Lubricating oil system for torque transmitting couplings of pressurized lubricated transmissions
By designing a lubricating oil system that includes feed channels, supply channels, and return channels, wear particles can be discharged when the lubricating oil is not fully pressurized, thus solving the problem of wear particles entering the gearbox and extending the service life of the gearbox.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- FLENDER GMBH
- Filing Date
- 2024-12-02
- Publication Date
- 2026-07-14
AI Technical Summary
In the prior art, if the lubricating oil is not pressurized sufficiently or not pressurized at all, wear particles will enter the gearbox, reducing its service life.
A lubrication system was designed, comprising a feed channel, a supply channel, and a return channel. Pressurized lubrication is achieved through a gap seal, and wear particles are discharged by gravity to prevent them from entering the gearbox.
It effectively prevents wear particles from damaging the gearbox and extends its service life, especially when the conveying pressure is insufficient, it can also effectively discharge wear particles.
Smart Images
Figure CN122396881A_ABST
Abstract
Description
Technical Field
[0001] This invention relates to a lubrication system that enables pressurized lubrication of the torque transmission coupling in a gearbox. The invention also relates to gearboxes having such a lubrication system, particularly wind turbine gearboxes and industrial gearboxes, and to a data aggregate through which such devices can be produced and simulated. Background Technology
[0002] WO 2015 / 032591 A1 and US 2018 / 0274663 A1 disclose a lubricating oil system in which pressurized lubricating oil for gear coupling formed between two gearbox components of different gearbox stages of a wind turbine gearbox can be pumped through a static gearbox housing and enters an oil guide passage formed in the gearbox component and leading to the gear coupling through a gap seal formed between the gearbox housing and the rotating gearbox component.
[0003] DE 10 2015 216 369 A1 discloses a lubrication system for lubricating a gear coupling between the sun shaft and planetary carrier of a planetary gearbox of a wind turbine, wherein lubricating oil is transferred from a static housing via a clearance seal to a retaining ring that is screwed onto the planetary carrier and leads to the gear coupling.
[0004] The service life of pressure-lubricated gearboxes needs to be extended. Summary of the Invention
[0005] The purpose of this invention is to specify measures that enable a long service life for pressure-lubricated gearboxes.
[0006] This objective is achieved by a lubricating oil system having the features of claim 1, a gearbox having the features of claim 12, a wind turbine gearbox having the features of claim 13, an industrial gearbox having the features of claim 14, and a data aggregate having the features of claim 15. The dependent claims and the following description specify preferred improvements, which may each constitute an aspect of the invention individually or in combination, the scope of which is defined by the claims. Where one feature is presented in combination with another, this is merely for the purpose of simplifying the presentation of the invention and is in no way intended to imply that said feature cannot be an improvement of the invention in the absence of the other features.
[0007] One aspect of the invention relates to a pressurized lubricating oil system for a torque transmission coupling of a gearbox, the gearbox having a static gearbox housing having a feed channel for feeding pressurized lubricant; a first gearbox component rotatable relative to the gearbox housing having a supply channel fluidly in communication with the feed channel via a clearance seal for receiving lubricating oil fed via the feed channel and the clearance seal; and a second gearbox component torque-transmittingly coupled to the first gearbox component via the coupling, wherein the supply channel is designed to guide the lubricating oil to the coupling, wherein the gearbox housing has at least one return channel fluidly in communication with the clearance seal for gravity-driven discharge of the lubricating oil from the clearance seal.
[0008] If, for example, lubricating oil is fed into the feed channel at a sufficiently high delivery pressure via an oil pump, the clearance seal provides such high flow resistance that virtually the entire mass flow of oil can be transferred from the feed channel of the static gearbox housing to the supply channel in the rotatable first gearbox component. Leakage of lubricating oil via the clearance seal is generally negligible. Pressurized lubricating oil can exit the supply channel near the torque transmission coupling (especially if designed as a gear coupling) and can flow through the torque transmission coupling to lubricate between the first and second gearbox components. After passing through the torque transmission coupling, the lubricating oil exiting the coupling can be collected and fed into an oil sump, from which the oil pump can pump the lubricating oil back into the feed channel. If wear or other contamination of the lubricating oil occurs in the torque transmission coupling due to unavoidable wear effects, the worn material can be flushed out of the torque transmission coupling by the pressurized lubricating oil and can deposit on the base of the oil sump. By properly shaping the oil sump, arranging the oil pump inlet opening within the sump, and / or employing suitable filtration techniques, it is easy to prevent wear material deposited on the base from being sucked into the pump. Although wear occurs in the torque transmission coupling, damage to other pressure-lubricated components caused by wear particles from the torque transmission coupling can be reliably prevented during expected normal operation.
