WO2013064384A1

WO2013064384A1 - Bearing component, bearing, drive shaft, and underwater power plant

Info

Publication number: WO2013064384A1
Application number: PCT/EP2012/070835
Authority: WO
Inventors: Johannes Goetz; Fred Menig
Original assignee: Aktiebolaget Skf
Priority date: 2011-11-02
Filing date: 2012-10-22
Publication date: 2013-05-10
Also published as: EP2773865A1; DE102011085611A1

Abstract

The invention relates to a concept for sealing a bearing component (110; 110a; 110b) for a bearing (100), which bearing component has a fastening possibility (120) for fastening to a component (130) to be supported, wherein the bearing component (110; 110a; 110b) or the component (130) to be supported has a recess (115, 117) for a seal (119), in such a way that the bearing component (110; 110a; 110b) can be connected to the component (130) to be supported at least a watertight manner. The concept also provides for an underwater power plant having a bearing component (110; 110a; 110b) or a bearing (100) and a drive shaft (130), which are mechanically coupled to one another and between which a seal (119) is located for sealing.

Description

B e s e c tio n Bearing component, bearing, drive shaft and underwater power plant

The present invention is in the field of underwater power plants, in particular the storage and sealing of drive shafts in underwater power plants. Submarine power plants are already known from the field of conventional technology. In the following, well-known storage concepts for underwater power plants are briefly summarized. The publication DE102009005556A1 discloses a concept for flushing of underwater power plants, which consciously dispenses with encapsulation of the bearings used. In such constructions, the area in direct contact with the surrounding water must be protected against excessive sediment. Furthermore, the growth in this area must be limited. One of the measures involved is to rinse the flooded area and, in particular, the bearings and the components associated therewith, such as sealing elements and the like.

One concept provides for applying at least one flushing connection to an underwater power station, by means of which a flushing medium can be supplied to the system from outside. Accordingly, there is no delivery system, such as a pump or the like, for the flushing medium in the system itself between the external flushing connection and the area to be flushed. Furthermore, an additional filter system is dispensed with. Instead, the flushing medium is supplied at such an overpressure at the external flushing connection that there is a sufficiently strong flow through the area to be flushed and an outflow to the outside area, whereby sediments and, preferably, an originally present growth, are transported to the outside.

A concept for optimized power control and control of underwater power plants is disclosed in the publication DE102008053732B3. The publication DE102008031615A1 shows a generator unit which can be handled as a whole and can be mounted as a unit, which can be transported and mounted separately from the actual drive shaft of an underwater power plant. This includes a generator rotor and a generator stator, the basic components of an electric generator. In addition, a generator housing is part of the generator unit. The control and power components of the electric generator can be additionally included in the generator assembly.

The document DE102008061912A1 deals with bearing cushions, for example for seawater suitable slide bearings. For a hydrodynamically building up lubricating film and the associated parabolic pressure development for soft or elastic sliding linings, a concave deflection occurs in the central area. This leads to a Lagerpalterweiterung and a slump in the pressure distribution in the central region of the sliding surface. This is counteracted by the fact that the material thickness of the sliding lining in the direction of the surface normal of the sliding surface is adapted to the lubricant film pressure occurring during operation. In the areas of high pressure, which lie around the surface center of the sliding surface, a reduced material thickness is used, while the edge regions have a high material thickness. In this case, the profile of the sliding surface is maintained, which typically corresponds to that of the mating surface. The adjustment of the material thickness of the sliding lining is carried out by a corresponding profiling of the bearing surface on the base body, which is opposite to the back of the sliding lining. In the simplest case, a raised base is provided in the central region of the support surface of the base body. A more accurate adjustment can be effected by a multiple stepped or convex course of the support surface.

Document DE102008006899A1 discloses a concept for supporting a drive shaft of an underwater power plant. Here, a bearing arrangement for supporting a shaft is provided, wherein the bearing arrangement has at least one radial sliding bearing and at least one axial sliding bearing and wherein the bearing arrangement can be lubricated by water penetrating from the outside.

FIG. 3 shows a schematic structure of an underwater power plant. FIG. 3 illustrates a nacelle 300 having a segmented structure. Close to the nacelle 300 in the front area, a hood 305 and a propellerformige Hydro turbine 310 on. The nacelle 300 includes two segments 315 and 320 that contain the drive shaft 325. In another segment 330 is a generator 335 which is coupled to the drive shaft 325. Another hood 340 terminates the underwater power plant after the generator 335.

The hood 305 forms with the water turbine 310, a circumferential unit which is coupled to the drive shaft 325. For storage of the drive shaft 325 a plurality of plain bearings are provided. In the front side of the drive shaft 325 facing the water turbine 310 there is a radial slide bearing 345. In the rear region of the drive shaft 325 facing the generator 335 there is another radial slide bearing 350. Axial forces of the drive shaft are absorbed by the two axial slide bearings 355 and 360 which have one the drive shaft 325 connected track disc 365 axially support.

The sliding bearings 345, 350, 355 and 360 can be designed to be seawater resistant, in particular water lubricated. This makes it possible to flood the entire interior of the machine nacelle 300 and to dispense with elaborate seals, in particular the bearings.

The sliding bearings used 345, 350, 355 and 360 are partially realized directly on the drive shaft 325. For the realization of the radial sliding bearings 345, 350 very hard coatings are applied to the two respective ends of the shaft 325 over a width of about 100 - 4000 mm, which then each represent the inner ring for one of the radial sliding bearings 345,350. For example, high-speed flame spraying (also HVOF, derived from high-velocity oxygen-fuel) or another thermal coating method for surface treatment can be used as the coating method. In addition, at these points, first a steel ring can be applied by welding and on the surface of which the coating takes place. The warehouse runs directly in the water or seawater. In the conventional approach, portions of the drive shaft 325 are provided with a coating, or is carried out first an attachment of Lag erring on the respective shaft ends by welding and then a coating of these rings. In addition, the coated areas must be reworked, eg by Grind. An exchange of the bearings in case of damage is not directly possible, so that in case of damage the complete shaft has to be repaired or exchanged.

