LOW-MAINTENANCE SEALING ARRANGEMENT FOR A VERTICALLY ORIENTED INDUSTRIAL GEARBOX

Description

[0001] The invention relates to a sealing arrangement for a vertically oriented industrial gearbox which is particularly low-maintenance, as well as to such an industrial gearbox.

[0002] DE 10 2013 212 464 A1 discloses an industrial gearbox with two planetary gear stages for driving a vertical mill. The planetary gear stages have vertically aligned shafts and fixed ring gears. The gear components of the planetary gear stages, which can be moved relative to one another, are lubricated with lubricating oil and sealed from the environment by a sealing arrangement.

[0003] From GB 783 118 A, a sealing arrangement, according to the preamble of claim 1, for a vertically extending turbine shaft of a gas turbine for driving a helicopter is known, wherein the turbine shaft is driven by exhaust gases from the gas turbine and is connected at one end to a compressor for supplying fresh air to the gas turbine and at the other end to a gearbox provided for driving a helicopter rotor. The turbine shaft is mounted via a rolling bearing in a stationary turbine housing. Below the rolling bearing, an annular trough is formed, from which a gap runs at an angle against the direction of gravity up to an upper end of a sleeve connected to the turbine shaft. A labyrinth seal is formed on the sleeve and has a plurality of pockets open towards the sleeve and a plurality of gap seals formed between the pockets.

[0004] There is a constant need to design industrial gearboxes to be low-maintenance and low-wear in order to minimize costly downtimes.

[0005] The object of the invention is to demonstrate measures that enable a low-maintenance industrial gearbox.

[0006] This object is achieved by a sealing arrangement having the features of claim 1 and an industrial gearbox having the features of claim 14. Preferred embodiments are specified in the subclaims and the following description, each of which, individually or in combination, may represent an aspect of the invention. If a feature is presented in combination with another feature, this merely serves to simplify the illustration of the invention and is in no way intended to imply that this feature cannot also be a further development of the invention without the other feature.

[0007] One aspect of the invention relates to a sealing arrangement for an industrial gearbox, comprising a vertically aligned lower power shaft for exchanging torque with the industrial gearbox, a gearbox component of the industrial gearbox provided radially outside the power shaft, wherein the power shaft has a higher speed than the gearbox component during normal operation, wherein a non-contact first seal is provided between the gearbox component and the power shaft, wherein the first seal has a conical first sealing gap that is bevelled relative to the direction of gravity and runs from radially outside to radially inside against the direction of gravity, wherein the first sealing gap communicates with a first overflow channel that runs downwards at least for the most part in the direction of gravity, wherein the first overflow channel ends below the first sealing gap in the direction of gravity, and,in particular to avoid a labyrinth seal, is designed as an annular gap.

[0008] Leakage of lubricant, especially lubricating oil, can occur particularly between components of the industrial gearbox that rotate relative to one another. To prevent this, contact seals such as a radial shaft seal or a felt seal can be provided. However, contact seals wear out and must be regularly maintained and replaced. This is particularly problematic in industrial gearboxes, where high relative speeds, high forces, and high temperatures can occur, leading to deformation of the components and increased wear of the contact seals. In addition, dust-intensive applications, such as a mill designed to crush solids, often require dust-proof encapsulation, making access to wearing parts generally difficult and requiring time-consuming maintenance.The use of non-contact seals, which avoid contact between the components rotating relative to one another even at the relative speeds and temperatures occurring in an industrial gearbox, has a low sealing effect due to the remaining relatively large sealing gap.

[0009] The invention exploits the knowledge that in a vertically aligned industrial gearbox, in which, for example, a power shaft can introduce a drive torque from bottom to top into the interior of a gearbox housing of the industrial gearbox or can discharge an output torque from top to bottom from the interior of the gearbox housing of the industrial gearbox, gravity effects and / or centrifugal force effects can be exploited to improve the sealing effect of a non-contact seal.

[0010] If the lubricant provided in the vertically aligned industrial gearbox were to pass through the sealing arrangement, the lubricant would have to be moved along the first sealing gap of the non-contacting first seal against the direction of gravity. The sealing effect of the first seal can thus easily be adjusted to a sufficiently high level over a correspondingly large extent in the vertical direction. With a structural design of the first seal that is very simple and cost-effective to manufacture compared to a labyrinth seal, a high sealing effect can be achieved. The first sealing gap can be delimited, at least in a predominant partial area, in particular by two conical surfaces facing one another, which are easy to manufacture and can form a constant radial distance between the conical surfaces facing one another, at least in a partial area along the flow direction of the first sealing gap.Due to the tapered shape of the sealing gap, the average diameter of the first sealing gap decreases along the flow direction against the direction of gravity, whereby the flow cross-section in the first sealing gap is automatically reduced by a simple design measure along the designated flow direction against the direction of gravity. Therefore, if lubricating oil leaks through the first sealing gap, it would not only have to fight against gravity, but also against a gradually increasing flow resistance due to the reduction in the flow cross-section. However, since the distance between the conical surfaces of the first sealing gap facing one another can be kept essentially constant, unnecessary capillary effects can be avoided despite the decreasing flow cross-section.The conical surfaces can, in particular, run essentially parallel to one another at least in one partial region and / or slightly tapered to one another in another partial region. The spacing of the conical surfaces can, in particular, be selected such that a suction capillary effect is avoided or kept to a minimum and / or that the passage of lubricant spraying upwards through the first sealing gap is blocked or kept to a minimum. The sealing gap between the conical surfaces can, at least in a respective partial region, have an essentially constant flow cross-section and / or a flow cross-section that tapers and / or widens counter to the direction of gravity.