[0009] However, it has been found that during continuous operation of the gearbox, situations may repeatedly occur where the lubricating oil is not pressurized or is not sufficiently pressurized. For example, when the gearbox is stationary and / or during idling and / or overspeed operation, the power branched from the gearbox for the purpose of operating the oil pump may be insufficient to establish the desired delivery pressure of the lubricating oil. This can have the effect that, under the resulting tribological conditions, the oil mass flow can occur from the torque transmission coupling to the clearance seal in the opposite direction to the expected flow direction, especially if the oil mass flow is driven by gravity radially outward from the radially inward direction via the supply channel to the clearance seal. Therefore, hydrostatic pressure can accumulate within the supply channel at the inlet facing the clearance seal, forcing the lubricating oil into the clearance seal. Here, wear particles from the torque transmission coupling may pass through the clearance seal along with leaking lubricating oil and enter the gearbox, potentially causing damage and reducing the gearbox's service life.
[0010] However, by means of a return channel in fluid communication with the clearance seal, this leakage flow of lubricating oil carrying wear particles from the torque transmission coupling can be discharged from the clearance seal before the wear particles can be transmitted from the leaking lubricating oil to locations detrimental to the gearbox's service life. Gravity in the return channel is sufficient to discharge the leakage flow, eliminating the need for actively generating delivery pressure, for example, via a pump. Instead, it is sufficient for the return channel to lead to the clearance seal at a location where gravity-driven discharge of the collected lubricating oil is possible without an external energy supply. The production cost for creating a suitable return channel is very low, involving at most low cost. Lubricating oil creeping into the clearance seal from the feed and / or supply channels can be discharged via the return channel before the lubricating oil can pass through the clearance seal over the entire axial range. With the aid of the lubricating oil system's return channel, lubricating oil contaminated with wear particles from the torque transmission coupling can be discharged by gravity under operating conditions where the delivery pressure is too low, thus preventing damage caused by wear particles and enabling a long service life for pressure-lubricated gearboxes.
[0011] Torque transmission couplings can be specifically designed as geared couplings. Here, the torque transmission connection between the first gearbox component and the second gearbox component can be generated by the meshing of internal and external teeth or other mutually meshing shape-fitting profiles, due to the axial relative movement between the first and second gearbox components during the assembly and production of the torque transmission coupling. During the assembly process, due to the axial relative movement, the contact surfaces that abut against each other in the circumferential direction may slide against each other in a manner involving wear, and the resulting wear leads to the presence of wear particles in the torque transmission coupling. Clearance may exist in the torque transmission coupling in the axial and / or circumferential directions, which can cause wear effects, especially during load reversal events; however, this wear can be at least significantly reduced by means of supplied lubricating oil.
[0012] The gearbox may have at least one gearbox stage, preferably at least two, at least three, or at least four gearbox stages. Each gearbox stage may be formed from a planetary gearbox or a spur gearbox. Each gearbox stage is particularly housed in the same, optionally multi-part, gearbox housing, wherein preferably, the static ring gear of the gearbox stage designed as a planetary gearbox may form part of the gearbox housing and / or part of the outer skin of the gearbox housing. The lubrication system is preferably formed by two consecutive gearbox stages in the torque direction of the gearbox, wherein if a correspondingly large number of gearbox stages exist, more than one lubrication system according to the invention may be provided in the gearbox, wherein the lubrication systems may each be designed as separate and functionally independent units, or may be designed as units fluidly connected to each other and preferably sharing the same oil pump.
[0013] In the system under consideration, the gearbox housing is a static and non-rotating component in which the gearbox stages can be housed and mounted. For example, the gearbox housing may be split in a horizontal and / or radial plane to allow access to a volume enclosed within it. The gearbox housing may be specifically secured to the ground, such as to a foundation, or to a machine support within the nacelle of a wind turbine. The gearbox housing may be specifically formed with an oil sump in which lubricating oil for the lubrication system can be collected and optionally cooled. An oil pump may pump lubricating oil from the oil sump into the feed channel at a desired delivery pressure.
[0014] The oil pump, which can pump pressurized lubricant into the feed channel, is preferably mechanically connected to the gearbox of the lubrication system, so that the delivery power for operating the oil pump can be branched from the power flow in the gearbox.
[0015] The first and second gearbox components can be, in particular, functional components of a gearbox stage designed as a planetary gearbox or spur gearbox. The first and second gearbox components are specifically part of corresponding different gearbox stages, but theoretically they can be part of the same gearbox stage. Preferably, the first gearbox component is the hub of the planet carrier of a gearbox stage downstream in the torque flow and designed as a planetary gearbox, while the second gearbox component is the sun shaft of a gearbox stage upstream in the torque flow and designed as a planetary gearbox, and vice versa. The first and / or second gearbox components are particularly designed as hollow shafts, at least in the axial sub-region.
[0016] The gap seal between the gearbox housing and the first gearbox component can be designed as a non-contact seal with an annular gap that is circumferential in the circumferential direction and extends in the axial direction. The radial clearance provided by the annular gap is sized such that sufficient sealing action is achieved by utilizing the expected material properties of the lubricant, the axial range of the gap seal, and the geometry of the feed and supply channels. This sealing action allows at most a small leakage flow during expected normal operation, which is acceptable at this level.