A disadvantage of the conventional concepts is the need to handle a large one-piece shaft. The length of such a drive shaft may be several meters, the diameter may also be over one meter. Typical values are 0.1 - 15 m in length with a diameter of 30 mm - 6000 mm and this with a power of 0.5 kW - 15 MW. In addition, the weight of such a drive shaft can easily amount to several tons, a typical weight would be 0.01 - 100 1.

A problem now is that a very large and heavy drive shaft 325 handled, transported, clamped on a machine, if necessary, must be coated. This is very expensive. In addition to the handling described above during assembly and bearing maintenance, handling such a large wave is generally a problem. Especially under water, where such a wave is usually roped, moving and aligning presents a great challenge Weight of these waves brings a high load for the bearings used.

It is therefore the object of the present invention to provide an improved concept for supporting a drive shaft for an underwater power plant.

The object is achieved by a bearing component, a bearing, a drive shaft and an underwater power plant according to the independent claims.

Exemplary embodiments can be based, for example, on the knowledge that the acting torques in an underwater power plant are very large. Flanges used for mechanical coupling of bearings and shafts must be dimensioned accordingly. In addition, embodiments may be based on the knowledge that hollow shafts can be used as drive shafts in underwater power plants. To reduce the load on the bearings, they can be filled with air or a gas. The resulting buoyancy can reduce the load on the bearings. In addition, embodiments may be based on the core idea that, in particular when filled with air or gas hollow shafts, the flanges should be sealed to prevent ingress of water into the hollow shaft or escape to avoid the gas from the hollow shaft. Embodiments may therefore provide a seal between these components.

Embodiments may also be based on the knowledge that, contrary to the conventional sealing by welding and a correspondingly large dimensioning of the flanges, also seals can be provided. These can achieve a good sealing effect, in particular, when they are attached to the respective components, such as e.g. Bearings, shafts and flanges are provided in recesses or grooves provided for this purpose. Here and below, under the terms component or component, e.g. Components of an underwater power plant, i. Bearing ring segments, bearing rings, bearings, shafts, flanges provided on these, etc.

Embodiments can therefore provide a bearing component for a bearing, which comprises a fastening possibility for fastening the bearing component to a component to be stored, the bearing component having a recess for a seal such that the bearing component can be connected to the component to be supported at least in a water-tight manner. In embodiments, the bearing component may be formed as a bearing segment, bearing disk segment, bearing ring segment, bearing ring or bearing disk. The watertight connection can prevent, for example, that when used under water, water enters the interior of a hollow shaft or a bearing. The bearing may for example be a radial bearing or a thrust bearing. In this respect, embodiments include bearing rings, bearing ring segments, bearing washers or their segments of a thrust bearing, etc.

In some embodiments, it may also be provided that the sealed interior of a construction of a bearing and a shaft is under pressure, that is, for example, filled under pressure with gas or air. This pressure can then counteract the pressure of the water. In other embodiments, the construction may also have a vacuum inside, for example, to further increase buoyancy. In embodiments, the bearing component with the component to be stored gas or airtight be connected. In the case of a thrust bearing, the bearing component can be designed as Axiallagerscheibensegment or as Axiallagerscheibe, so that the bearing ring segment or the bearing ring itself can serve as a seal of the hollow shaft. In some embodiments, seals may be particularly advantageous if frictional coatings are provided on the connecting surfaces of the components in order to increase a frictional force between the components. Thus, on the one hand can be dispensed with welding and, due to the frictional force between the components, can also be dispensed with mounting means, such as holes, bolts, screws, etc. However, the advantage of reducing the mounting means may be a disadvantage of the difficult seal. Embodiments can remedy this disadvantage by means of recesses provided on the components, since the recesses permit the use of seals, which in turn make it possible to seal the components with one another.

In addition, embodiments may provide the necessary fastening means, such as e.g. Screws or bolts, which are used to attach the bearing component to a component to be stored, as possible to minimize costs, i. For example, with as few screws as possible. This can be achieved by applying a coating to the bearing component or to the component to be supported, which increases a frictional force between the bearing ring / component and the component to be supported. Due to the increased frictional force, fastening means, such as e.g. Screws or bolts can be saved. This reduces the maintenance and assembly costs, as the corresponding parts can thus be assembled and disassembled faster. It does not need to be omitted by the above-described sealing measures on a use of air or gas filled hollow shafts, or standing on vacuum components. Embodiments may therefore provide a bearing component comprising a coating which increases a frictional force between the bearing component and the component to be supported and adjacent the recess to the coating.

Another core idea of some exemplary embodiments lies in equipping a bearing or the bearing component with a flange, so that this or these can be frictionally coupled to a drive shaft and / or in a corresponding coating of the flange. Such a coupling can then take place at both ends of the drive shaft, ie in the case of an underwater power plant for the storage of the area facing a water turbine and / or of a generator facing a water turbine. Empire. The radial bearings or thrust bearings can be flanged to the respective ends of the shaft. The bearings can then consist of one piece, a welding of rings on the shaft can be omitted. The handling of the bearings can thus be facilitated in their manufacture. These can be coated as desired, a coating of the shaft with a lubricious coating can be omitted. For sealing, accordingly, a recess for a seal on the flange and / or on the shaft or its flange may be provided.