[0011] If lubricant should pass through the first sealing gap of the first non-contact seal, this generally very small portion of the lubricant can be drained away from the first seal via the overflow channel, which is designed as an annular gap and acts in particular as a gap seal. The overflow channel is formed as an annular gap between the power shaft and a component connected to the transmission component, in particular the first seal cover. The overflow channel has, in particular, a substantially constant flow cross-section, whereby any transitions provided at the beginning and / or end of the overflow channel are disregarded with regard to the constant flow cross-section.The overflow channel can therefore act as a particularly simply designed gap seal, whereby a labyrinth seal, which is more complex to manufacture and maintain and has a plurality of annular pockets formed between each two subsequent radially projecting webs, can be avoided. The overflow channel preferably consists of a single gap seal, in particular for the purpose of avoiding a labyrinth seal. The overflow channel can have a cylindrical outer channel wall running at least over a large part of the vertical extent, preferably over the entire vertical extent, of the overflow channel and a cylindrical inner channel wall running over the entire vertical extent of the overflow channel, wherein in particular the inner channel wall is formed by the power shaft itself, i.e. not by a sleeve connected to the power shaft.Preferably, the outer channel wall of the overflow channel and the radially inner (conical) surface of the first sealing gap are designed in one piece with a common component, in particular a first sealing cover, wherein in particular this common component has an annular collecting volume for collecting lubricant below the bearing and below the first sealing gap.

[0012] In addition, during normal operation, when the power shaft rotates, a relative rotation can occur between the radially inner and the radially outer boundary of the first sealing gap. The lubricant penetrating the first sealing gap can be entrained by the radially inner and / or the radially outer boundary of the first sealing gap due to friction effects and distributed over the circumferential surface, whereby the lubricant can flow back to the associated boundary under the force of gravity. In addition, the lubricant can be forced radially outwards by centrifugal force as a result of the rotary movement component and can be pressed downwards along the inclined plane formed by the radially outer boundary of the first sealing gap.In addition to the force of gravity acting on the lubricant anyway, a portion of the centrifugal force acting on the lubricant, directed along the inclined plane of the radially outer boundary of the first sealing gap, can transport the lubricant downwards out of the first sealing gap in the direction of gravity. As a result, it can be expected that during normal operation almost no lubricant can pass through the first sealing gap and reach the overflow channel. It is therefore sufficient to design the overflow channel as a simple annular gap with a sealing gap effect and to avoid a labyrinth seal, since even a slight flow resistance at the upper end of the overflow channel due to the small radial extent of the overflow channel is sufficient to delay the penetration of the lubricant into the overflow channel until the lubricant is pumped radially outwards from the overflow channel back to the first sealing gap due to centrifugal force effects.Even if lubricant enters the first sealing gap of the first seal against gravity, the simple but effective design of the first sealing gap can convey the lubricant back radially outwards and downwards without any wear effects, so that with the help of the sealing arrangement a low-maintenance and cost-effective industrial gearbox is possible.

[0013] The power shaft can transmit torque through an outer shell of the industrial gearbox, in particular provided by a gearbox housing, at the lower end of the outer shell. The power shaft can in particular output torque converted in the industrial gearbox from the industrial gearbox as an output shaft and drive, for example, a mill shaft of a vertical mill. However, it is also possible for the power shaft to be connected to a drive motor and, as a drive shaft, to input torque into the industrial gearbox. The power shaft of the industrial gearbox can in particular be a sun shaft connected to a sun gear of a planetary gear or a plate carrier shaft connected to a planet carrier of the planetary gear. The power shaft can be designed as a solid shaft or a hollow shaft.The power shaft itself or a component connected to the power shaft can in particular form a boundary of the first sealing gap. The gear component can in particular be designed to be immovable or to rotate more slowly than the power shaft. The gear component can in particular be a ring gear of a planetary gear and / or a gear housing. Preferably, the industrial gear unit has a planetary gear unit with a fixed ring gear which radially outwards forms an outer shell of the industrial gear unit and is connected at each of its end faces to a part of a fixed gear housing. Preferably, a gear housing provided above the gear component in the direction of gravity can form a support for a drive motor or for a turntable of a vertical mill driven by the industrial gear unit.In particular, a bearing, preferably at least one rolling bearing, can be provided between the transmission component and the power shaft rotatable relative thereto. The bearing can, for example, engage the transmission component and the power shaft or the transmission component and another component of the industrial transmission and support them rotatably relative to one another. The lubricant can, in particular, be provided for lubricating the bearing and, for example, can reach the first seal from the bearing through the effects of gravity. The lubricant can, additionally or alternatively, be provided for lubricating tooth engagements of the industrial transmission and can reach the first seal through displacement on tooth flanks and / or through the effects of gravity.