[0017] The feed channel may begin at a surface of the gearbox housing, specifically facing the internal volume of the gearbox housing. For example, the gearbox housing may have radially inwardly projecting ribs by which a first gearbox component and / or a second gearbox component will be directly or indirectly supported, such that the ribs form a surface at least facing the components in the axial direction, and the feed channel may begin at this surface. The feed channel may open at its end to an annular gap of a clearance seal and end there. The feed channel may consist of multiple sub-sections, each formed individually, for example, by drilling, but the entire feed channel may also be formed from its beginning to its end in a single production step. Optionally, another channel may travel from the feed channel to at least one other lubrication point, such that the mass flow of lubricant can be distributed and branched between two or more channel components.
[0018] The supply channel may begin at the outer surface of the first gearbox component facing the clearance seal and may terminate near the torque transmission coupling, particularly from the radially outer side of the torque transmission coupling and / or from the axial end of the torque transmission coupling, allowing lubricating oil to enter the torque transmission coupling from the supply channel. Preferably, multiple supply channels are arranged, for example, in a star configuration in a common axial region. Additionally or alternatively, multiple supply channels adjacent to each other in the axial direction may also be provided. With multiple supply channels, lubrication in the torque transmission coupling can be homogenized and improved. The delivery pressure of the pressurized lubricating oil is specifically configured to be sufficiently high so that, within the expected rotational speed range during normal operation, the effects of centrifugal force on the lubricating oil in the supply channel can be at least compensated. The delivery pressure of the pressurized lubricating oil can be significantly higher than the back pressure caused by centrifugal force.
[0019] The return channel may begin on the inner side of the gearbox housing facing the clearance seal and lead indirectly or directly to a region lower in the direction of gravity, particularly to the oil groove formed by the gearbox housing. Lubricating oil discharged via the return channel can preferably be guided via a filter, so that wear particles in the lubricating oil located in the return channel can be filtered out, and thus the filtered lubricating oil can be reused in the lubrication system. Preferably, the return channel extends forward from the clearance seal with only a component in the direction of gravity.
[0020] Due to the inherent weight of the lubricating oil and the resulting hydrostatic pressure, gravity-driven discharge of the lubricating oil is possible. Specifically, when the gearbox is stationary or at a correspondingly low rotational speed, there is no centrifugal effect, or not a sufficiently strong centrifugal effect, to adequately counteract the gravity-driven discharge of the lubricating oil. Furthermore, when the gearbox is stationary or at a correspondingly low rotational speed, the driving force supplied to the oil pump is not high enough for the delivery pressure accumulated by the oil pump to adequately counteract the gravity-driven discharge of the lubricating oil.
[0021] Specifically, the at least one return channel is axially offset relative to the supply channel toward the gap seal. During normal operation, leakage of lubricating oil via the return channel can be prevented by the sealing barrier effect of the gap seal. Therefore, the discharge of lubricating oil via the return channel only occurs under operating conditions where the lubricating oil can actually pass through the correspondingly long axial section of the gap seal. It is assumed that the delivery pressure of the pressurized lubricating oil when delivering the lubricating oil from the feed channel to the supply channel is high enough that a suction-jet effect occurs in the gap seal. As the lubricating oil flows over those axial edges of the gap seal facing the feed and supply channels, these suction-jet effects create a negative pressure in the annular gap of the gap seal, and thus any lubricating oil that has entered the annular gap of the gap seal can be drawn out of the annular gap against any major capillary force. If the delivery pressure of the pressurized lubricating oil is so low that this suction-jet effect no longer occurs, and the delivery pressure is also so low that there is a risk of lubricating oil contaminated with wear particles flowing back into the annular gap, but this lubricating oil can be discharged in a timely manner through the axially offset return channel. Particularly preferred is that at least one return channel is offset in one axial direction relative to the feed channel and relative to the supply channel, and at least another return channel is offset in the opposite axial direction relative to the feed channel and relative to the supply channel.
[0022] Preferably, the first gearbox component has a groove in fluid communication with a clearance seal, wherein a return channel is indirectly in fluid communication with the clearance seal via the groove, and due to the groove, the clearance depth of the clearance seal in the radial direction is greater in the axial region occupied by the groove than in the axial region of the adjacent groove of the clearance seal. The clearance depth in the radial direction and the clearance width in the axial direction of the groove can be sufficiently large so that lubricating oil that has entered the clearance seal can be collected in the groove and discharged via a return channel fluidly connected to the groove. The groove can also be in the form of a circumferential extension. However, if a portion of the groove is fluidly connected to the return channel and preferably includes a minimum circumferential point as observed in the direction of gravity, the groove can also extend only partially in the circumferential direction. A groove extending only partially in the circumferential direction may be sufficient, especially if the first gearbox component automatically presents a defined zero position in the circumferential direction when the gearbox is stationary.
[0023] The gearbox housing particularly preferably has at least one lubrication channel fluidly connected to the supply channel for lubricating at least one lubricating oil consumption device, wherein, in particular, the lubricating oil consumption device is fluidly in communication with a clearance seal. By means of the lubrication channel branching from the feed channel, a proportion of pressurized lubricating oil can be delivered to the lubricating oil consumption device, such as a bearing to be lubricated, rather than to a torque transmission coupling. The bearing can be, in particular, a rolling bearing or a sliding bearing. Lubrication of the lubricating oil consumption device via leakage flow through the clearance seal can be avoided. Instead, by means of the geometry of the lubrication channel and knowing the expected delivery pressure and the geometry of the feed channel, the mass flow rate of lubricating oil to the lubricating oil consumption device can be precisely specified. As an alternative to or supplement to the lubrication channel, the gearbox housing may have an additional lubrication channel fluidly connected to the lubricating oil consumption device separately from the feed channel, wherein the additional lubrication channel is preferably supplied with lubricating oil by the same lubricating oil pump as the feed channel. This allows the feed channel and the additional lubrication channel to be sized independently of each other, such that an effect on the mass flow rate in one channel has substantially no effect on the mass flow rate in the other channel.
