Low maintenance seal assemblies for vertically arranged industrial gearboxes

Abstract

The invention relates to a sealing assembly (42) for an industrial gearbox (10), comprising a vertically arranged lower power shaft (16) for exchanging torque with the industrial gearbox (10); a gearbox component (40) of the industrial gearbox (10), which is arranged radially outside the power shaft (16), and the power shaft (16) has a higher rotation speed than the gearbox component (40) during a predetermined use period; a non-contact first sealing portion (44) is arranged between the gearbox component (40) and the power shaft (16), and the first sealing portion (44) has a conical first sealing gap (56), which is inclined along the gravity direction (14) and extends from the radial outside to the radial inside against the gravity direction (14). Even if lubricant enters the first sealing gap (56) of the first sealing portion (44) against the direction of gravity (14), the simple and effective design of the first sealing gap (56) can transport the lubricant radially outward and downward without causing wear effects, thereby realizing a low-maintenance and cost-effective industrial gearbox (10) with the seal assembly (42).

Description

Technical Field

[0001] The invention relates to a sealing assembly for a vertically arranged industrial transmission, which has particularly low maintenance costs, and also to an industrial transmission of this type, and to a data cluster for the virtual representation of an object of this type. Background Art

[0002] DE 10 2013 212 464 A1 discloses an industrial transmission having two planetary gear stages for driving a vertical mill, wherein the planetary gear stages have vertically arranged shafts and fixed ring gears. The transmission components in the planetary gear stages that are movable relative to each other are lubricated with lubricating oil and sealed against the environment by sealing assemblies.

[0003] A sealing assembly for a vertically running turbine shaft of a gas turbine for driving a helicopter is known from GB 783 118A, wherein the turbine shaft is driven by the exhaust gases of 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 transmission arranged to drive the rotor of the helicopter. The turbine shaft is mounted in a stationary turbine housing via rolling bearings. An annular groove is formed below the rolling bearing, and a gap with an inclined profile in the direction opposite to the force of gravity extends from the annular groove to the upper end of a sleeve connected to the turbine shaft. A labyrinth seal is formed on the sleeve, which has a plurality of groove cavities opening toward the sleeve and a plurality of gap seals formed between the groove cavities.

[0004] Industrial gearboxes are always designed to be low maintenance and have low wear to minimize costly downtime. Summary of the invention

[0005] The object of the invention is to specify measures which allow a low-maintenance industrial transmission to be realized.

[0006] Preferred improvements are described in detail in the following description, which improvements may represent an aspect of the invention alone or in combination. If one feature is presented in combination with another feature, this is only to simplify the presentation of the invention and is by no means intended to indicate that the feature cannot be an improvement of the invention without the other feature. One aspect of the invention relates to a sealing assembly for an industrial transmission, which has a vertically arranged lower power shaft, which is used to exchange torque with the industrial transmission; a transmission component of the industrial transmission, which is arranged radially outside the power shaft, wherein during the intended operation, the power shaft has a rotation speed greater than the transmission component, wherein a non-contact first sealing portion is arranged between the transmission component and the power shaft, wherein the first sealing portion has a conical first sealing gap, which is inclined in the direction of gravity and extends from the radial outer side to the radial inner side against the direction of gravity, wherein the first sealing gap is connected to a first overflow channel extending downward at least to a large extent in the direction of gravity, wherein the first overflow channel ends below the first sealing gap in the direction of gravity and is in the form of an annular gap in particular to avoid a labyrinth seal.

[0007] Leakage of lubricants, in particular lubricating oils, can occur in particular between components of industrial transmissions that rotate relative to one another. In order to prevent this from happening, contact seals, such as radial shaft sealing rings or felt seals, can be provided. However, contact seals wear and must be regularly maintained and replaced. This is a problem in particular in industrial transmissions, due to the high relative speeds, high forces and high temperatures that lead to deformation of the components and increased wear of the contact seals. In addition, in dust-intensive applications, such as mills for crushing solids, dust-proof packaging is usually provided, and therefore in principle it is difficult to access the wearing parts and time-consuming maintenance is required. The use of non-contact seals, which avoid contact between components that rotate relative to one another even at the relative speeds and temperatures that occur in industrial transmissions, has a poor sealing effect due to the relatively large remaining sealing gap.

[0008] The present invention has found that in a vertically arranged industrial transmission device, in which, for example, a power shaft can introduce a driving torque from bottom to top into the interior of a transmission housing of the industrial transmission device or lead an output torque from top to bottom out of the interior of a transmission housing of the industrial transmission device, the gravity effect and / or the centrifugal effect can be used to improve the sealing effect of the non-contact sealing part.