In embodiments, a flange on a bearing component, e.g. be provided at the axial end. This can also be composed of several segments, each of which may be the same or different. In embodiments, for example, bearing ring segments may have corresponding flange segments. Therefore, when the flange is described below, it may also be one-piece, or multi-piece, i. composed of flange segments, be formed. In embodiments, the coating or the recess can therefore also be provided on the flange.

This flange is used for. B. for attachment of the bearing component to the drive shaft. In embodiments, the flange may be mounted both on a bearing inner ring and on a bearing outer ring as a bearing component. In embodiments, the bearing ring or the bearing disk may be formed integrally with the flange. In other embodiments, bearing ring and flange may also be formed in several pieces.

Due to the mechanical separation of bearing and drive shaft, maintenance can be considerably facilitated. During maintenance work on the bearing or the shaft, it is no longer necessary to change the entire drive shaft or the entire drive train, but the drive shaft and bearings can also be removed and serviced separately after the mechanical decoupling. This advantage increases with the number of mechanically decoupled bearings. In other words, the drive shaft may be supported by a plurality of decoupled or flanged bearings, with reduced maintenance due to the possibility of separate handling for each decoupled bearing. In addition, the maintenance effort by the friction force increasing coating be further reduced, since the fasteners, eg for the attachment of the bearing to the drive shaft, and thus assembly and maintenance times can be reduced or minimized. On a hollow shaft provided valves may also allow to fill them after installation with air or gas. For example, these can be correspondingly sealed against each other via correspondingly provided recesses on the components. In embodiments, a recess for a seal can accordingly be adapted to a component in order to seal a cavity which may be located in the drive shaft and / or in the bearing when a drive shaft is fastened.

Accordingly, embodiments can also provide a bearing with a bearing component described above. In addition, embodiments may also include a drive shaft for an underwater power plant, which has a recess for a seal, so that the drive shaft with a bearing component is at least watertight connectable. The drive shaft can be designed as a hollow shaft, but there are also embodiments possible in which the drive shaft is solid and yet waterproof to the bearing component is connected to seal the bearing component or a gap between the drive shaft and the bearing component. The drive shaft may have a coating which increases a frictional force between the drive shaft and a bearing component to be attached thereto, the recess being adjacent to the coating.

Furthermore, embodiments may also include an underwater power plant with a bearing component or a bearing and a drive shaft as described above, wherein the bearing component is at least watertightly connected to the drive shaft. Alternatively, the underwater power plant may include a bearing component, a bearing ring segment, a bearing ring or a bearing without recess and a drive shaft without recess, provided that they are mechanically coupled to each other and there is a seal between them for sealing. Embodiments of underwater power plants and their components may be generally adapted for use underwater. For example, embodiments may be adapted for use in oceans, in rivers, locks, barrages, etc., ie generally for use in salt and fresh water. In addition, embodiments may be designed for different depths, variable water pressure, temperatures, etc. Embodiments may allow separate manufacture of the bearings. In addition, reduce the weight of the drive shaft and the weight of the bearing. Overall, the logistics costs and associated costs can be reduced.

In one embodiment, the processing of the now smaller components, i. Bearings and drive shaft, to be separated from each other. As a result, smaller production plants can be used, which can further reduce manufacturing costs. In addition, the manufacturing precision can be increased and the bearings can be individually coated individually. As a result, there are also other possibilities with regard to the coating, such as e.g. Dipping / bath treatment, as a direct coating on the shaft surface is no longer necessary. Also, there is no longer any distortion due to welding and no cleaning work is required, which would occur in conventional concepts after welding. By means of recesses provided on the components, gaskets can be used during the assembly which make it possible to completely seal the components with one another.

The complex conventional system can thus be broken down by embodiments into several simplified subsystems. The individual subsystems can be processed more expediently, or they can only be made accessible to certain process or processing steps due to the decomposition. This can allow a better adaptation or optimization of the processes to the subsystems and thus a cost reduction. Downtimes of the system can be reduced, in particular by the fact that now storage changes are possible on site. Also, by exemplary embodiments, a stock preparation without large logistics effort possible. This also allows a cost reduction in production - assembly and maintenance can be achieved. In embodiments, bearings can be processed separately, thereby tribologically more favorable surface designs are possible, for example, an introduction of lubrication and wells suitable for application is facilitated and not least, the provision of recesses for the seals. In addition, lubricant lines and lubricant delivery systems can be more easily introduced into the system, ultimately reducing maintenance and, hence, operating costs. By coating the drive shaft or the mounting side of the bearing or both of the mounting effort of the decoupled bearing can be reduced. The fastening means can be correspondingly reduced if the friction between bearing ring segment or bearing ring or bearing disk can be correspondingly increased on its mounting side. Accordingly, less fasteners, such as screws, rivets, etc. are necessary to ensure a secure attachment. To ensure a secure attachment, a twisting or Mitwandern of the bearing ring in the circumferential direction must be prevented. This should also be ensured if there should be a contact between bearing inner and outer bearing ring, or between the bearing disk and the pulley guide.

Embodiments may therefore provide a coating of the bearing component and / or a component to be supported in such a way that a frictional connection between the respective bearing ring and the component to be stored, such as. the drive shaft increases. The coating may have various properties, e.g. an extremely large friction coefficient. The opposite side can also be coated, i. in embodiments, both the bearing component, e.g. the bearing ring, or its segment, as well as the component to be stored, e.g. a drive shaft, be coated. The recesses for the seal may also lie within the coating, in some embodiments the recesses may also relate only to the coating, i. a recess can also be realized by an interruption of the coating.