[0024] Specifically, the return channel leads to the gap seal axially between the supply channel and the lubricating oil consumption device. Therefore, the lubricating oil consumption device is protected from contamination by wear particles in the leaking flow from the supply channel through the gap seal to the lubricating oil consumption device, because the lubricating oil contaminated with wear particles can be pre-discharged via the return channel and does not reach the lubricating oil consumption device first.
[0025] The lubricating oil consumption device is preferably designed as a pressure-lubricated bearing for mounting the first gearbox component onto the gearbox housing. The bearing can be, in particular, a rolling bearing or a sliding bearing. For example, a clearance seal terminates in both axial directions at the bearing (especially an angular contact rolling bearing) through which the first gearbox component is mounted onto the gearbox housing. Damage to the (sliding) bearing surface from wear particles from the torque transmission coupling is avoided by means of a return channel.
[0026] Particularly preferably, the coupling at the output side of the torque transmission coupling, which is offset from the supply channel, and the return channel are in fluid communication with the oil sump. Whether the lubricating oil flows via the torque transmission coupling during normal operation or via the return channel during operation with insufficient delivery pressure, the lubricating oil can be collected in the oil sump and reused therefrom. The mass transfer of lubricating oil from the torque transmission coupling and from the return channel to the oil sump can be gravity-driven. For example, if the collection area is not yet part of the oil sump itself, the lubricating oil can drip from the outlet side of the torque transmission coupling and be guided from the collection area to the oil sump. For example, if the return channel does not yet lead to the oil sump itself, the return channel can lead to a discharge channel leading to the oil sump.
[0027] Specifically, when viewed along the direction of gravity, the return channel leads to the clearance seal at the lowest point on the circumference of the first gearbox component. This prevents residual lubricating oil from remaining in the clearance seal. Consequently, the hydrostatic pressure of the fluid in the return channel is maximized.
[0028] Preferably, an annular groove is formed in the first gearbox component or gearbox housing between the feed channel and the supply channel. This annular groove is in fluid communication with a clearance seal and extends circumferentially to transfer lubricating oil between the feed channel and the supply channel. The annular groove compensates for the circumferential offset of the supply channel, which rotates with the first gearbox component, relative to the feed channel formed in the gearbox housing for stationary operation. Therefore, the supply channel can be filled with lubricating oil having substantially the same or at least uniform delivery pressure and mass flow rate, thereby avoiding or at least reducing pressure pulsations and vibrations.
[0029] The first gearbox component is particularly preferably designed as a first shaft of a first gearbox stage rotatable about the main rotational axis, wherein, in particular, the second gearbox component is designed as a second shaft rotatable about the main rotational axis, wherein preferably, the second shaft is part of a gearbox stage other than the first gearbox stage, or part of the first gearbox stage. This makes it easier to design the torque transmission coupling between the first and second gearbox components as a toothed coupling.
[0030] Specifically, measures are provided such that, in the unloaded state, the coupling substantially allows at least limited, wear-affected relative movement of the first gearbox component relative to the second gearbox component in the axial and / or circumferential directions. This wear-affected relative movement is permitted at least during assembly and possibly during load reversal events during ongoing operation, as the resulting wear particles can be directly flushed away by the mass flow of lubricating oil during normal operation, or discharged via a return channel in the event of insufficient delivery pressure. This allows for the provision of an inexpensive torque transmission coupling with relatively low material requirements, without the gearbox service life being adversely affected by wear.
[0031] On the other hand, a gearbox for converting torque and / or rotational speed is provided, the gearbox having at least one gearbox stage and a lubrication system, which can be designed and modified as described above for pressurized lubrication of at least one gearbox stage. Preferably, the at least one gearbox stage is designed as a planetary gearbox, and further preferably, the planetary gears are lubricated with pressurized lubricating oil via planetary channels, wherein, in particular, the planetary channels are in fluid communication with the feed channel indirectly or bypassing the supply channel. The pressurized lubricating oil fed in the feed channel can also be used to lubricate at least one planetary gear rotatably mounted on a planetary carrier. Here, in principle, there is design freedom to design the fluid connection of the planetary channels such that lubricating oil branches from the feed channel or from the supply channel to the planetary channels. The gearbox can be designed and modified in particular as described above. By means of the return channel of the lubricating oil system, in operating conditions where the delivery pressure is too low, lubricating oil contaminated by wear particles from the torque transmission coupling can be discharged by gravity, thereby avoiding damage caused by wear particles and enabling a long service life of the pressure-lubricated gearbox.