[0009] If the lubricant provided in a vertically arranged industrial transmission is intended to pass through the sealing assembly, the lubricant must move along the first sealing gap of the non-contacting first sealing part against the direction of gravity. Therefore, the sealing effect of the first sealing part can be easily adjusted to a sufficient degree in the vertical direction over a correspondingly large range. In the case of a structural design of the first sealing part that is very simple to manufacture and cost-effective to produce compared to the labyrinth seal, a high sealing effect can be achieved. The first sealing gap can be defined in particular by two conical surfaces at least in the main part area, which face each other, are simple to manufacture and can form a constant radial distance between the two conical surfaces facing each other at least in a part area along the flow direction of the first sealing gap. Due to the inclined profile of the sealing gap, the average diameter of the first sealing gap in the flow direction is reduced against the direction of gravity, so that the flow cross section in the first sealing gap is automatically reduced against the direction of gravity along the specified flow direction by simple structural measures. Therefore, in the event of leakage via the first sealing gap, the leaking lubricant oil must not only overcome gravity but also resist the flow resistance that gradually increases due to the reduction of the flow cross section. However, since between the mutually facing conical surfaces of the first sealing gap, the distance between the conical surfaces can remain essentially constant, unnecessary capillary effects can be avoided despite the reduction in the flow cross section. The conical surfaces can in particular extend essentially parallel to one another at least in a partial region and / or extend with a slightly beveled profile in different partial regions. The distance between the conical surfaces can in particular be selected in such a way that a suction capillary effect is avoided or reduced and / or a high splashing lubricant is prevented or reduced through the first sealing gap. The sealing gap between the conical surfaces can have an essentially constant flow cross section and / or at least in a specific partial region have a gradually tapering and / or expanding flow cross section counter to the direction of gravity.

[0010] If the lubricating oil passes through the first sealing gap of the first non-contact sealing part, this usually small part of the lubricating oil can be removed from the first sealing part through an overflow channel, which is designed as an annular gap and is used in particular as a gap sealing part. The overflow channel is in the form of an annular gap between the power shaft and the component connected to the transmission component, in particular the first sealing cover. The overflow channel has in particular a substantially constant flow cross section, wherein a transition section can be selectively provided at the beginning and / or end of the overflow channel that is not considered with respect to the constant flow cross section. Therefore, the overflow channel can be used as a gap sealing part of particularly simple design, wherein a labyrinth seal can be avoided, which is more complicated to produce and maintain and has a plurality of annular grooves formed between each two consecutive radially protruding strips. Preferably, in particular for the purpose of avoiding a labyrinth seal, the overflow channel consists of a single gap sealing part. The overflow channel can have a cylindrical outer channel wall extending at least over a large part of the vertical extent of the overflow channel, preferably over the entire vertical extent, and a cylindrical inner channel wall extending over the entire vertical extent of the overflow channel, wherein in particular the inner channel wall is formed by the power shaft itself, that is to say it is not formed 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 integrally formed with a common component, in particular the first sealing cover, wherein in particular the common component has an annular collecting volume for collecting lubricant below the bearing and below the first sealing gap.

[0011] In addition, when the power shaft rotates as expected during operation, relative rotation may occur between the radial inner boundary and the radial outer boundary of the first sealing gap. Due to the friction effect, the lubricant penetrating the first sealing gap will be carried by the radial inner boundary and / or the radial outer boundary of the first sealing gap and distributed on the circumferential surface, as a result, the lubricant can be driven by gravity to flow back to the associated boundary. In addition, as a result of the rotating motion part, the lubricant can be driven by centrifugal force to be pressed radially outward and downward along the inclined plane formed by the radial outer boundary of the first sealing gap. In addition to the gravity acting on the lubricant in any case, a part of the centrifugal force acting on the lubricant, which is guided by the inclined plane along the radial outer boundary of the first sealing gap, can transport the lubricant downward from the first sealing gap in the direction of gravity. Therefore, it can be foreseen that during normal operation, almost no lubricant can pass through the first sealing gap and reach the overflow channel. Therefore, it is sufficient to design the overflow channel as a simple annular gap having the function of a sealing gap and to avoid a labyrinth seal, because as long as the lubricant is transported radially outwards from the overflow channel back to the first sealing gap due to the centrifugal force effect, the low 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 lubricating oil into the overflow channel. Even if the lubricant enters the first sealing gap of the first seal against gravity, the simple and effective shape of the first sealing gap can transport the lubricant radially outwards and downwards without causing wear effects, and therefore, with the help of the sealing assembly, a low-maintenance and cost-effective industrial transmission can be realized.

[0012] The power shaft can transmit torque at the lower end of the housing through the housing of the industrial transmission, in particular the housing provided by the housing of the transmission. In particular, the power shaft can release torque from the industrial transmission and drive a mill shaft of, for example, a vertical mill, which is converted into an output shaft in the industrial transmission. However, the power shaft can also be connected to a drive motor and introduce torque into the industrial transmission as a drive shaft. The power shaft of the industrial transmission can be especially connected to the sun shaft of the sun gear of the planetary transmission or the planetary carrier shaft of the planetary carrier of the planetary transmission. 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 especially constitute the boundary of the first sealing gap. In particular, the transmission component can be designed to be fixed or rotate slower than the power shaft. The transmission component can especially be a ring gear and / or a transmission housing of a planetary transmission. Preferably, the industrial transmission has a planetary transmission with a fixed ring gear, which radially forms the housing of the industrial transmission on the outside and is connected to a part of the fixed transmission housing on the end face in each case. Preferably, a transmission housing arranged above the transmission component in the direction of gravity can form a support for a drive motor or for a rotating plate driven by an industrial transmission in a vertical mill. Between the transmission component and the power shaft rotatable relative thereto, in particular a bearing, preferably at least one rolling bearing, can be arranged. For example, the bearing can act on the transmission component and the power shaft or the transmission component and another component of the industrial transmission and mount them rotatably relative to each other. The lubricant can be provided in particular for lubricating the bearing and, for example, is transferred from the bearing to the first seal due to the action of gravity. The lubricant can be provided as a supplement or alternative to the lubrication of the tooth meshing of the industrial transmission and can reach the first seal by displacement along the tooth flank and / or due to the action of gravity.