In embodiments, the segments can be mounted on the shaft in such a way that the side with the friction coating lies on the end face of the drive shaft or on the shaft shoulder and / or on the shaft axis. The attachment can be done eg by means of screws, bolts, pins, rivets, gluing, plugging, etc. Due to the friction coating, the resistance of the segments against co-rotation in the circumferential direction can be greatly increased. This may result in embodiments that significantly fewer fasteners are required for the attachment of the segment pieces to the shaft shoulder. As a result, the wave itself is weakened less. At the same time, the recesses for the seal can be provided on the end face of the drive shaft, for example, such that a recess on the drive shaft with a recess on the bearing ring or the bearing plate or its / Flange covered. In the resulting cavity, a seal can be provided such that it jammed between the recesses and thus ensures a reliable seal.

The advantages mentioned can occur in particular in embodiments of plain bearings, since here, especially when used in water-lubricated underwater power plants, high starting torques and thus startup loads can occur. The overcoming of these high starting torques can be facilitated precisely by the coating and the increased frictional force in embodiments, which does not need to be dispensed with a use of the cavity to achieve additional buoyancy of the shaft through the provided recesses and seals.

Accordingly, exemplary embodiments can provide, for example, a coating with a friction lining and a seal on the side surfaces of the bearings, the shaft, a rotor, a generator or a turbine.

Embodiments of the present invention will be explained in detail below with reference to the accompanying drawings. Show it

Figures la-e embodiments of bearing components, bearing rings, or bearing ring segments, and drive shafts;

Figure 2a shows another embodiment of a bearing ring, or of bearing ring segments;

FIG. 2b an overview of different sealing cross sections in exemplary embodiments;

Figure 2c is an overview of different mounting options and sealing options in embodiments; and

Figure 3 is a conventional underwater power plant.

1 a shows an embodiment of a bearing component in the form of a bearing ring 110 a, or a bearing ring segment 110 a. Under a bearing ring segment 110a is in the following part of a bearing ring 110a understood. Accordingly, the bearing ring segment may, for example, comprise a certain angular range of a bearing ring 110a, ie, in embodiments, a plurality of identical or unequal bearing ring segments may form a bearing ring. Embodiments of bearing ring segments are not limited to a specific subdivision of a bearing ring in bearing ring segments, there are any axial and radial segmentation conceivable. In addition, in embodiments both radial bearing and thrust bearing segments may occur, an example of a radial bearing is explained in the figure la. In the figure, while the entire radial bearing 100 is shown with an inner ring 110a and an outer ring 140 in a cross section. In other words, the bearing ring 110a, or the bearing ring segment 1 10a, in the embodiment of Figure la as a bearing inner ring 110a, or as a bearing inner ring segment 110a, executed. In the following discussion of embodiments, reference will be made to a bearing ring, wherein the embodiments also refer to a bearing ring segment, to bearing disc segments and to bearing discs. In a repetition of the same versions for a bearing ring and a bearing ring segment can be waived in part in favor of clarity. This also applies to designs with respect to a flange or a flange segment.

In addition, FIG. 1a shows a part of the drive shaft 130. The bearing ring segment 110a for a radial bearing 100, or generally the bearing component for a bearing, comprises a fastening possibility for fastening the bearing ring segment 110a to a component 130 to be supported, the bearing ring segment 110a forming a recess 115 for a seal 119, such that the bearing ring segment 110a is at least watertight connectable to the component 130 to be stored. The same applies to an embodiment of an entire bearing ring 110a or generally a bearing component, which may be formed in embodiments as a bearing segment 110, 110a, 110b, bearing disk segment, bearing ring segment 110, 110a, 110b, bearing ring 110, 110a, 110b or bearing disk. In the figure la and below, the individual components are each provided only at the top in the figure with reference numerals. In the cross-sectional views, the components in the lower part of the respective figure can also be seen. The recesses 115, 117 may accordingly be, for example, closed grooves running in the end face of the components. Embodiments also include bearing components such as bearing rings, bearing washers or segments thereof of thrust bearings. In this respect, the term bearing component for axial bearings also designates bearing disks. For example, they can provide a thrust washer to which a drive shaft 130 is attached. The drive shaft 130 may, for example, be divided into two parts, between which the thrust bearing disc is arranged. The axial bearing disk can then have recesses for sealing elements on one or both sides for sealing the respective drive shaft parts relative to the axial bearing disk. For example, a thrust washer segment or a thrust washer may be adapted for use in a journal bearing of a drive shaft 130 of an underwater power plant. However, embodiments can also generally provide the use in plain bearings. In embodiments, seals may also be provided between the segments. As a result, for example, a backwashing of the segments can be prevented. In addition, a seal or sealant between the segments may help to close a manufacturing and / or assembly gap between the segments. This can also help to reduce or prevent breaks in the lubricating film during operation. For example, sealing lips can be inserted between the segments here. In embodiments, the Axiallagerscheibensegmente or radial bearing ring segments may also have vulcanized sealing lips or seals.

Furthermore, FIG. 1 a shows that the bearing component, ie for example the bearing ring segment or the bearing ring 110 a, comprises a coating 125 which increases a frictional force between the bearing ring segment 110 a and the component 130 to be supported. 1a shows the coating 125 using the example of the inner bearing ring 110a. In addition, Fig. La shows a coating 125 on both sides, ie, both the inner bearing ring 110a is coated according to one embodiment and the drive shaft 130. The drive shaft itself also also has a recess 117, which in this embodiment, the recess 1 15 of the bearing ring. 1 10a opposite. In embodiments, recesses 115, 117 may generally be designed as grooves, trenches, bevels or bevels, coating interruptions, depressions, etc. In embodiments, a recess 115, 117 may be formed such that, in interaction with the bearing component 130, a cavity for a seal 119 results, as will be explained in more detail below. In general, exemplary embodiments therefore also include a drive shaft 130 for an underwater power plant, which has a recess 117 for a seal, such that the drive shaft 130 can be connected to a bearing component, for example a bearing ring segment 110a or a bearing ring 110a, at least in a water-tight manner. The drive shaft 130 can be designed as a hollow shaft or solid, depending on where the cavity to be sealed is located in the drive train. The drive shaft 130 may include a coating 125 that increases a frictional force between the drive shaft 130 and a bearing component to be attached thereto, such as a bearing ring segment 110a or a bearing ring 110a to be attached thereto, the recess 117 being adjacent the coating 125.