[0032] On the other hand, a wind turbine gearbox for a wind turbine is provided, comprising a lubrication system and / or a gearbox, the lubrication system being designed and modified as described above for pressurized lubrication, and the gearbox being designed and modified as described above for torque and / or rotational speed conversion. Specifically, an input coupling for connecting the wind turbine rotor shaft and / or an output coupling for connecting the generator is provided, the wind turbine rotor shaft being provided to introduce torque generated by wind power, and the generator being provided for industrial power generation. The wind turbine gearbox can be designed and modified specifically as described above. The size of the wind turbine gearbox can be designed for industrial power generation, and for this purpose, it can be designed to be correspondingly large, stable, and heavy. By means of a return channel in the lubrication system, in operating conditions where the delivery pressure is too low, lubricating oil contaminated by wear particles from the torque transmission coupling can be discharged by gravity, thus avoiding damage caused by wear particles and enabling a long service life for the pressure-lubricated wind turbine gearbox.
[0033] The wind turbine is specifically designed as an industrial wind turbine. Industrial wind turbines are primarily designed to generate energy from wind power, with the electricity generated from the wind specifically designed to be fed into the public power grid so that renewable energy can be supplied to energy consumers. The wind turbine gearboxes designed for industrial wind turbines are specifically designed for power outputs exceeding 1.0 MW, preferably exceeding 5.0 MW, and particularly preferably exceeding 7.5 MW, and are accordingly designed to be robust and large in size.
[0034] Another aspect of the invention relates to a drivetrain for a wind turbine, the drivetrain having a rotor shaft connectable to a wind-driven rotor, a motor shaft for operation in generator mode, and a gearbox that torque-transmittingly connects the rotor shaft to the motor shaft, and can be particularly designed and modified as described above for converting torque and rotational speed. The drivetrain can be particularly designed and modified as described above, wherein the drivetrain is specifically designed and sized for use in industrial wind turbines. By means of a return channel in the lubricating oil system, lubricating oil contaminated by wear particles from the torque-transmitting coupling can be discharged by gravity under operating conditions where the delivery pressure is too low, thereby avoiding damage caused by wear particles and enabling a long service life for the pressure-lubricated drivetrain.
[0035] Another aspect of the invention relates to a wind turbine for generating electrical energy from wind energy, the wind turbine having a rotor for providing torque from wind energy, a gearbox coupled to the rotor, and which can be particularly designed and modified as described above for converting torque, and having a generator for generating electrical energy from the torque introduced from the gearbox. The wind turbine can be particularly designed and modified as described above. The wind turbine preferably has a transmission system that can be designed and modified as described above. By means of a return channel in the lubricating oil system, in operating conditions where the delivery pressure is too low, lubricating oil contaminated by wear particles from the torque transmission coupling can be discharged by gravity, thereby avoiding damage caused by wear particles and enabling a long service life for the pressure-lubricated wind turbine.
[0036] On the other hand, an industrial gearbox for industrial applications is provided, comprising a lubrication system and / or a gearbox, the lubrication system being designed and modified as described above for pressurized lubrication, and the gearbox being designed and modified as described above for converting torque and / or rotational speed. Specifically, an input coupling is provided for connection to a drive motor providing driving power, and / or an output coupling is provided for connection to a mechanical working device. The industrial gearbox can be designed and modified specifically as described above. The dimensions of the industrial gearbox can be designed for power conversion in industrial applications, particularly differentiated by the extremely high power and / or torque to be transmitted, and for this purpose can be designed to be correspondingly larger, more stable, and heavier. By means of a return channel in the lubrication system, in operating conditions where the delivery pressure is too low, lubricating oil contaminated by wear particles from the torque transmission coupling can be discharged by gravity, thus avoiding damage caused by wear particles and enabling a long service life for the pressure-lubricated industrial gearbox.
[0037] Another aspect of the invention relates to industrial applications with an industrial gearbox, which can be designed and modified as described above. The industrial gearbox has at least one gearbox component to be lubricated and at least one lubricant delivery device, which can be designed and modified as described above, for delivering lubricant to the gearbox component to be lubricated. The industrial application may have a drive unit, which can be designed as, for example, an electric motor, an internal combustion engine, a hydraulic motor, or a wind-driven rotor. The drive unit can be coupled to the industrial gearbox for converting the torque and rotational speed of the power generated by the drive unit, wherein the industrial gearbox can be designed and modified as described above. The industrial gearbox of the industrial application can also be torque-transmittedly coupled to a mechanical working device, wherein mechanical energy introduced via the industrial gearbox can be utilized. Mechanical working devices include, for example, mills, vertical mills, sugar mills, cement plants, crushers, conveyor belts, pumps, roller presses, slat conveyors, pipe mills, rotary furnaces, rotary gears, agitators, lifting devices, waste compactors, waste presses, and crushing devices for recyclable materials from optionally pre-separated and / or pre-sorted waste. Industrial applications can be specifically designed and modified as described above. By means of the lubricating oil system's return channel, in operating conditions where the conveying pressure is too low, lubricating oil contaminated by wear particles from the torque transmission coupling can be discharged by gravity, thus avoiding damage caused by wear particles and enabling a long service life for pressure-lubricated industrial applications.