[0014] The non-contact first seal consists, in particular, exclusively of a single first sealing gap. A cascade of multiple sealing gaps, as would be provided in a non-contact labyrinth seal, can be deliberately avoided. Multiple spaced-apart lamellae, each of which delimits a sealing gap offset from one another, can be avoided. The first seal can be limited to a conical first sealing gap. This can minimize manufacturing costs and / or provide a particularly robust and low-maintenance seal. The first seal is therefore particularly simple and cost-effective with very few components. In particular, the first seal consists of exactly two components, each of which delimits one side of the first sealing gap.

[0015] When referring to a vertical direction or a direction of gravity with regard to the industrial gearbox and / or the sealing arrangement, this refers to the intended installation position in which the center lines or axes of rotation of the gearbox component and the power shaft are aligned in the vertical direction, i.e. along the direction of gravity.

[0016] An industrial gearbox is a gearbox that is exposed to particularly heavy loads in industrial plants. In contrast to turbomachines and / or helicopter engines, the industrial gearbox must withstand particularly high torques at comparatively lower speeds. The industrial gearbox is designed to be correspondingly massive for this purpose. A typical industrial gearbox usually has a dead weight of at least 500 kg, with typical industrial gearboxes having a dead weight of over 1 t, in particular at least 5 t or at least 10 t. The power shaft, via which the power is introduced into the industrial gearbox, is dimensioned for the power of the industrial gearbox and therefore also has a very massive design, in particular a comparatively large diameter. The sealing arrangement for the power shaft is therefore dimensioned accordingly large, especially with regard to the inner diameter.At the same time, the components, particularly the housing parts, in the immediate vicinity of the power shaft and / or the industrial gearbox can be designed to be correspondingly solid, so that the sealing arrangement can be connected very easily and without major adjustments. Preferably, functional components of the sealing arrangement can be formed integrally from already provided gearbox components and / or housing parts, which are merely adapted in terms of their shape for their functionality in the sealing arrangement. The industrial gearbox can be connected to a mechanical application, which is, for example, a conveyor belt, with the aid of which recyclable materials from, possibly previously separated and / or sorted, waste or similar can be fed to a shredder.The mechanical application can also 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, waste compactor, scrap press, shredder for recyclable materials from, possibly previously separated and / or sorted, waste or similar.

[0017] In particular, a radially inner circumferential surface of the first sealing gap is non-rotatably attached to the transmission component, and a radially outer circumferential surface of the first sealing gap is non-rotatably attached to the power shaft. The respective circumferential surface is configured, at least over a, preferably predominantly, partial area, in particular conical, i.e., in particular as an outer truncated cone or inner truncated cone. The respective circumferential surface can form a boundary of the first sealing gap in the radial direction. Preferably, the respective circumferential surface extends over the entire vertical extent of the first sealing gap, so that a parting line within the respective circumferential surface is avoided.Since the transmission component is provided, in particular coaxially, radially outside the power shaft and the outer surface of the first sealing gap, which is directly or indirectly fastened to the transmission component, is provided on the radially inner boundary of the first sealing gap, a substantially U-shaped engagement of the outer surface of the first sealing gap, which is directly or indirectly fastened to the power shaft and forms the radially outer boundary, can result. This forms a chicane for the mass flow of the leaking lubricant, so that a reduction in the flow velocity of the leaking lubricant is already achieved, which makes it more difficult for the lubricant to pass through the first sealing gap. In addition, high-spiking lubricant can be more easily retained by the material of the radially outer surface, which engages the radially inner outer surface, in particular in a substantially U-shape, and is connected to the power shaft.The material forming the radially outer surface can form a splash guard for the first sealing gap.

[0018] Preferably, the transmission component is mounted so as to be rotatable relative to the power shaft via a bearing bridging a bearing gap, wherein the first sealing gap communicates with the bearing gap. The lubricant, in particular lubricating oil, provided for lubricating the bearing, in particular rolling bearings, can be displaced from the bearing and, in particular driven by gravity, reach the first seal. For example, the bearing can have an inner ring and an outer ring which are rotatable about a vertical axis, wherein the lubricant provided in the bearing can escape downwards from the bearing in the direction of gravity. The lubricant can be retained in a volume between the bearing gap and the first sealing gap. In particular, at least a portion of the lubricant which has nevertheless entered the first sealing gap can be returned to this volume by gravity and / or centrifugal force without external aids, i.e. passively.Preferably, the volume provided between the bearing gap and the first sealing gap is provided with an oil return for the active and / or passive removal of lubricant. For example, the lubricant can be reused via the oil return to lubricate another component of the industrial gearbox. Since the lubricant escaping from the bearing can hardly escape through the first non-contact seal through the first sealing gap, it is possible to omit a sealing bearing cap for the bearing without having to worry about significant leakage. This can reduce manufacturing costs, the number of components, and maintenance effort.

