pin (38), wherein the spring element (54) is at least largely received in the receiving chamber (58).

4. Fluid transfer device (26) according to claim 2 or 3, wherein the support ring (52) has a through opening for at least a part of the hollow pin (38), wherein at least one axially extending annular gap (60), preferably at least two axially spaced annular gaps (60), is formed between the support ring (52) and the hollow pin (38), wherein in particular the annular gap (60) is dimensioned to allow an angular deviation Aa of the hollow pin (38), wherein in particular 0.01° < Aa < 2.0°, preferably 0.02° < Aa < 1.0° and particularly preferably 0.05° < Aa < 0.5° applies.

5. Fluid transfer device (26) according to one of claims 2 to 4, wherein the hollow pin (38) is sealed to the support ring (52) via an annular seal (62) or membrane that is elastically deformable in the radial direction.

6. Fluid transfer device (26) according to one of claims 2 to 5, wherein the support ring (52) is composed of a plurality of support ring segments (72) following one another in the circumferential direction, wherein the support ring segments (72) form a sealing gap chicane (74), in particular a labyrinth seal, on their tangential sides facing one another.

7. Fluid transfer device (26) according to one of claims 2 to 6, wherein the support ring (52) is fastened to the second component (28) and / or guided in translation via at least one fastening element, in particular a relief pin corresponding to the outer contour of the hollow pin (38).

8. Fluid transfer device (26) according to one of claims 1 to 7, wherein the cover (46) has an inner ring (40) and an outer ring (44), wherein the hollow pin (38) is guided through an intermediate space (42) between the inner ring (40) and the outer ring (44), wherein in particular a passage surface remaining in the intermediate space (42) is closed by the support ring (52).

9. Fluid transfer device (26) according to one of claims 1 to 8, wherein the cover (46) is fastened to the first component (28) via a fastening means, wherein the fastening means, in particular a screw, is guided from an axial side facing away from the second component (30) through an opening (50) of the first component (28) to the cover (46).

10. Fluid transfer device (26) according to one of claims 1 to 9, wherein the first sliding bearing surface (66) and / or the second sliding bearing surface (68) is / are positioned completely within the annular chamber (32) extending to the end face (34) of the first component (28).

11. Fluid transfer device (26) according to one of claims 1 to 10, wherein the cover (46) is centered on the annular chamber (32) via a centering bevel.

12. Fluid transfer device (26) according to one of claims 1 to 11, wherein a seal is pressed between the cover (46) and the end face (34) of the first component (28).

13. Wind power gearbox (18) for an industrial wind turbine (10), with a gear stage designed as a planetary gear and a fluid transfer device (26) according to one of claims 1 to 12, wherein the second component (30) of the fluid transfer device (26) is formed by a planet carrier of the gear stage and the first component (28) is formed by a stationary housing or a rotating gear component, in particular a further planet carrier, of a further gear stage following in the direction of power flow.

14. Drive train (14) for an industrial wind turbine (10), with a wind turbine gearbox (18) according to claim 13 for power transmission along a power flow leading from a wind-driven rotor (12) to a generator (20) and a lubricating arrangement for lubricating bearing points and / or tooth engagements of the wind turbine gearbox (18), wherein a flow direction of the lubricant transferred from the lubricating arrangement via the fluid transfer device (26) is oriented counter to the force flow direction.

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 fluid transfer device (26) according to one of claims 1 to 12, wherein the data packets are prepared to carry out an additive production of the components of the fluid transfer device (26), 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 fluid transfer device (26) 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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