The bearing component may be connectable to the component 130 to be stored gas or air tight, i. the compound can be sealed in such a way that even a pressurized gas does not escape. In addition, the seal can be designed such that even if there is a vacuum in the interior of the hollow shaft sealed with the bearing and the whole assembly is under water, no water can penetrate into the interior of the arrangement. The water pressure can be considerable, especially at greater depths. The water pressure increases by about ever per 10m water depth. The seal may be formed in embodiments to withstand a water pressure of lbar, 5bar, 10bar, 20bar, 50bar, 100bar, 200bar, 500bar or 1000bar. It should be noted that in the following the coating in the figures is shown on both sides, but embodiments may also comprise one-sided coatings. In addition, the coating in the figures for the sake of clarity is shown locally limited. In embodiments, the coating may also cover larger areas such as e.g. include entire side surfaces or surfaces.

In exemplary embodiments, the bearing component, for example the bearing ring segment 110a or the bearing ring 110a, can have a flange 120 as an attachment at one axial end, with the flange 120 having the recess 115 and / or the coating 125. In simple embodiments, the mounting option can also be realized for example by drilling. Such an embodiment illustrates the Fig. Ib. The bearing ring 110a shown there for a radial bearing 100 for a drive shaft 130 has at one axial end a flange 120, wherein the flange 120, the mounting option for mounting the bearing ring 110a at the has drive shaft 130. The attachment option may include, for example, fasteners, such as holes, threads, weld studs, weld nuts, screws, lands or grooves, clamps, etc. Under a flange here is a bridge, a nose, a spring, an extension oa. understood, which serves for attachment to another component. The respective other component can likewise have fastening means or fastening possibilities such as bores, threads, screws, welding studs, webs or grooves, clamps, etc. Moreover, in embodiments, the flange 120 may include grooves, lands, or teeth to, for example, achieve secure engagement with the drive shaft 130 and secured against rotation with the drive shaft 130. The drive shaft may be designed accordingly in embodiments.

As can be seen from the figures la and lb, the bearing ring segment 110a or the bearing ring 110a adapted to support a drive shaft 130 of an underwater power plant, wherein the recess 115 is adapted to the seal 119 to when fixed to a drive shaft 130, a cavity the drive shaft 130 and / or a bearing seal. In embodiments, the drive shaft 130 may be configured as a hollow shaft or solid. In embodiments, for sealing the bearing ring 110 a at the axial end facing away from the component to be supported, a further seal may be provided. For example, a kind of cover can be made here or it can result in a cover with or through a housing. For example, then the cavity of a drive shaft can be extended by that of a bearing ring and closed by a housing.

In exemplary embodiments, the bearing ring 110 can be embodied as a bearing inner ring 110a, as shown in FIGS. 1a and 1b, or as a bearing outer ring 110b. The figure lc shows an embodiment in which the bearing ring 110b is formed as a bearing outer ring 110b. In other words, the flange 120 may also be attached to a bearing outer ring 110b. In the figure lc of the bearing inner ring is designated by the reference numeral 140. The recess 115 is likewise located on the flange 120 in this embodiment. In such an exemplary embodiment, the sealing of an Nes cavity of the drive shaft 130 through the flange 120 itself done, in that it can form a cover. In other embodiments, the subsequent components, not shown in the figures, such as additional shafts, a housing, or a bearing may provide for sealing of the bearing 100. In further embodiments, the flange 120 may also be provided on a thrust washer. For example, this may include the drive shaft 130 or extend into this (hollow shaft) and thereby have the recess 115 for the seal 119.

As can be seen in the exemplary embodiments illustrated in FIGS. 1 a, 1 b and 1 c, the flange 120 can extend along the axis of rotation of the bearing 100, that is to say in the axial direction. As the embodiments listed above, the flange 120 may at least partially enclose the drive shaft 130 and screwed, riveted, or the like, for example, with this. become. Since in embodiments also hollow shafts are used, it is also conceivable that the flange 120 also projects into the drive shaft 130 and is fastened from the inside to the drive shaft 130, where in these cases then the recess 115 for the seal 119 are can. The drive shaft 130 may have radial mounting holes in embodiments. Depending on whether the flange 120 overlaps the input shaft 130 internally or externally, the attachment holes, threads or generally the attachment means may be provided inside or outside the drive shaft 120.

Another embodiment is shown in FIG. The figure ld again shows a radial bearing 100 with a bearing ring 110a, which is designed here as a bearing inner ring 110a. In addition, FIG. 1 d shows a bearing outer ring 140. In this exemplary embodiment, furthermore, the flange 120 can be seen, which also has a radial extension here. The radial extent of the flange 120 allows attachment to the end face of the drive shaft 130, which then may have mounting holes in the axial direction, for example. The recess 1 15 is also located on the side of the flange 120 which extends in the radial direction in this exemplary embodiment. The coating 125 can accordingly also be located on the end face of the flange 120 in exemplary embodiments.