[0019] Particularly preferably, a first sealing cover is provided which is connected to the transmission component, the first sealing cover defining at least part of the first sealing gap radially on the inside. The first sealing cover can define a flow path for the lubricant and, in particular, form a U-shaped baffle for the lubricant on its inner side facing the first sealing gap. The first sealing cover can be easily mounted by an axial relative movement relative to the material forming the radially outer boundary of the first sealing gap. The first sealing cover can be connected to the radially outer transmission component and / or a transmission housing, in particular via fastening means, in particular screws, which run in the axial direction, i.e., in particular, substantially parallel to a rotational axis of the power shaft.A joint between the first sealing cover and the transmission component and / or the transmission housing can be offset radially outward and spaced from a lower base on the inside of the first sealing cover in the direction of gravity so that the lubricant cannot reach the joint. This even makes it possible to eliminate the need for a sealing element in the joint, thereby reducing the number of components. Alternatively, a cost-effective sealing element, such as an O-ring or an annular paper seal, can be provided in the joint for safety reasons.

[0020] In particular, the first sealing cover has a first collection volume for collecting lubricant, provided below the first sealing gap in the direction of gravity. The first sealing cover can form the collection volume on a lower base on the inside of the first sealing cover, as seen in the direction of gravity. The lubricant can preferably be actively or passively drained from the collection volume, so that the risk of lubricant from the collection volume entering the first sealing gap of the first non-contact seal can be reduced. The collection volume allows the incoming lubricant to be collected at a distance from the first sealing gap in the direction of gravity, so that even lubricant that splashes up can hardly reach the first sealing gap.It may also be provided that the first sealing cover is removed at scheduled maintenance intervals to remove the lubricant collected since the last maintenance from the collection volume. Additionally or alternatively, it may also be provided that the lubricant collected since the last maintenance can be removed via a closable drain opening communicating with the collection volume.

[0021] The power shaft preferably has an undercut first conical seat for radially outer delimitation of the first sealing gap. The first conical seat can be mounted on the power shaft as a separate component or can be designed integrally with the power shaft. The first conical seat can point radially inward and, in particular, encompass the material forming the radially inner delimitation of the first sealing gap in a substantially U-shaped manner. The first conical seat can be produced cost-effectively, for example, by a machining process, in particular turning, in a radially outward-projecting axial surface of the power shaft.

[0022] In particular, a first ramp is formed between the first sealing gap and the first overflow channel to create a larger flow cross-section than in the first sealing gap. For example, the gradient of the radially inner boundary of the first sealing gap with the transition to the ramp can change abruptly, for example via a kink, or gradually, for example via a curve. Between the radially outer boundary of the first sealing gap, a funnel-like enlargement of the flow cross-section from bottom to top can occur in the direction of gravity above the radially inner boundary of the first sealing gap in a common height range with the ramp. Any capillary effects present in the first sealing gap can thereby be eliminated or at least reduced, so that mass transport of the lubricant through the first sealing gap caused by capillary effects can be stopped in the region of the ramp.The ramp can be sloped to the horizontal so that lubricant on the ramp can flow back into the first sealing gap under gravity. This allows lubricant passing through the first sealing gap to flow back automatically, preventing or at least reducing leakage.

[0023] Particularly preferably, a radially outer channel wall of the first overflow channel, a / the radially inner circumferential surface of the first sealing gap, and a collecting surface for the lower boundary of a / the first collecting volume for collecting lubricant, provided below the first sealing gap in the direction of gravity, are formed in one piece, in particular by precisely one / the first sealing cover. The number of components can thus be kept low. Furthermore, this exploits the knowledge that the one-piece component can be easily slipped onto the power shaft from below and, in the designated end position, can be easily fastened, in particular screwed, to the transmission component, in particular the ring gear, and / or a stationary housing part.For this purpose, the first sealing cover, which is already provided, can be used, which, when used in an industrial application, is already sufficiently solid and stable to allow the required shape to be formed. Since sliding contact with the relatively rotating power shaft is avoided, the one-piece component can also be made of plastic, so that the shape required for the first sealing gap and the overflow channel can be easily achieved by plastic injection molding of a plastic, in particular a thermoplastic.

[0024] Preferably, an intermediate piece is connected to the power shaft in a rotationally fixed manner, wherein the intermediate piece has an end face facing the first overflow channel for the gravity-driven and / or centrifugal force-driven discharge of lubricant coming from the first overflow channel radially outwards. The lubricant dripping downwards via the overflow channel can impinge on the end face of the intermediate piece at the lower end of the overflow channel. Since the intermediate piece is connected to the power shaft in a rotationally fixed manner, the end face of the intermediate piece can act as a centrifugal disk and move the lubricant radially outwards away from the power shaft under centrifugal force. This prevents mass transport of the lubricant at a joint between the intermediate piece and the power shaft, which could ultimately lead to leakage.The end face of the intermediate piece can, in particular, be tapered downwards from the radially inner to the radially outer side to the horizontal, so that even when the power shaft is stationary and centrifugal forces are absent, the lubricant arriving at the end face can flow radially outward over the end face by gravity. The lubricant can, for example, be collected and / or directed at the radially outer end of the end face to prevent leakage.