[0013] In particular, the non-contact first seal consists only of a single first sealing gap. A cascade of multiple sealing gaps, as provided in a non-contact labyrinth seal, can be deliberately avoided. Multiple mutually spaced plates, each of which defines a sealing gap offset from one another, can be avoided. The first seal can taper in a conical first sealing gap. Thus, production costs can be minimized and / or a particularly robust and low-maintenance seal can be provided. Thus, the first seal is designed to be particularly simple and cost-effective, having particularly few components. In particular, the first seal consists of exactly two components, each of which defines one side of the first sealing gap.

[0014] If a vertical or gravitational direction is specified with respect to an industrial transmission and / or a seal assembly, this means an intended installation position wherein the centerline or rotational axis of the transmission component and the power shaft are aligned in the vertical direction, ie in the gravitational direction.

[0015] Industrial transmission is a transmission that is subjected to particularly high loads in industrial equipment. In contrast to turbomachinery and / or helicopter drives, industrial transmissions must withstand particularly large torques at relatively low rotational speeds. For this reason, industrial transmissions are therefore designed to be sturdy. The net weight of a typical industrial transmission is usually at least 500 kg, wherein the net weight of a typical industrial transmission exceeds 1 t, in particular at least 5 t or at least 10 t. Therefore, the power shaft through which power is introduced into the industrial transmission is dimensioned for the power of the industrial transmission and therefore has a very sturdy design, in particular a relatively large diameter. Therefore, the sealing assembly of the power shaft is correspondingly large in size, in particular with respect to its inner diameter. At the same time, components near the power shaft and / or the industrial transmission, in particular housing parts, can be correspondingly designed to be sturdy, and therefore the sealing assembly can be connected very easily without significant adjustments. Preferably, the functional components of the sealing assembly can be formed in one piece by the transmission components and / or housing parts, and these components or parts can be provided in any case and are only adjusted with respect to their shape for their functionality in the sealing assembly. The industrial transmission can be connected to a mechanical application, which for example designs a conveyor belt, by means of which recyclable materials from waste or the like, which are optionally separated and / or sorted beforehand, can be fed to a pulverizer. For example, the mechanical application can also include mills, vertical mills, sugar mills, cement mills, stone crushers, conveyor belts, pumps, roller presses, plate belts, tube mills, rotary kilns, rotary gears, agitators, lifting devices, garbage presses, scrap presses, pulverizers for recyclable materials from waste or the like, which are optionally separated and / or sorted beforehand.

[0016] In particular, the radially inner circumferential surface of the first sealing gap is fastened to the transmission component for rotation therewith, and the radially outer circumferential surface of the first sealing gap is fastened to the power shaft for rotation therewith. The respective circumferential surface is formed in particular conically at least over a partial area, preferably over a major partial area, i.e., in particular forms an outer conical pile type or an inner conical pile type. The respective circumferential surface can form a boundary of the first sealing gap in the radial direction. Preferably, the respective circumferential surface extends in the entire vertical direction of the first sealing gap, so that a separating engagement piece in the respective circumferential surface is avoided. Since the transmission component is arranged radially outside the power shaft, in particular coaxially, and the circumferential surface of the first sealing gap, which is fastened directly or indirectly to the transmission component, is arranged at the radially inner boundary of the first sealing gap, a substantially U-shaped surround of the circumferential surface of the first sealing gap, which is fastened directly or indirectly to the power shaft and forms the radial outer boundary, can be produced. This forms a sharp turn in the mass flow of the leaking lubricant and thus achieves a reduction in the flow velocity of the leaking lubricant, which makes it difficult to pass through the first sealing gap. Furthermore, the material of the radially outer circumferential surface, which in particular surrounds the radially inner circumferential surface in a substantially U-shaped manner and is connected to the power shaft, is more likely to retain high-splash lubricants. The material forming the radially outer circumferential surface may form a splash protection for the first sealing gap.

[0017] Preferably, the transmission component is rotatably mounted relative to the power shaft by a bearing, which bridges the bearing gap, wherein the first sealing gap is connected to the bearing gap. Lubricant, especially lubricating oil, provided for lubricating the bearing, especially the rolling bearing, can flow out of the bearing and reach the first sealing portion, especially driven by gravity. For example, the bearing can have an inner ring and an outer ring, which can rotate around a vertically extending axis, wherein the lubricant provided in the bearing can overflow downward from the bearing in the direction of gravity. The lubricant can be retained in the volume between the bearing gap and the first sealing gap. In particular, at least some of the lubricant that has entered the first sealing gap can be returned to the volume without external assistance, i.e. passively returned, under the drive of gravity and / or centrifugal force. Preferably, an oil return device for active and / or passive lubricant removal is provided by means of a volume arranged between the bearing gap and the first sealing gap. For example, the lubricant can be used again to lubricate another component of the industrial transmission by the oil return device. Since the lubricant overflowing from the bearing is almost impossible to overflow through the first non-contact seal portion through the first sealing gap, the sealed bearing cover of the bearing can be saved without worrying about significant leakage. This can reduce production costs, the number of parts and maintenance costs.