The figure le shows a further embodiment in which the bearing ring 110b is formed as a bearing outer ring 110b. Again, it can be seen that the flange 120 next an axial extension also has a radial extent with a correspondingly arranged coating 125 and correspondingly arranged recess 115. Conceivable are also other embodiments in which the flange 120 has only a radial extension, that is, not primarily in the axial direction of the bearing ring 110 projects away. In other words, the bearing ring 110 or the bearing component in embodiments may have a flange 120 which extends in the axial and / or radial direction and has the coating 125 and / or the recess on a side facing the component 130 to be supported. Embodiments may also include a bearing component 110, 110a, 110b, a bearing ring segment 110, 110a, 110b or a bearing ring 110, 110a, 11bb for a bearing 100 for a drive shaft 130 of an underwater power plant. Furthermore, a flange 120 or a flange segment 120 can be provided at one axial end, wherein the flange 120 or the flange segment 120 has a fastening possibility for fastening the bearing ring segment 110, 110a, 110b to the drive shaft 130 and / or a recess 115 for a seal 119 has. Furthermore, exemplary embodiments may include the coating 125, which increases the frictional force to the component 130 to be stored.

The bearing ring segment 110, 110a, 110b can also be designed as a bearing inner ring segment 110a or as a bearing outer ring segment 110b. The flange 120 or the flange segment 120 may extend in embodiments in the axial and / or radial direction. In other words, the frictional force between the bearing ring segment or the bearing ring or the bearing component 110, 110a, 110b and the component 130 to be supported can be increased along the axis of rotation of the component 130, ie on an axial contact surface (contact surface with axial extension). with the device 130, as shown for example in Figures lb and lc. In further exemplary embodiments, as shown for example in FIGS. 1 a, 1 d and 1 e, the contact surface can also have a radial extension. The recess 115 can consist in a simple interruption of the coating 125, ie it can simply represent a recess in the coating. In other embodiments, the coating 125 in the region of the recess 115 may also have a smaller thickness, so that the recess 115 may be embodied for example as a depression in the coating. Accordingly, exemplary embodiments also include a bearing 100, for example a sliding or roller bearing 100, which has one of the abovementioned bearing components, such as bearing rings 110, 110a, 110b, bearing disks or their bearing segments 110, 110a, 110b. FIG. 2a shows a further embodiment in which a section of a bearing 100 is shown on the left side. From the bearing 100, the bearing ring 110 can be seen. It can also be seen that the bearing ring 1 10 has a flange 120, via which the bearing ring 110 can be attached to the drive shaft 130. In addition, the coating 125 can be seen on the side of the bearing ring 110 or the flange 120 facing the drive shaft 130. On this side is also the recess 115. On the opposite side is at the same height the recess 117 of the drive shaft 130. In this embodiment, the two recesses 115 and 117 form a circular groove in the baffle plane between the bearing ring 110 and the drive shaft. In this groove can run, for example, a circular seal. The cross section of the groove is formed by the two recesses 115, 117 and is rectangular in the present case. It can also be seen in FIG. 2a that both the flange 120 and the drive shaft 130 have bores via which screwing can be carried out. For example, screws of type M 4 - 48 can be used here. In embodiments, the holes, for example, a diameter greater than or equal to 3 - 70mm, z. B. 10 mm, 20 mm or 30 mm. In the same way, a bearing disk or its segment can be connected to a drive shaft at least watertight.

The bearing ring 110 itself may have an outer diameter of, for example, 2200 mm in embodiments, wherein in the figure 2a, the outer radius 155 is shown to the axis of rotation 145 of the bearing. In general, the outer diameter (double outer radius 155) can also be greater than or equal to 40, 60, 100, 1000, 2000, 3000, 4000, 6000 or 10000 mm. In one embodiment, the inner diameter (twice the inner radius 150) of the bearing ring 110 is about 1800 mm. In exemplary embodiments, the inner diameter (double inner radius 150) of the bearing ring 110 can also be greater than or equal to 20, 30, 50, 500, 1000, 1500, 2000, 3000, 5000 or 10000 mm.

In one embodiment, the inner diameter of the bearing shell may comprise 2000 mm, which corresponds to twice the inner radius 160 of the bearing shell according to FIG. 2a. In other words, the bearing ring 110 may have a shell thickness of 200 mm. In exemplary embodiments, however, double Innenradii 160 of the bearing shell greater than or equal to 10, 20, 50, 80, 100, 1000, 2000, 3000, 4000, 6000 or 10000 mm are conceivable. The shell thickness of the bearing ring 110 may also be greater than or equal to 10, 30, 50, 100, 200, 300 or 400 mm in exemplary embodiments.

The bearing height 170, i. the axial extent of the bearing ring 110 may be, for example, 1000 mm. In embodiments, however, bearing heights 170 greater than or equal to 10, 20, 50, 100, 200, 300, 500, 1000, 2000, 3000 or 4000 mm are conceivable.

As already explained above, exemplary embodiments may also include a drive shaft 130 for an underwater power plant, which has fastening means or a fastening possibility for the flange 120 of a bearing component, a bearing ring 110 or the bearing ring itself and the coating 125 at at least one axial end, and a recess 117 for a seal. The drive shaft 130 may have axial and or radial bores. In other embodiments, the drive shaft 130 itself may in turn comprise a flange to be attached to the bearing ring 110 or its flange 120. The recess 117 can then also be located in the flange of the drive shaft 130. In embodiments, the drive shaft 130 may also have teeth as fastening means for the flange 120 or its segments. In further embodiments, the drive shaft 130 may also have holes and an additional toothing.

Exemplary embodiments also include an underwater power plant with a bearing component, a bearing ring segment 110, 110a, 110b, a bearing ring 110, 110a, 110b or a bearing 100 and a drive shaft 130 as described above. Alternatively, an embodiment of an underwater power plant may also comprise a bearing component, a bearing ring segment 110, a bearing ring 110 or a bearing 100 without a recess 115 and a drive shaft 130 without a recess 117, provided they are mechanically coupled to each other and there is a seal 119 between them for sealing.