[0025] Particularly preferably, the power shaft has a step forming an axial stop for the intermediate piece, wherein a radial inner side of the intermediate piece is provided radially further inward than the first overflow channel. The at least slight radial offset of the inner side of the intermediate piece to the radially inner edge of the overflow channel can ensure that lubricant arriving at the end face of the intermediate piece is conveyed radially outward, where the flow resistance is considerably lower than at the joint between the intermediate piece and the power shaft. In addition, the step forming the axial stop can determine the axial relative position of the intermediate piece to the power shaft. Preferably, the intermediate piece is pressed onto the power shaft in a rotationally fixed manner and, for this purpose, is pushed onto the power shaft until it abuts against the axial stop of the step.

[0026] In particular, a non-contact second seal is provided in the direction of gravity below the first seal between the transmission component and the power shaft to provide sealing resistance against lubricant passing through the first seal, wherein the second seal in particular has a conical second sealing gap that is beveled relative to the direction of gravity and runs from radially outside to radially inside, counter to the direction of gravity. The non-contact second seal can adjoin the first seal, the downstream overflow channel, and the downstream end face of the intermediate piece, in particular in the direction of flow of the lubricant. The non-contact second seal can in particular be designed analogously to the first seal as described above. The above explanation of the first seal applies analogously to the second seal.The sealing arrangement can therefore be essentially two-stage with two contactless seals, each having a conical sealing gap through which the lubricant can only pass against the direction of gravity.

[0027] Preferably, it is provided that a radially inner surface of the second sealing gap is fixedly connected to the transmission component in a rotationally fixed manner and a radially outer surface of the second sealing gap is fixedly connected to the power shaft in a rotationally fixed manner and / or a second sealing cover is provided which is directly or indirectly connected to the transmission component,wherein the second sealing cover defines at least a portion of the second sealing gap radially inwardly and / or the second sealing cover has a second collecting volume provided below the second sealing gap in the direction of gravity for collecting and / or discharging lubricant and / or the intermediate piece has a second undercut conical seat for radially outwardly defining the second sealing gap and / or the second sealing gap communicates with a second overflow channel extending downwards at least for the most part in the direction of gravity and / or a second ramp is formed between the second sealing gap and the second overflow channel to form a larger flow cross-section than in the second sealing gap. The second seal can thus be designed in part or entirely analogously to the first seal, with the proviso,that the second seal is arranged below the first seal in the direction of gravity, and the radially outer boundary of the second sealing gap is not formed by the power shaft itself, but by the intermediate piece connected to the power shaft. Furthermore, it is possible to provide the second seal with a smaller nominal diameter than the first seal. Furthermore, the second seal cover can be attached to the first seal cover, so that the second seal cover is only indirectly connected to the transmission component and / or the transmission housing.

[0028] Particularly preferably, an end seal, in particular a labyrinth seal or contact seal, communicating with the second sealing gap is provided below the second seal in the direction of gravity, wherein the end seal is provided on a smaller radius than the first sealing gap and the second sealing gap. The labyrinth seal is in particular greased. The end seal can be provided at a lower end of the gearbox housing. The end seal is thus more easily accessible than the first seal and the second seal and can be serviced more easily and quickly if necessary.

[0029] One aspect further relates to an industrial gear, in particular for driving a vertical mill, with a vertically aligned power shaft for introducing a torque, wherein the power shaft is a planetary carrier shaft or sun shaft of a planetary gear, and a gear component which rotates more slowly or is stationary in normal use compared to the power shaft, wherein the gear component is designed as a ring gear and / or gear housing of the planetary gear, and a sealing arrangement which can be designed and further developed as described above for retaining lubricant.Even if lubricant enters the first sealing gap of the first seal against gravity, the simple but effective design of the first sealing gap can convey the lubricant back radially outward and downward without causing wear, so that a low-maintenance and cost-effective industrial gearbox is possible with the help of the sealing arrangement. The industrial gearbox can also be designed and developed as described in DE 10 2013 212 464 A1, preferably to form a vertical mill, for example for comminuting solids.