[0018] Particularly preferably, a first sealing cover connected to a transmission component is provided, wherein the first sealing cover defines at least part of the first sealing gap radially inwardly. The first sealing cover can define the flow path of the lubricant and form a U-shaped sharp turn facing the first sealing gap for the lubricant in particular on its inner side. The first sealing cover can be easily installed by axial relative movement of the material forming the radial outer boundary of the first sealing gap. The first sealing cover can be connected to the radial outer transmission component and / or the transmission housing, in particular by a fastening device extending in the axial direction, in particular a fastening device substantially parallel to the axis of rotation of the power shaft, in particular a screw. The separation joint of the first sealing cover and the transmission component and / or the transmission housing can be radially offset outwardly in this way and spaced apart from the lower base in the direction of gravity on the inner side of the first sealing cover so that the lubricant cannot reach the separation joint. This can even save the sealing element in the separation joint, which reduces the number of components. Alternatively, for safety, a cost-effective sealing element, such as an O-ring or an annular paper seal, can also be provided in the separation joint.

[0019] In particular, the first sealing cover has a first collection volume, which is arranged below the first sealing gap in the direction of gravity for collecting lubricant. The first sealing cover can form a collection volume on the lower base in the direction of gravity on the inner side of the first sealing cover. Preferably, the lubricant can be actively or passively removed from the collection volume and the risk of the lubricant entering the first sealing gap of the first non-contact sealing portion from the collection volume is reduced. Due to the collection volume, the inflowing lubricant can be collected at a distance from the first sealing gap in the direction of gravity, and therefore even high splash lubricants are difficult to reach the first sealing gap. It is also conceivable that, during the regular maintenance provided in any case, the first sealing cover is removed from the collection volume to remove the lubricant collected since the last maintenance. Additionally or alternatively, it is also conceivable that the lubricant collected since the last maintenance is removed through a closable discharge port connected to the collection container.

[0020] Preferably, the power shaft has an undercut first conical seat for the radially outer boundary of the first sealing gap. The first conical seat may be placed on the power shaft as a separate component or may be formed integrally with the power shaft. The first conical seat may face radially inwards and may surround material forming the radially inner boundary of the first sealing gap, in particular in a substantially U-shaped manner. The first conical seat may be cost-effectively manufactured on a radially outwardly protruding axial surface of the power shaft, for example by machining, in particular turning.

[0021] In particular, a first slope is formed between the first sealing gap and the first overflow channel to form a larger flow cross section than in the first sealing gap. For example, the gradient of the radial inner boundary of the first sealing gap with a transition to the slope can change suddenly, for example, by bending, or gradually, for example, by rounding. Between the radial outer boundaries of the first sealing gap, for example, a funnel-shaped increase in the flow cross section from bottom to top can lead to a common height area with the slope above the radial inner boundary of the first sealing gap in the direction of gravity. Therefore, the capillary effect that may exist in the first sealing gap will be dispersed or at least weakened, and thus the lubricant caused by the capillary effect is ended in the material transport of the first sealing gap in the region of the slope. The slope can have a slope profile relative to the horizontal plane so that the lubricant located on the slope can flow back to the first sealing gap under gravity drive. Therefore, the lubricant passing through the first sealing gap can automatically flow back, which can avoid or at least reduce leakage.

[0022] Particularly preferably, the radially outer channel wall of the first overflow channel, the radially inner circumferential surface of the first sealing gap and the collecting surface of the lower boundary of the first collecting volume arranged below the first sealing gap in the direction of gravity for collecting lubricant are formed integrally, in particular by a precise first sealing cover. The number of components can thus be kept low. In addition, it has been found that the integral component can be easily inserted into the power shaft from below and can be easily fastened, in particular with screws, to the transmission components, in particular the ring gear and / or the fixed housing part, at the specified end position. For this purpose, the first sealing cover can be used in particular, which is provided in any case and is in any case strong and stable when used in industrial applications to be able to form the shape required for this purpose. Since sliding contact with the relatively rotating power shaft is avoided, the integral component can also be made of plastic in particular and is therefore made by injection molding of plastic, in particular thermoplastic plastic, and can be easily realized as the shape provided by the first sealing gap and the overflow channel.

[0023] Preferably, the intermediate piece is connected to the power shaft to rotate with it, wherein the intermediate piece has an end face facing the first overflow channel for driving the lubricant from the first overflow channel to be discharged radially outward by gravity and / or centrifugal force. The lubricant dripping downward through the overflow channel can hit the lower end of the overflow channel located on the end face of the intermediate piece. Since the intermediate piece is connected to the power shaft to rotate with it, the end face of the intermediate piece can be used as a rotating disk and move the lubricating oil radially outward from the power shaft under the drive of centrifugal force. This prevents the lubricating oil from being transported to the separation joint between the intermediate piece and the power shaft, which eventually causes leakage. The end face of the intermediate piece can extend downward from the radial inside to the radial outside and be inclined relative to the horizontal plane, and therefore, even if the power shaft is stationary and there is no centrifugal force, the lubricant reaching the end face can also flow radially outward on the end face under the drive of gravity. For example, the lubricant can be collected at the radially outer end of the end face and / or guided to prevent leakage.