[0038] Another aspect of the invention relates to a data aggregate having data packets, which are combined in a common file or distributed across different files. To reproduce the three-dimensional form and / or interactions of all components provided in the lubricating oil system, which can be designed and improved as described above, or in the gearbox, which can be designed and improved as described above, the data packets are configured to perform additive manufacturing of the components of the lubricating oil system or the gearbox, particularly by 3D printing, when processed by a data processing device for performing technical simulations, and to perform simulations of the function of the lubricating oil system or the gearbox, and output simulation results generated during the simulations for further use, particularly for performing fatigue strength verification under varying loads and / or varying temperature loads and / or different tribological boundary conditions, and optionally comparing them with measurement data determined on a real device manufactured according to the invention and / or on a prototype of the device according to the invention. The data packets of the data aggregate are particularly suitable for the design according to the invention of the specific device described above, i.e., the lubricating oil system and / or gearbox, so that the interactions of the components according to the invention can be adequately reproduced when processed in the data processing device. Data packets can be stored in a spatially distributed manner, but adapted to each other, such that, with all data packets placed together in a common data processing apparatus, the compiled data aggregate provides all the data required for additive manufacturing and / or technical simulation through the data processing apparatus of the device according to the invention. For example, each data packet is a separate part of a database, which, in order to form a data aggregate, are placed together and adapted to each other in a manner corresponding to a particular device according to the invention, with respect to their relative size and / or absolute size and / or material properties. The data aggregate can constitute a virtual embodiment of a particular device according to the invention in a so-called "digital twin" manner, which allows for virtual inspection in the form of simulation or real representation through additive manufacturing processes. Such digital twins are presented, for example, in US 2017 / 286572 A1, the disclosure of which is incorporated herein by reference as part of this invention.
[0039] If the machine tool's data processing apparatus processes the data aggregate, then the device according to the invention is produced, such that after processing the data aggregate in the data processing apparatus, the device according to the invention is obtained at least in prototype form. Specifically, each data packet can replicate individual components of the separately associated device according to the invention, such that the individual components can be easily, practically and / or virtually assembled in terms of their relative positions and / or relative mobility to achieve the interactions essential to the invention. In particular, by means of corresponding data packets, various components of a particular device can be created individually and optionally from different materials by additive manufacturing, and then said components are assembled to form a prototype of the particular device. Thus, the distribution of data in the data aggregate across different data packets makes it easy to perform sequential additive manufacturing of the relatively movable components of a particular device in the form of component kits, which are configured to be explicitly assembled only for the interactions of the components used for the prototype according to the invention, to solve the problem on which the invention is based.
[0040] Additionally or alternatively, in the virtual environment during technical simulation, the individual components of a particular device, their interactions, physical states, and / or physical parameters of the device according to the invention can be calculated and / or predicted based on different boundary conditions and / or changes over time using data packets from the data aggregate, and reused to check whether the device according to the invention is sufficiently suitable for its intended purpose, based on the assumed design and considering the hypothetical simulation effects. If the data aggregate is processed by a data processing device that replicates the simulation environment, boundary conditions, particularly varying boundary conditions, can be considered to examine the behavior of the device according to the invention. Thus, for example, the centrifugal force effects in the individual components of the device according to the invention can be examined based on different steady-state and / or dynamic loads and / or different operating temperatures, where such simulation results can be input into the creation of fatigue strength verification. Preferably, the simulation results obtained after processing the data aggregate are stored in the data processing device for the simulation environment so that these simulation results can be compared with measurement data determined on an actual manufactured device according to the invention and / or on a prototype of the device according to the invention. Thus, the quality of the simulation results obtained through the data aggregate and / or in the presence of particularly large deviations can be evaluated to identify measurement errors and / or erroneous measurements. This simplifies and improves the non-destructive quality control of the device according to the invention.
[0041] The use of data aggregates enables inexpensive production of prototypes and / or computer-based simulations, allowing for the study of the functionality of the device under discussion, identification of problems in specific use cases, and finding improvements. Solutions to the problems upon which this invention is based can be easily and inexpensively examined using data aggregates. Attached Figure Description
[0042] The invention will now be discussed by way of example with reference to the accompanying drawings and based on preferred exemplary embodiments, wherein the features presented below can constitute an aspect of the invention individually or in combination, the scope of which is defined by the claims. In the drawings: Figure 1 A schematic perspective view of a wind turbine is shown. Figure 2 : Shows what can be used Figure 1 A schematic cross-sectional view of the upper part of the lubrication system of a wind turbine, and Figure 3 It shows Figure 2 A schematic cross-sectional view of the lower part of the lubricating oil system. Detailed Implementation
[0043] Figure 1 The wind turbine 10 shown can be used to industrially generate electricity from wind energy. For this purpose, the wind turbine 10 has a wind turbine rotor 12 that can be rotated by the force of wind. The wind turbine rotor 12 is coupled to a drivetrain 14. For this purpose, the wind turbine rotor 12 is connected to a wind turbine rotor shaft 16, which is coupled within the drivetrain 14 to a wind turbine gearbox 18 to convert the torque introduced via the wind turbine rotor 12 and the wind turbine rotor shaft 16. The torque converted in the wind turbine gearbox 18 is fed via a motor shaft to an electric motor operating in generator mode, which can form a generator 20. The electrical energy generated by the electric motor can be fed to a rechargeable battery and / or the power grid. In the exemplary embodiment shown, the drivetrain 14 is fully housed in a nacelle 22, which is mounted on the upper free end of a tower 24. The wind turbine rotor 12, the wind turbine gearbox 18, and the generator 20 can be arranged coaxially relative to each other and can preferably be tilted relative to the horizontal plane.