[0030] An unclaimed aspect further relates to a data agglomerate with data packets summarized in a common file or distributed across different files for depicting the three-dimensional shape design and / or the interactions of all components provided in the sealing arrangement, which can be designed and further developed as described above, or in the industrial gearbox, which can be designed and further developed as described above, wherein the data packets are prepared for the purpose of additive manufacturing of the components of the sealing arrangement, which can be designed and further developed as described above, or in the industrial gearbox, which can be designed and further developed as described above, in particular by 3D printing, when processed by a data processing device for operating a machine tool for the additive manufacturing of devices,and / or when processed by a data processing device for carrying out a technical simulation, to carry out a simulation of the functioning of the sealing arrangement, which can be designed and further developed as described above, or of the industrial gearbox, which can be designed and further developed as described above, and to output the simulation results generated for further use, in particular for the purpose of providing proof of fatigue strength as a function of changing loads and / or changing temperature loads. The data packets of the data agglomerate are specifically adapted to the inventive design of the respective device in order to be able to adequately represent the inventive interaction of the components of the inventive device during processing in the data processing device. The data packets can in particular be stored in a spatially distributed manner,but be 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 thus assembled data agglomerate 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. For example, the data packets are each separate parts of a data library ("library"), which are combined to form the data agglomerate and adapted to one another with regard to their relative dimensions to one another 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 particular the sealing arrangement and / or the industrial gearbox, in the manner of a so-called "digital twin."which enables a virtual investigation in the form of a simulation or a real objectification with the aid of an additive manufacturing process. In particular, each data packet can depict a separately implemented component of the respective associated device according to the invention, so that the individual components can easily be assembled in reality and / or virtually in terms of their relative position and / or relative mobility in order to realize the interactions essential to the invention. With the aid of the data packets of the data agglomerate, the physical state and / or the change in physical parameters depending on various boundary conditions and / or over time of the associated device according to the invention can be calculated and / or predicted in a virtual environment during a technical simulation of the individual components of the respective device and their interactions, as well as for the verification,whether the device according to the invention, based on the assumed design and taking into account the assumed simulated influences, is sufficiently suitable for the intended purpose. In particular, it is possible to use the respective data packages to produce the various components of the respective device separately, possibly from different materials, by additive manufacturing and subsequently assemble them into a prototype of the respective device. The division of the data of the data agglomerate into different data packages thus enables a simple sequential additive manufacturing of relatively movable components of the respective device in the form of a kit of parts.which is designed to be assembled only in a meaningful way for the inventive interaction of the components of the prototype to solve the problem underlying the invention. This enables cost-effective production of prototypes and / or computer-based simulations to study the functionality of the sealing arrangement and / or the industrial gearbox, identify problems in the specific application, and find improvements. Even if lubricant enters the first sealing gap of the first seal against gravity, the simple but effective design of the first sealing gap can pump the lubricant back radially outward and downward without wear effects, so that with the help of the sealing arrangement, a low-maintenance and cost-effective industrial gearbox is possible, which can be easily and cost-effectively verified with the help of the data agglomerate.

[0031] The invention will now be explained by way of example with reference to the accompanying drawings using preferred embodiments, wherein the features presented below may represent an aspect of the invention both individually and in combination. They show: Fig. 1 : a lower part of an industrial gearbox, Fig. 2 : one for the industrial gearbox from Fig. 1 intended sealing arrangement.

[0032] The Fig. 1 The partially illustrated industrial gear unit 10 can be used in particular for a vertical mill for comminuting solids. When used as intended, the industrial gear unit 10 is oriented substantially vertically, so that a main axis of rotation 12 is aligned along a direction of gravity 14. At the lower end of the industrial gear unit 10, in the direction of gravity 14, a power shaft 16 used as an output shaft can transfer a torque converted in the industrial gear unit 10 from the industrial gear unit 10. The industrial gear unit 10 has at least one planetary gear unit 18, wherein preferably two or more planetary stages can be provided. The planetary gear unit 18 forming a final planetary stage has a planet carrier 20, which is connected in particular in one piece to a planet carrier shaft 21, which in the illustrated embodiment simultaneously forms the power shaft 16.The planet carrier 20 has at least one planetary gear axle 22 fixedly secured to the planet carrier 20 for rotation therewith, on which a planetary gear 24 is mounted via a planetary gear bearing 26 configured for relative rotation via a plain bearing or roller bearing. Alternatively, the planetary gear 24 can have a planetary gear shaft that rotates with the planetary gear 24 and can be mounted within a flange of the planet carrier 20. In particular, at least three, preferably four, five, six, or seven, planetary gears 24 are provided. Each planetary gear 24 meshes radially inwardly with a sun gear 27 that is fixedly connected to a sun gear shaft 28 for rotation therewith. In the illustrated embodiment, drive power from a drive motor, which may already have been converted to speed and torque by at least one upstream planetary stage of the industrial gear 10, is transmitted via the sun gear shaft 28 to the power shaft 16 via the planetary gear 18.The power shaft 16, as an output shaft, can transfer the converted drive power directly or indirectly to a mill shaft of the vertical mill in order to set a mill table in rotation. Radially outward, the respective planetary gear 24 meshes with a ring gear 30, which rotates more slowly than the power shaft 16. In the illustrated embodiment, the ring gear 30 is even held immovably and can form an outer shell of a gear housing 32 on its outside, from which the power shaft 16 protrudes. In the illustrated embodiment, the gear housing 32 can be composed of the ring gear 30, an upper housing part 34, and a lower housing part 36. The upper housing part 34 can be fastened, in particular screwed, to an upwardly facing end face of the ring gear 30, wherein the upper housing part 34 can in particular have a bearing surface for supporting a drive motor of the vertical mill.The lower housing part 36 can be fastened, in particular screwed, to a downwardly facing end face of the ring gear 30, wherein the lower housing part 36 and thus also the ring gear 30 are mounted on the power shaft 16 via a bearing 38, in particular designed as a rolling bearing. The ring gear 30 and the lower housing part 36 form a gear component 40 of the industrial gear unit 10, which is provided radially outside of the power shaft 16.