[0024] Particularly preferably, the power shaft has a step which forms an axial stop for the intermediate piece, wherein the radial inner side of the intermediate piece is arranged radially further inwards than the first overflow channel. Since the inner side of the intermediate piece is at least slightly radially offset from the radial inner edge of the overflow channel, it can be ensured that lubricant reaching the end face of the intermediate piece is conveyed radially outwards away, where the flow resistance is significantly lower than at the separating 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 with respect to the power shaft. Preferably, the intermediate piece is pressed onto the power shaft for rotation therewith and for this purpose is pushed onto the power shaft until the intermediate piece strikes the axial stop of the step.

[0025] In particular, a non-contact second seal is arranged below the first seal between the transmission component and the power shaft in the direction of gravity to provide a sealing resistance to prevent the lubricant from passing through the first seal, wherein, in particular, the second seal has a conical second sealing gap, which is inclined in the direction of gravity and extends from the radial outside to the radial inside against gravity. The non-contact second seal can be connected to the first seal, the subsequent overflow channel and the subsequent end face of the intermediate piece in the direction of lubricant flow. The non-contact second seal is designed in the same way as the above-mentioned first seal. The above explanation of the first seal also applies to the second seal. Therefore, the sealing assembly can basically be a two-stage having two non-contact seals, each of which has a conical sealing gap, and the lubricant can only pass through the sealing gap against the direction of gravity.

[0026] Preferably, the radially inner circumferential surface of the second sealing gap is arranged to be fastened to the transmission component for rotation therewith, and the radially outer circumferential surface of the second sealing gap is fastened to the power shaft for rotation therewith, and / or a second sealing cover is provided which is directly or indirectly connected to the transmission component, wherein the second sealing cover delimits at least a part of the second sealing gap radially on the inside, and / or the second sealing cover has a second collecting volume which is arranged 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 the radially outer boundary of the second sealing gap, and / or the second sealing gap is connected to a second overflow channel which extends downwards in the direction of gravity at least to a large extent, and / or a second ramp is formed between the second sealing gap and the second overflow channel for forming a larger flow cross section than the second sealing gap. Thus, the second sealing portion can be designed partially or completely similar to the first sealing portion, but the second sealing portion is arranged below the first sealing portion 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, the second sealing part has a smaller nominal diameter than the first sealing part.In addition, the second sealing cover can be fastened to the first sealing cover and the second sealing cover is thus only indirectly connected to the transmission component and / or the transmission housing.

[0027] Particularly preferably, the end seal, in particular a labyrinth seal or a contact seal, which communicates with the second sealing gap, is arranged below the second seal in the direction of gravity, wherein the end seal is arranged on a smaller radius than the first sealing gap and the second sealing gap. The labyrinth seal is in particular oiled. The end seal can be arranged at the lower end of the transmission housing. This makes the end seal more accessible and, if necessary, easier and faster to maintain than the first and second seals.

[0028] One aspect also relates to an industrial transmission, in particular a transmission for driving a vertical mill, the transmission having a vertically arranged power shaft for introducing torque, wherein the power shaft is a planetary carrier shaft or sun shaft of a planetary transmission, and the transmission having a transmission component which rotates slower than the power shaft or is at rest during the intended use, wherein the transmission component is in the form of a ring gear and / or a transmission housing of the planetary transmission, and the transmission having a sealing assembly which can be designed and developed as described above for retaining lubricant. Even if lubricant enters the first sealing gap of the first seal against the direction of gravity, the simple and effective design of the first sealing gap can convey the lubricant radially outward and downward without causing wear effects, and thus, with the help of the sealing assembly, a low-maintenance and cost-effective industrial transmission can be achieved. The industrial transmission can be designed and developed in particular as described in DE 10 2013212 464 A1, preferably to form a vertical mill, for example for comminuting solids.