[0044] Figure 2 The lubrication system 26 shown is illustrated as part of the wind turbine gearbox 18, but it could also be part of an industrial gearbox (not explicitly shown) without significant structural modifications, where the power flow could be directed in the opposite direction to that in the wind turbine gearbox 18. The lubrication system 26 is designed for pressurized lubrication, in which case the lubricating oil is delivered at an elevated delivery pressure during the intended normal operation for which the lubrication system 26 is designed. For this purpose, an oil pump (not shown) can draw lubricating oil from an oil sump and deliver it to the feed channel 28 at the intended delivery pressure. The feed channel 28 is formed in the static gearbox housing 30. In the illustrated exemplary embodiment, the feed channel 28 consists of an axial bore and a radial bore, but theoretically, the feed channel 28 could consist of three or more sub-sections, or simply provide exactly one bore.
[0045] The first gearbox component 32 is rotatably mounted in the gearbox housing 30 and supported in the radial and / or axial directions by means of two axially spaced bearings 31. The bearings 31 can be designed as sliding bearings or rolling bearings, wherein in the exemplary embodiment shown, two angular contact rolling bearings are provided in an O-shaped arrangement. Preferably, the bearings 31, which serve as lubricating oil consumption devices, are lubricated by lubricating oil. For this purpose, in each case, a lubrication channel 34 can advance from the feed channel 28 and lead to the associated bearing 31, so that the bearing 31 can also be pressure lubricated.
[0046] In the illustrated exemplary embodiment, the first gearbox component 32 is designed as a hollow shaft or hub. The first gearbox component 32 may, for example, be located downstream in the torque flow and is designed as part of the planet carrier of a gearbox stage of a planetary gearbox. Between bearings 31, the first gearbox component 32 is radially separated from the gearbox housing 30 by a non-contact clearance seal 36. A feed channel 28 extends radially toward the clearance seal 36. At least one supply channel 38 is formed in the first gearbox component 32 substantially opposite the end of the feed channel 28, communicating with the feed channel 28 via an annular groove 40 and forming a lubricating oil delivery device. In the illustrated exemplary embodiment, the annular groove 40 is formed in the first gearbox component 32; however, the annular groove 40 may also be additionally or alternatively formed in the gearbox housing 30. A plurality of supply channels 38 may also be arranged continuously in the circumferential direction and / or adjacent to each other in the axial direction.
[0047] Supply channel 38 leads to the radially internal torque transmission coupling 42 of the second gearbox component 44. The torque transmission coupling 42 is specifically designed as a toothed coupling, in which case the internal teeth of the first gearbox component 32 can engage with the external teeth of the second gearbox component 44 via axial relative movement. The second gearbox component 44 may be, in particular, the sun shaft of a gearbox stage located upstream in the torque flow and designed as a planetary gearbox. Lubricating oil from feed channel 28, after being delivered to supply channel 38, can be used for pressurized lubrication of the torque transmission coupling 42.
[0048] like Figure 3 As shown, under conditions of insufficient delivery pressure, such as in a stationary state or during idling operation, lubricating oil can flow out of the torque transmission coupling 42 by gravity, allowing lubricating oil to flow into the supply channel 38 in the opposite direction of intended flow, even if the supply channel 38 is intentionally or unintentionally positioned at a circumferential angular position where the supply channel 38 is arranged at its lowest point in the direction of gravity. The lubricating oil present in the supply channel 38 provides hydrostatic pressure that forces the lubricating oil to leak into the gap seal.
[0049] To prevent potentially contaminated lubricating oil from adversely affecting bearing 31, in each case, a return channel 46 is provided axially between the fluid connection of the supply channel 38 and the associated bearing 31. This return channel is also fluidly connected to the clearance seal, particularly via a partially or fully circumferential groove. Thus, contaminated lubricating oil forced into the clearance seal can be discharged into the return channel 46, preventing it from reaching the bearing 31 axially following the clearance seal 36. Instead, the contaminated lubricating oil can be guided away from the bearing 31 via the return channel 46 and gravity-driven into the oil sump.
Claims
1. A pressurized lubricating oil system (26) for a torque transmission coupling (42) in a gearbox, It has a static gearbox housing (30), wherein the gearbox housing (30) has a feed channel (28) for feeding pressurized lubricant. It has a first gearbox component (32) capable of rotating relative to the gearbox housing (30), wherein, The first gearbox component (32) has a supply channel (38) in fluid communication with the feed channel (28) via a clearance seal (36) for receiving lubricating oil fed via the feed channel (28) and the clearance seal (36), and The system includes a second gearbox component (44) which is torque-transmitted to the first gearbox component (32) via the coupling (42), wherein the supply channel (38) is designed to guide the lubricating oil to the coupling (42). Its features The gearbox housing (30) has at least one return channel (46) in fluid communication with the gap seal (36) for gravity-driven discharge of the lubricating oil from the gap seal (36).