[0033] The bearing 38 can be lubricated with a lubricant, in particular lubricating oil, whereby it is possible for lubricant to be displaced from the bearing 38 and drip downward in the direction of gravity 14. To prevent leakage, the transmission component 40 and the power shaft 16 are part of a sealing arrangement 42, which has a non-contact first seal 44 and a non-contact second seal 48 communicating via a first overflow channel 46, to which an end seal 50 provided at a smaller radius is finally connected via a second overflow channel 80.

[0034] As in Fig. 2As shown in detail, the sealing arrangement 42 has a first sealing cover 52 which, through an axial relative movement, can engage with a protruding first extension 52 into an undercut formed by the power shaft 16, wherein the undercut forms a first undercut conical seat 54. Between the first conical seat 54 and the first extension 52, a conical first sealing gap 56 of the first seal 44 is formed, which extends counter to the direction of gravity 14 and from radially outward to radially inward. The first sealing cover 52 can be fastened to a lower end face of the transmission component 40 and can delimit a first collecting volume 58 into which the lubricant coming from the bearing 38 can drip. For the lubricant to leak, it would be necessary for the lubricant to pass from the first collecting volume 58 against the direction of gravity 14 through the first sealing gap 56 of the first seal 44.In addition, the first conical seat 54 forming the radially outer surface of the first sealing gap 56 can rotate at the speed of the power shaft 16 and exert a centrifugal force on the lubricant that has entered the first sealing gap 56, as a result of which the lubricant is conveyed radially outwards and along the first conical seat 54 radially outwards back into the first collection volume 58. At the upper end of the first sealing gap 56, there is a first ramp 60 that leads to a larger flow cross-section than in the first sealing gap 56. Lubricant passing through the first sealing gap 56 can settle on the first ramp 60 and flow back into the first sealing gap 56 under the force of gravity.

[0035] Even if lubricant were to pass through the first seal 44, the lubricant can flow via the first overflow channel 46 onto an upwardly facing end face 62 of an intermediate piece 64 that is non-rotatably attached to the power shaft 16. The intermediate piece 64 is pressed onto the power shaft 16 up to a step 66 with a smaller diameter than the first overflow channel 46. The end face 62 of the intermediate piece 64 is beveled to the horizontal so that the incoming lubricant can flow radially outward via the end face 62 under the force of gravity. In addition, the intermediate piece 64 can rotate at the speed of the power shaft 16 and support the radially outward movement of the lubricant through applied centrifugal forces. The lubricant can flow from the end face 62 of the intermediate piece 64 into a second collection volume 70 defined by a second seal cover 68.The second sealing cover 68 can engage with a protruding second extension 72 through an axial relative movement into an undercut formed by the intermediate piece 64, wherein the undercut forms a second undercut conical seat 74. Between the second conical seat 74 and the second extension 72, a conical second sealing gap 76 of the second seal 48 is formed, which extends counter to the direction of gravity 14 and from radially outward to radially inward. The second sealing cover 68 can be fastened to a lower end face of the transmission component 40 and / or to a lower end face of the first sealing cover 52. For lubricant to leak, it would be necessary for the lubricant from the second collecting volume 70 to pass through the second sealing gap 76 of the second seal 48 counter to the direction of gravity 14.In addition, the second conical seat 74 forming the radially outer surface of the second sealing gap 76 can rotate at the speed of the power shaft 16 and exert a centrifugal force on the lubricant that has entered the second sealing gap 76, due to which the lubricant is conveyed radially outwards and along the second conical seat 74 radially outwards back into the second collecting volume 70. At the upper end of the second sealing gap 76, there is a second ramp 78 that leads to a larger flow cross-section than in the second sealing gap 76. Lubricant passing through the second sealing gap 76 can settle on the second ramp 78 and flow back into the second sealing gap 76 under the force of gravity.Even if the lubricant were to pass through the non-contact second seal 48 and be directed to the end seal 50 via a second overflow channel 80, the end seal 50, configured, for example, as a greased labyrinth seal, can prevent lubricant leakage. In particular, the end seal 50 is designed solely as a dust seal to prevent dust from penetrating the industrial gear unit 10. Since only very little lubricant, if any, reaches the end seal 50, a low sealing effect of the end seal is sufficient to prevent lubricant leakage.

Claims

1. Seal assembly (42) for an industrial transmission (10), comprising a vertically aligned lower power shaft (16) for exchanging torque with the industrial transmission (10), a transmission component (40) of the industrial transmission (10), said transmission component (40) being provided radially outside the power shaft (16), wherein the power shaft (16) comprises an intended greater rotational speed than the transmission component (40) during operation, wherein a contactless first seal (44) is provided between the transmission component (40) and the power shaft (16), wherein the first seal (44) comprises a conical first sealing gap (56) which is bevelled in the direction of gravity (14) and runs from radially on the outside to radially on the inside counter to the direction of gravity (14), and a first overflow channel (46) running downwards to at least a large extent in the direction of gravity (14), wherein the first sealing gap (56) communicates with the first overflow channel (46), wherein the first overflow channel (46) ends below the first sealing gap (56) in the direction of gravity (14) and is in the form of an annular gap, characterized in that the overflow channel comprises a substantially constant flow cross section and consists of a single gap seal, for the purpose of avoiding a labyrinth seal.