[0029] One aspect also relates to a data cluster, in which data packets are combined in a common file or distributed across different files for representing the three-dimensional shape and / or interaction of all components provided in a sealing component that can be designed and developed as described above or an industrial transmission that can be designed and developed as described above, wherein the data packets are prepared when processed by a data processing device for operating a power tool for additive manufacturing of the device to perform additive manufacturing of the sealing component that can be designed and developed as described above or an industrial transmission that can be designed and developed as described above, in particular by 3D printing, and / or when processed by a data processing device for performing technical simulations to simulate the function of the sealing component that can be designed and developed as described above or an industrial transmission that can be designed and developed as described above and output the simulation results generated in the process for further use, in particular for providing fatigue strength verification according to variable loads and / or variable temperature loads. The data packets of the data cluster are particularly suitable for the construction according to the invention of the corresponding device so that the interactions according to the invention of the components of the device according to the invention can be fully reflected during the processing of the data processing device. The data packets can be stored in particular in a spatially distributed manner, but can also be adapted to each other in such a way that when all data packets are brought together in a common data processing device, the data cluster thus gathered provides all data required for additive manufacturing and / or technical simulation of the device according to the invention with the help of the data processing device. For example, the data packages are each independent parts of a data file library, which are combined to form a data cluster and adapted to each other according to their dimensions relative to each other and / or absolute dimensions and / or material properties corresponding to the respective device according to the invention. The data cluster can represent a virtual embodiment of the respective device according to the invention, in particular a sealing assembly and / or an industrial transmission, in a manner known as a "digital twin", which allows virtual investigations in the form of simulations or real objectification by means of additive manufacturing processes. In particular, the data packages can in each case represent individual implementation components of the respective relevant device according to the invention, and the individual components can therefore be easily assembled in their relative positions and / or relative movability to realize the interaction according to the invention. By using the data packages of the data cluster in a virtual environment during the technical simulation of the individual components of the respective device and their interaction, the physical state and / or physical parameter changes of the relevant device according to the invention over time according to different boundary conditions and / or can be calculated and / or predicted and can be used to check whether the device according to the invention is sufficiently suitable for the intended use based on the assumed construction and taking into account the assumed simulation effects. In particular, with the aid of the respective data package, different components of the respective device can be produced separately and optionally from different materials by additive manufacturing and then assembled to form a prototype of the respective device.Thus, dividing the data of the data cluster into different data packets makes it possible to simply additively manufacture the components of the device in question in the form of a set of components that are movable relative to each other, which are prepared according to the invention for the interaction of the components of a prototype for solving the problem on which the invention is based to be assembled as needed. This makes it possible to economically produce prototypes and / or carry out computer-based simulations to study the function of the sealing assembly and / or industrial transmission, find problems in specific applications, and seek improvements. Even if the lubricant enters the first sealing gap of the first sealing part against gravity, the simple and effective shape of the first sealing gap can transport the lubricant radially outward and downward without any wear, so that by using the sealing assembly, a low-maintenance and cost-effective industrial transmission can be achieved, which can also be easily and cost-effectively checked with the help of the data cluster.

[0030] Therefore, any method of producing such an object based on rapid production technology does not in fact involve an inventive step unless:

[0031] - can present strong arguments as to why a person skilled in the art would not consider using rapid manufacturing techniques to produce such an object, or

[0032] - The product itself has special structural features that demonstrate the value of the invention by solving a specific problem, or

[0033] - objects produced using rapid manufacturing methods produce unexpected effects, or

[0034] - There is no known technology to produce this product other than rapid manufacturing methods.

[0035] In the case of the sealing assembly claimed in the present application, none of the above requirements appear to be met. BRIEF DESCRIPTION OF THE DRAWINGS

[0036] The present invention will be described below with reference to the accompanying drawings in the form of preferred exemplary embodiments, wherein the features shown below may represent one aspect of the present invention alone or in combination. In the accompanying drawings:

[0037] Figure 1 : shows the lower part of an industrial transmission,

[0038] Figure 2 : Shown is Figure 1 Seal assemblies provided for the industrial transmission shown. DETAILED DESCRIPTION

[0039] Figure 1The industrial transmission 10 shown in the middle part can be used in particular for vertical mills for comminuting solids. During the intended use, the industrial transmission 10 is arranged essentially vertically and the main axis of rotation 12 is therefore arranged in the direction of gravity 14. At the lower end of the industrial transmission 10 in the direction of gravity 14, a power shaft 16 serving as an output shaft can output a torque from the industrial transmission 10, which is converted in the industrial transmission 10. The industrial transmission 10 has at least one planetary transmission 18, wherein two or more planetary stages can preferably be provided. The planetary transmission 18 forming the last planetary stage has a planet carrier 20, which is particularly integrally connected to a planet carrier shaft 21, which in the exemplary embodiment shown in the figure simultaneously forms the power shaft 16. The planet carrier 20 has at least one planet gear axle 22, which is fastened to the planet carrier 20 for rotation therewith and on which the planet gears 24 are relatively rotatably mounted via planet gear bearings 26, which are each a sliding bearing or a rolling bearing. Alternatively, the planetary gears 24 may have a planetary gear shaft that rotates with the planetary gears 24 and may be mounted on the side of the planet carrier 20. In particular, at least three, preferably four, five, six or seven planetary gears 24 are provided. The respective planetary gears 24 are radially meshed with the sun gear 27 inside, which is connected to the sun gear shaft to rotate with it. In the exemplary embodiment shown in the figure, the driving power from the drive motor and optionally converted in terms of rotation speed and torque by at least one upstream stage of the industrial transmission 10 is transmitted to the power shaft 16 through the planetary transmission 18 through the sun gear shaft 28. The power shaft 16 can directly or indirectly transmit the converted driving force to the mill shaft of the vertical mill as an output shaft to rotate the mill disk. On the radial outer side, the respective planetary gears 24 are meshed with a ring gear 30 that runs slower than the power shaft 16. In the exemplary embodiment shown in the figure, the ring gear 30 is even stationary and the outer side thereof can form the outer shell of the transmission housing 32, and the power shaft 16 protrudes from the outer shell. In the exemplary embodiment shown, the transmission housing 32 can be assembled from the ring gear 30 and 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 support surface for supporting a drive motor of a 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 the ring gear 30 are mounted on the power shaft 16 via bearings 38, in particular in the form of rolling bearings. The ring gear 30 and the lower housing part 36 form a transmission component 40 of the industrial transmission 10, which is arranged radially outside the power shaft 16.