The coating 125 in embodiments may comprise a different material than the bearing component, the bearing ring segment 110, 110a, 110b, the bearing ring 110, 110a, 110b or the drive shaft 130. In embodiments, the coating may be 125 Ni disgust, tungsten, cobalt, chromium, aluminum, diamond or a ceramic material. The coating 125 may generally have particles with a Mohs hardness greater than or equal to 9. In exemplary embodiments, the bearing component, the bearing ring segment 110, 110a, 110b, the bearing ring 110, 110a, 110b or the drive shaft 130 may comprise a metallic, a ceramic or a mixed material or a partially ceramic material. The coating 125 may be provided in embodiments on one side, ie either on the side of the bearing component, the bearing ring or on the side of the drive shaft, or on both sides.

The coating 125 serves to increase a frictional force and thus the adhesion to the component to be stored. The friction coating 125 can have as its main component a high-strength, tough and hard metal, wherein the coating 125 may be characterized in at least one surface area with a square-shaped base with a side length in the range of one millimeter, by a profile with many pointed mountains and valleys , In this surface area, a proportion of those peaks and valleys which project beyond a plane plane-parallel to the ground plane, which has a distance in the range between 15 and 30 μm from the highest mountain, can be greater than approximately 20%.

The topography of the friction coating 125, in particular when the coating is formed as a flame-sprayed molybdenum coating, can have a high surface carrying ratio, for example greater than 20%, and high static friction coefficients, for example greater than 0.6 or even greater than 0.65, based on a mating of said coating with a steel counterpart , or with the end face of the drive shaft, the wave washer or the shaft shoulder, have. The same applies in reverse configuration for a bearing ring when the shaft side is coated. In exemplary embodiments, the friction coating 125 may have particles with a Mohs hardness greater than or equal to 9 and / or a predeterminable average grain size. In embodiments, however, particles having a Mohs hardness greater than or equal to 6, 7 or 8 may also occur. Furthermore, the coating may have a thickness approximately equal to half the mean grain size. The coating carrier, ie the uncoated storage component, the uncoated bearing ring segment 110, 110a, 110b, the uncoated bearing ring 110, 110a, 110b or the uncoated drive shaft 130 may have a surface comprising recesses. A proportion of approximately 85% or more of the depressions may be formed with respect to a surface area surrounding the respective depression with a depth of less than approximately 10% and / or an opening width of less than or equal to approximately 15% of the coating thickness. The coating 125 may be applied to the surface of the coating carrier and enclose the particles at least in a lower region oriented towards the coating carrier. The surface of the coating carrier can therefore be designed such that the groove-like depressions have a surface area surrounding the respective depression, a depth of less than approximately 10% of the coating thickness and / or an opening width of less than approximately 15% of the coating thickness. This ensures optimum adhesion to the coating 125 and at the same time prevents particles from disappearing into depressions in such a way that they do not contribute to increasing the friction of the coating arrangement.

The friction coating 125 may comprise, for example, nickel, tungsten, cobalt, chromium, aluminum, diamond or a ceramic material. The coating 125 can be formed, for example, from electroplated nickel, so that at the same time a protective layer against corrosion-causing and other environmental influences is generated for the coating carrier.

In addition, the coating or the coatings may have hard particles, in particular particles with the degree of hardness of diamond or cubic boron nitrate (CBN) or of corundum or carbide. The coatings can be distinguished by the fact that they improve the detachable connection between the components as friction-increasing coatings. In exemplary embodiments, the coating may comprise zinc silicate or the particles may be formed, for example, by spray-galvanizing or the like, correspondingly with a friction-increasing coating. By virtue of the fact that the connection is galvanized, a reliable, friction-increasing coating can likewise be provided. In embodiments, hard particles such as diamond can be used as particles, wherein the particle size can be greater than 30 pm, preferably more than 35 pm. For example, a nickel-based coating 125 for diamond coating with a mean particle size of 46 pm (D46 diamond) can be produced.

In embodiments with one-sided coating 125, the material of the bearing component, the bearing ring segment 110, 110a, 110b, the bearing ring 110, 110a, 110b or the drive shaft 130 can be selected with a greater Mohs hardness and / or a greater tensile strength than the material of the drive shaft 130 or also a housing, so the component to be stored. Therefore, the regions of the particles projecting beyond the coating 125 can press into the component to be stored and thus increase the friction. The coating 125 below the particles as well as the areas of the coating carrier below the particles can only be slightly deformed compared with the impressions into the counterelement / component. In both sides coated embodiments, in particular, a hard coating with the o.g. Properties and a softer coating, which is just intended for receiving or pressing the particles are present.

In embodiments, as a friction coating 125 particles can be applied in one or a few layers, with a subsequent fixing of the particles by an electrodeposited metal, especially nickel, so that a particle layer is fixed, wherein when applying multiple layers, the excess layers, for example by a Brushes can be removed after fixing. For example, a coating 125 is conceivable in which the particle layer protruding from the nickel layer accounts for more than 25%, or up to 40%, of the surface of the coating, thus ultimately achieving very high static friction coefficients of greater than 0.7 and also greater than 0.8. Here, by a single layer is meant that in a majority of the coated surface, in particular greater than 75%, actually only one layer of particles is fixed, and only in smaller areas of the coated surface, the particles can also adhere in multiple layers, in particular two layers.

Examples of coating methods are thermoplastic polymer coating, nanocoating, plasma coating, carbide coating, PVD, CVD (chemical vapor deposition), TiC coating, TiCN, Ti, AlTiN, DLC (diamond-like carbon, dia- mond-like carbon), HVOF, etc. are conceivable.