2. Seal assembly (42) according to Claim 1, wherein a radially inner circumferential surface of the first sealing gap (56) is fastened to the transmission component (40) for rotation therewith and a radially outer circumferential surface of the first sealing gap (56) is fastened to the power shaft (16) for rotation therewith.

3. Seal assembly (42) according to Claim 1 or 2, wherein the transmission component (40) is mounted rotatably relative to the power shaft (16) via a bearing (38) bridging a bearing gap, wherein the first sealing gap (56) communicates with the bearing gap.

4. Seal assembly (42) according to any one of Claims 1 to 3, wherein a first sealing cover (52) which is connected to the transmission component (40) is provided, wherein the first sealing cover (52) bounds at least part of the first sealing gap (56) radially on the inside.

5. Seal assembly (42) according to Claim 4, wherein the first sealing cover (52) comprises a first collecting volume (58), which is provided below the first sealing gap (56) in the direction of gravity (14), for collecting lubricant.

6. Seal assembly (42) according to any one of Claims 1 to 5, wherein the power shaft (16) comprises an undercut first conical seat (54) for the radially outer boundary of the first sealing gap (56).

7. Seal assembly (42) according to any one of Claims 1 to 6, wherein a first ramp (60) for forming a larger flow cross section than in the first sealing gap (56) is formed between the first sealing gap (56) and the first overflow channel (46).

8. Seal assembly (42) according to any one of Claims 1 to 7, wherein a radially outer channel wall of the first overflow channel (46), a / the radially inner circumferential surface of the first sealing gap (56), and a collecting surface for the lower boundary of a / the first collecting volume (58), which is provided below the first sealing gap (56) in the direction of gravity (14), for collecting lubricant are formed integrally, in particular by precisely one / the first sealing cover (52).

9. Seal assembly (42) according to any one of Claims 1 to 8, wherein an intermediate piece (64) is connected to the power shaft (16) for rotation therewith, wherein the intermediate piece (64) comprides an end face (62) facing the first overflow channel (46) for the gravity-driven and / or centrifugally driven discharge radially to the outside of lubricant coming from the first overflow channel (46).

10. Seal assembly (42) according to Claim 9, wherein the power shaft (16) comprises a step (66) forming an axial stop for the intermediate piece (64), wherein a radial inside of the intermediate piece (64) is provided radially further on the inside than the first overflow channel (46).

11. Seal assembly (42) according to any one of Claims 1 to 10, wherein a contactless second seal (48) for providing a sealing resistance against lubricant passing the first seal (44) is provided below the first seal (44) between the transmission component (40) and the power shaft (16) in the direction of gravity (14), wherein the second seal (48) comprises a conical second sealing gap (76) which is bevelled in the direction of gravity (14) and runs from radially on the outside to radially on the inside counter to the direction of gravity (14).

12. Seal assembly (42) according to Claim 11, wherein a radially inner circumferential surface of the second sealing gap (76) is fastened to the transmission component (40) for rotation therewith and a radially outer circumferential surface of the second sealing gap (76) is fastened to the power shaft (16) for rotation therewith, and / or a second sealing cover (68) connected directly or indirectly to the transmission component (40) is provided, wherein the second sealing cover (68) bounds at least a part of the second sealing gap (76) radially on the inside, and / or the second sealing cover (76) comprises a second collecting volume (70), which is provided below the second sealing gap (76) in the direction of gravity (14), for collecting and / or discharging lubricant, and / or the intermediate piece (64) comprises a second undercut conical seat (74) for the radially outer boundary of the second sealing gap (76), and / or the second sealing gap (76) communicates with a second overflow channel (80) running downwards to at least a large extent in the direction of gravity (14), and / or a second ramp (78) for forming a larger flow cross section than in the second sealing gap (76) is formed between the second sealing gap (76) and the second overflow channel (80).

13. Seal assembly (42) according to Claim 11 or 12, wherein an end seal (50) communicating with the second sealing gap (76), in particular labyrinth seal or contacting seal, is provided below the second seal (48) in the direction of gravity (14), wherein the end seal (50) is provided on a smaller radius than the first sealing gap (56) and the second sealing gap (76).

14. Industrial transmission (10), in particular for driving a vertical mill, comprising a vertically aligned power shaft (16) for introducing a torque, wherein the power shaft (16) is a planet carrier shaft (21) or sun shaft (28) of a planetary transmission (18), and comprising a transmission component (40), which rotates more slowly in comparison to the power shaft (16) during use as intended or is at a standstill, wherein the transmission component (40) is in the form of a ring gear (30) and / or transmission housing (32) of the planetary transmission (18), and comprising a seal assembly (42) according to any one of Claims 1 to 13 for retaining lubricant.