[0040] The bearing 38 can be lubricated with a lubricant, in particular a lubricating oil, wherein the lubricant can flow out of the bearing 38 and can drip downward in the direction of gravity 14. To avoid leakage, the transmission component 40 and the power shaft 16 are part of a sealing assembly 42, which has a non-contacting first seal 44 and a non-contacting second seal 48, which communicates via a first overflow channel 46 and to which an end seal 50 arranged on a smaller radius is finally connected via a second overflow channel 80.

[0041] like Figure 2 As shown in detail in FIG. 4 , the sealing assembly 42 has a first sealing cover 52, which can be engaged with the protruding first extension 52 into the undercut formed by the power shaft 16 by axial relative movement, 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 sealing portion 44 is formed, which gap is opposite to the direction of gravity 14 and extends from the radial outside to the radial inside. The first sealing cover 52 can be fastened to the lower end face of the transmission component 40 and can define a first collecting volume 58, into which lubricant from the bearing 38 can drip. For lubricant leakage, the lubricant from the first collecting volume 58 needs to pass through the first sealing gap 56 of the first sealing portion 44 against the direction of gravity 14. Furthermore, the first conical seat 54 forming the radially outer circumferential surface of the first sealing gap 56 can rotate at the rotation speed of the power shaft 16 and exert a centrifugal force on the lubricant having reached the first sealing gap 56, and the lubricant is thus transported radially outward and transported radially outward along the first conical seat 54 back into the first collecting volume 58. The first slope 60 is connected to the upper end of the first sealing gap 56 and results in a larger flow cross section than in the first sealing gap 56. The lubricant passing through the first sealing gap 56 can settle on the first slope 60 and flow back to the first sealing gap 56 driven by gravity.

[0042] Even if the lubricant passes through the first seal 44, the lubricant can reach the upward facing end face 62 of the intermediate member 64, which is fastened to the power shaft 16 to rotate therewith, through the first overflow channel 46. The intermediate member 64 is pressed onto the power shaft 16 on a smaller diameter than the first overflow channel 46 until the step 66. The end face 62 of the intermediate member 64 is inclined relative to the horizontal plane so that the inflowing lubricant can flow radially outward through the end face 62 driven by gravity. In addition, the intermediate member 64 can rotate at the rotation speed of the power shaft 16 and can assist the radial outward movement of the lubricant by the applied centrifugal force. The lubricant can enter the second collection volume 70 defined by the second sealing cover 68 from the end face 62 of the intermediate member 64. The second sealing cover 68 can be engaged with the protruding second extension 72 into the undercut formed by the intermediate member 64 by axial relative movement, 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 sealing portion 48 is formed, which extends from the radial outer side to the radial inner side against the direction of gravity 14. The second sealing cover 68 can be fastened together with the lower end surface of the transmission device component 40 and / or the lower end surface of the first sealing cover 52. For the leakage of lubricant, the lubricant from the second collection volume 70 needs to pass through the second sealing gap 76 of the second sealing portion 48 against the direction of gravity 14. In addition, the second conical seat 74 forming the radially outer circumferential surface of the second sealing gap 76 can rotate at the rotation speed of the power shaft 16 and exert centrifugal force on the lubricant that has entered the second sealing gap 76, so that the lubricant is radially transported outward and transported radially outward along the second conical seat 74 back to the second collection volume 70. The second slope 78 is connected to the upper end of the second sealing gap 76 and results in a larger flow cross section than in the second sealing gap 76. The lubricant passing through the second sealing gap 76 can settle on the second slope 78 and flow back to the second sealing gap 76 under gravity drive. The end seal 50, for example in the form of a greased labyrinth seal, can prevent the lubricant from leaking out, even if the lubricant also passes through the non-contact second seal 48 and is guided to the end seal 50 via the second overflow channel 80. In particular, the end seal 50 is designed only as a dust seal, the purpose of which is to prevent dust from entering the industrial transmission 10. Since very little lubricant, if any, reaches the end seal 50, a low sealing effect of the end seal against lubricant leakage is sufficient.

Claims

1. A sealing assembly (42) for an industrial transmission device (10), comprising: a vertically arranged lower power shaft (16) for exchanging torque with the industrial transmission (10), A transmission device component (40) of the industrial transmission device (10), the transmission device component being arranged radially outside the power shaft (16), wherein: The power shaft (16) has a higher rotational speed than the transmission member (40) during a predetermined operation, Wherein, a non-contact first sealing portion (44) is arranged between the transmission device component (40) and the power shaft (16), The first sealing portion (44) has a conical first sealing gap (56) which is inclined along the gravity direction (14) and extends from the radial outer side to the radial inner side in the opposite direction of the gravity direction (14), and the first sealing portion has a first overflow channel (46) which extends downward along the gravity direction (14). The first sealing gap (56) is connected to the first overflow channel (46), characterized in that the first overflow channel (46) ends below the first sealing gap (56) in the gravity direction (14) and is in the form of an annular gap, wherein the overflow channel (46) has a substantially constant flow cross section and is in the form of an annular gap in order to avoid a labyrinth seal.