2. The lubricating oil system (26) according to claim 1, wherein the at least one return channel (46) is axially offset relative to the supply channel (38) and leads to the gap seal (36).
3. The lubricating oil system (26) according to claim 1 or 2, wherein the first gearbox component (32) has a groove in fluid communication with the clearance seal (36), wherein the return channel (46) is in indirect fluid communication with the clearance seal (36) via the groove, and due to the groove, the clearance depth of the clearance seal (36) in the radial direction is greater in the axial region occupied by the groove than in the axial region of the clearance seal (36) adjacent to the axial region of the groove.
4. The lubricating oil system (26) according to any one of claims 1 to 3, wherein the gearbox housing (30) has at least one lubrication channel (34) fluidly connected to the feed channel (28) for lubricating at least one lubricating oil consumption device, wherein the lubricating oil consumption device is in fluid communication with the gap seal (36).
5. The lubricating oil system (26) according to claim 4, wherein the return channel (46) is axially connected to the gap seal (36) between the supply channel (38) and the lubricating oil consumption device.
6. The lubricating oil system (26) according to claim 4 or 5, wherein the lubricating oil consumption device is designed for mounting the first gearbox component (32) on the gearbox housing (30) to a pressure-lubricated bearing (31).
7. The lubricating oil system (26) according to any one of claims 1 to 6, wherein the coupling (42) is in fluid communication with the oil sump on the output side of the torque transmission coupling (42) that avoids the supply channel (38) and the return channel (46).
8. The lubricating oil system (26) according to any one of claims 1 to 7, wherein when viewed along the direction of gravity, the return channel (46) leads to the gap seal (36) at the lowest point on the circumference of the first gearbox component (32).
9. The lubricating oil system (26) according to any one of claims 1 to 8, wherein, Between the feed channel (28) and the supply channel (38), an annular groove (40) is formed in the first gearbox component (32) or the gearbox housing (30), the annular groove (40) being in fluid communication with the gap seal (36) and extending circumferentially for conveying the lubricating oil between the feed channel (28) and the supply channel (38).
10. The lubricating oil system (26) according to any one of claims 1 to 9, wherein the first gearbox component (32) is designed as a first shaft of a first gearbox stage capable of rotating about a main rotation axis, wherein the second gearbox component (44) is designed as a second shaft capable of rotating about the main rotation axis, wherein the second shaft is part of a gearbox stage other than the first gearbox stage or part of the first gearbox stage.
11. The lubricating oil system (26) according to any one of claims 1 to 10, wherein the coupling (42) substantially allows at least limited and wear-affected relative movement of the first gearbox component (32) relative to the second gearbox component (44) in the axial and / or circumferential directions under no-load conditions.
12. A gearbox for converting torque and / or rotational speed, the gearbox having at least one gearbox stage and having a lubrication system (26) as claimed in any one of claims 1 to 11 for pressurizing lubrication of the at least one gearbox stage, wherein the at least one gearbox stage is designed as a planetary gearbox and the planetary gears are lubricated with pressurized lubricating oil via planetary channels, wherein the planetary channels are in fluid communication with the feed channel (28) indirectly or by bypassing the supply channel (38).
13. A wind turbine gearbox (18) for a wind turbine (10), comprising a lubricating oil system (26) for pressurized lubrication as claimed in any one of claims 1 to 11 and / or a gearbox for converting torque and / or rotational speed as claimed in claim 12, wherein, An input coupling is provided for a connection to a wind turbine rotor shaft (16) and / or an output coupling is provided for a connection to a generator (20), the wind turbine rotor shaft (16) being provided for introducing torque to generate wind power, and the generator (20) being provided for industrial power generation.
14. An industrial gearbox for industrial applications, the industrial gearbox having a lubrication system (26) for pressurized lubrication as claimed in any one of claims 1 to 11 and / or having a gearbox for changing torque and / or rotational speed as claimed in claim 12, wherein, An input coupling is provided for connecting a drive motor and / or an output coupling is provided for connecting a mechanical working device, wherein the drive motor is provided for introducing driving force.
15. A data aggregate having data packets, said data packets being combined in a common file or distributed across different files, for replicating the three-dimensional form and / or interactions of all components provided in a lubricating oil system (26) as claimed in any one of claims 1 to 11 or a gearbox as claimed in any one of claims 12, wherein said data packets are configured to When processed by a data processing device for additive manufacturing of equipment using machine tools, additive manufacturing of the components of the lubrication system (26) or the gearbox is performed, particularly by 3D printing. And / or, When processed by a data processing device for performing technical simulations, the function of the lubricating oil system (26) or the gearbox is simulated, and the simulation results generated during the simulation are output for further use, particularly for the purpose of performing fatigue strength verification based on varying loads and / or varying temperature loads and / or different tribological boundary conditions.