FIG. 2b shows an overview of different sealing cross sections 201 to 215, as they may occur in exemplary embodiments. 2b shows a rectangular cross section with an inwardly curved side 201, a rectangular or square cross section 202, a bulbous or oval cross section 203, a trapezoidal cross section 204, a stem-shaped tapered cross sections 205, 206, a circular or annular cross section 207, a cross-shaped or star-shaped cross-section 208, a triangular cross-section 209, a funnel-shaped cross-section 210, a lip-like cross-section 211, a two-sided inwardly curved cross-section 212, a convex on two sides cross-section 213, cross sections with multiple sealing lips or extensions 214th , 215 etc. The variety of the cross-sectional variants shown already indicates that exemplary embodiments should not be restricted to specific geometries of seals. Any cross sections with arbitrary arrangements of sealing lips are conceivable. As a seal, for example O-rings, a sealing cord, adhesive sealants (eg cohesive compounds, adhesives, putties, elastomers, etc.), special seals, metal composite seals, fabric seals, inflatable seals, gaskets, gaskets, sleeve gaskets, etc. may be used. These seals can be made of different materials and of different shapes. The installation can be radial, axial or in combination radial and axial. FIG. 2c shows various components with the recesses 115, 117 and their combination with the friction layer 125 and the seal 119. FIG. 2c shows a section of a bearing ring 110 or a bearing ring segment 110, as has already been illustrated with reference to FIG , In this case, two recesses 115 are shown at the two end faces of the bearing rings or the flange, can be introduced into the corresponding seals for sealing. The figure 2c II) shows a section of a bearing ring 110 and a drive shaft 130, wherein in this constellation, the recess 117 is attached to the drive shaft 130. This embodiment illustrates how the bearing ring can be secured thereto by means of a flange overlapping the drive shaft. FIG. 2c III) illustrates an exemplary embodiment in which the recesses 115, 117 are provided at the edges of the end face of a drive shaft 130 and a bearing ring 110. In the figure 2c IV), an embodiment is shown in which the bearing ring 110 overlaps the drive shaft 130 and both bearing ring 110 and drive shaft 130 have at their end faces a friction coating 125. A recess 117 is provided in the form of a chamfer at the edge of the end face of the drive shaft 130, so that the seal 119 can be introduced into the corner region between the recess 117 and the bearing ring 110. FIG. 2 c V) illustrates an exemplary embodiment of a drive shaft 130 or a bearing ring 110 with a friction coating 125, which has a recess 115, 117 for a seal 119.

The figure 2c VI) shows a compound of a bearing ring 110 and a drive shaft 130, each having a friction coating 125, and with two opposite recesses 1 15, 117 form a gap for the seal 119 at their end faces. The figure 2c VII) illustrates once again the forces acting in an underwater scenario. The bearing ring 110 and the drive shaft 130 are screwed, so that act on these forces the screw each from the right and the left side. Between the two recesses 1 15, 1 16 so the seal 119 is jammed. From the outside, that is, in the figure from the direction from above water pressure or the force F _Wa ter to the seal 119 acts. In this embodiment, it is assumed that a gas filled hollow shaft 130, so that acts on the seal 119 from the inside of the gas pressure or the force F _gas . In other embodiments, the hollow shaft may also be under vacuum, ie have a negative pressure. In this case, the force F _gas would act in the opposite direction.

Figures 2c VIII) and 2C IX) each show an embodiment of an underwater power plant with a bearing ring segment 110 or a bearing ring and a drive shaft 130 which are mechanically coupled to each other and between which a seal 119 is to seal. Both components have a friction coating 125, but no recesses.

Claims

P a n t a n s p r e c h e

Bearing component, bearing, drive shaft and underwater power plant

A bearing component (110; 110a; 110b) for a bearing (100) of a water turbine, comprising a fastening possibility (120) for fastening the bearing component (110; 110a; 10b) to a component (130) to be supported, wherein the bearing component ( 110, 110a, 110b) has a recess (115) for a seal (119), such that the bearing component (110, 110a, 110b) can be connected to the component (130) to be supported at least in a water-tight manner.

The bearing component (110; 110a; 110b) according to claim 1, which is designed as a bearing segment (110; 110a; 110b), bearing disk segment, bearing ring segment (110; 110a; 110b), bearing ring (110; 110a; 110b) or bearing disk.

The bearing component (110, 110a, 110b) according to one of the preceding claims, which can be connected to the component (130) to be supported in a gas-tight or air-tight manner.

The bearing component (110; 110a; 110b) according to one of the preceding claims, comprising a coating (125) which increases a frictional force between the bearing component (110; 110a; 110b) and the component (130) to be supported and the recess (115 ) adjoins the coating (125).

The bearing component (110; 110a; 110b) according to one of the preceding claims, which has a flange (120) as an attachment at one axial end, the flange (120) having the recess (115) or the coating (125).

The bearing component (110; 110a; l 10b) according to any one of the preceding claims, adapted for supporting a drive shaft (130) of an underwater power plant, the recess (115) for the seal (119) being adapted to engage when attached a hollow shaft as the drive shaft (130) to seal the cavity of the drive shaft (130).

7. A bearing (100) with a bearing component (110; 110a; l 10b) according to one of the preceding claims.

8. A drive shaft (130) for an underwater power plant which has a recess (117) for a seal such that the drive shaft (130) is at least watertightly connectable to a bearing component (110; 110a; 110b) and / or the drive shaft ( 130) is designed as a hollow shaft.

The drive shaft (130) of claim 8 including a coating (125) which increases a frictional force between the drive shaft (130) and a bearing component to be attached thereto, the recess (117) being adjacent the coating (125).

10. An underwater power plant having a bearing component (110, 110a, 10b) and a drive shaft (130) according to one of the preceding claims, wherein the bearing component (110, 110a, 110b) or the bearing (100) with the drive shaft (130) at least is connected to a bearing component, a bearing ring segment (110, 110a, 110b), a bearing ring (110, 110a, 110b) or a bearing (100) and a drive shaft (130), which are mechanically coupled to each other and between which Seal a seal (119) is located.