2. The seal assembly (42) of claim 1, wherein: A radially inner circumferential surface forming the first seal gap (56) is fastened to the transmission component (40) for rotation therewith, and a radially outer circumferential surface forming the first seal gap (56) is fastened to the power shaft (16) for rotation therewith.

3. The sealing assembly (42) according to claim 1 or 2, wherein: The transmission component (40) is rotatably mounted 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. The sealing assembly (42) according to claim 1 or 2, wherein: A first sealing cover (52) is provided which is connected to the transmission component (40), wherein the first sealing cover (52) delimits at least a portion of the first sealing gap (56) radially inwardly.

5. The seal assembly (42) of claim 4, wherein: The first sealing cover (52) has a first collecting volume (58) which is arranged below the first sealing gap (56) in the direction of gravity (14) for collecting lubricant.

6. The sealing assembly (42) of claim 1 or 2, wherein: The power shaft (16) has an undercut first conical seat (54) for the radially outer boundary of the first sealing gap (56).

7. The sealing assembly (42) of claim 1 or 2, wherein: A first ramp (60) is formed between the first sealing gap (56) and the first overflow channel (46) for forming a larger flow cross section than in the first sealing gap (56).

8. The sealing assembly (42) of claim 1 or 2, wherein: The radial outer channel wall of the first overflow channel (46), the radial inner circumferential surface forming the first sealing gap (56), and the collecting surface for the lower boundary of the first collecting volume (58) are integrally formed, and the first collecting container is used to collect lubricant. The first collecting container is arranged below the first sealing gap (56) in the gravity direction (14).

9. The seal assembly (42) of claim 8, wherein: The radially outer channel wall of the first overflow channel (46), the radially inner circumferential surface forming the first sealing gap (56), and the collecting surface for the lower boundary of the first collecting volume (58) are formed entirely by only one first sealing cover (52).

10. The sealing assembly (42) of claim 1 or 2, wherein: An intermediate member (64) is connected to the power shaft (16) for rotation therewith, wherein the intermediate member (64) has an end surface (62) facing the first overflow channel (46) for gravity-driven and / or centrifugal-driven radial discharge of lubricant from the first overflow channel (46) to the outside.

11. The seal assembly (42) of claim 10, wherein: The power shaft (16) has a step (66) which forms an axial stop for the intermediate piece (64), wherein the radial inner side of the intermediate piece (64) is arranged radially further inward than the first overflow channel (46).

12. The seal assembly (42) of claim 1 or 2, wherein: A non-contact second sealing portion (48) is provided between the transmission component (40) and the power shaft (16) below the first sealing portion (44) along the gravity direction (14) for providing a sealing resistance to prevent lubricant from passing through the first sealing portion (44), wherein the second sealing portion (48) has a conical second sealing gap (76) which is inclined along the gravity direction (14) and extends from the radial outer side to the radial inner side in the opposite direction of the gravity direction (14).

13. The seal assembly (42) of claim 12, wherein The radially inner circumferential surface forming the second sealing gap (76) is fastened to the transmission component (40) for rotation therewith, and the radially outer circumferential surface forming the second sealing gap (76) is fastened to the power shaft (16) for rotation therewith, and / or A second sealing cover (68) is provided which is directly or indirectly connected to the transmission component (40), wherein The second sealing cover (68) radially delimits at least part of the second sealing gap (76) on the inside, and / or The second sealing cover (76) has a second collecting volume (70) arranged below the second sealing gap (76) along the gravity direction (14) for collecting and / or discharging lubricant, and / or The intermediate piece (64) has a second undercut conical seat (74) for the radially outer boundary of the second sealing gap (76), and / or The second sealing gap (76) is in communication with a second overflow channel (80), the second overflow channel extending downwardly along the gravity direction (14), and / or A second slope (78) is formed between the second sealing gap (76) and the second overflow channel (80) to form a larger flow cross section than in the second sealing gap (76).

14. The seal assembly (42) of claim 12, wherein: An end seal portion (50) connected to the second seal gap (76) is arranged below the second seal portion (48) along the gravity direction (14), wherein the end seal portion (50) is arranged on a smaller radius than the first seal gap (56) and the second seal gap (76).

15. The seal assembly (42) of claim 14, wherein: The sealing portion (50) is a labyrinth seal or a contact seal.

16. An industrial transmission (10) having a vertically arranged power shaft (16) for introducing torque, wherein: The power shaft (16) is a planetary carrier shaft (21) or a sun shaft (28) of a planetary transmission (18), and the industrial transmission has a transmission component (40) which rotates slower than the power shaft (16) or remains stationary during the intended use, wherein the transmission component (40) is in the form of a ring gear (30) and / or a transmission housing (32) of the planetary transmission (18), and the industrial transmission has a sealing assembly (42) as described in any one of claims 1 to 13 for retaining lubricant.

17. The industrial transmission device (10) according to claim 16, wherein: The industrial transmission is used to drive a vertical mill.

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