Patent Application
20240011527
The invention relates to a slide bearing arrangement, and a nacelle equipped with the slide bearing arrangement for a wind turbine, and a wind turbine.
A bearing element for mounting the rotor hub of a wind turbine is known from WO 2011/127510 A1.
It was the object of the present invention to make available an improved slide bearing arrangement.
This object is achieved by means of a device in accordance with the claims.
In accordance with the invention, a slide bearing arrangement is configured. The slide bearing arrangement comprises:
In particular, it can be provided that the bearing surface is cambered outward. In other words, the bearing surface can be configured so as to be convex.
The slide bearing arrangement in accordance with the invention has the advantage that, due to the structure in accordance with the invention, it is configured both to receive axial forces and to receive radial forces.
It can further be provided that an apex of the bearing surface has the greatest radial distance of the bearing surface to an axis of rotation.
Further, it can be expedient if the individual slide bearing pads have the basic form of a spherical cap with a spherical cap radius in a spherical cap section and have a transition radius in a transition section.
In a first embodiment variant, it can be provided that the transition radius is smaller than the spherical cap radius. This results in the advantage that the spherical cap section can be configured to receive the radial forces and/or the axial forces acting in a first direction. The transition section can be configured to receive axial forces acting in a second direction. Here, the axial forces acting in the first direction can be greater than the axial forces acting in the second direction.
It can further be provided that the transition radius and the spherical cap radius have the same size.
Further, it can be provided that the spherical cap section extends up to an apex and the transition section adjoins the spherical cap section at the apex. A slide bearing thus configured has a surprisingly long lifetime.
Furthermore, it can be provided that the transition section transitions tangentially to the spherical cap section. Particularly a slide bearing thus configured has surprisingly good sliding properties.
Also advantageous is an embodiment, in accordance with which it can be provided that the apex is arranged at a distance from a second front end of the slide bearing pad, wherein the distance is between 1% and 49%, in particular between 5% and 35%, preferably between 10% and 25%, of an axial extension of the slide bearing pad. Particularly in a slide bearing arrangement thus designed, strong radial forces and/or strong axial forces can be absorbed in a first direction.
In accordance with one advancement, it is possible that a removal opening is configured in the outer ring element, which removal opening interrupts the mating surface of the outer ring element, starting from a first front end of the outer ring element. This results in the advantage that, due to this measure, the individual slide bearing pads are simple to change, without the complete slide bearing arrangement having to be dismantled into its parts to that end. In particular, it is conceivable that it is achieved with this measure that the individual slide bearing pads can be changed in the integrated state of the slide bearing arrangement without the slide bearing arrangement having to be completely dismantled. It can further be provided that the removal opening extends from a first front end of the outer ring element at least up to the apex of the slide bearing element.
Further, it is conceivable that, in the operating mode of the slide bearing, a porous material, such as a sponge, for example, is arranged in the removal opening, which porous material serves to temporarily receive lubricating oil. With this measure, it can be achieved that the sliding surface of the individual slide bearing pads is evenly covered with a lubricating oil film.
In one advancement, it can be provided that a sensor system is arranged in the removal opening, which sensor system serves to acquire operating modes and/or wear states of the slide bearing. Such a sensor system may be, for example, a temperature sensor, an oscillation sensor or suchlike.
The individual slide bearing pads are simple to remove from their operating position through the removal opening.
Further, it may be expedient if the removal opening has a circumferential extension and that the slide bearing pads each have a circumferential extension, wherein the circumferential extension of the slide bearing pads is between 60% and 99.9%, in particular between 80% and 99%, preferably between 90% and 98%, of the circumferential extension of the removal opening. Particularly with such a size ratio, the removal opening has a sufficient circumferential extension to enable the individual slide bearing pads to be taken out of the slide bearing arrangement in a simple manner through the removal opening. At the same time, the removal opening is sufficiently small so as not to cause a weakening of the outer ring element and/or a reduction of the load-bearing capacity of the slide bearing arrangement.
Furthermore, it can be provided that the removal opening is configured so as to widen radially towards the first front end. This results in the advantage that the outer ring element can have a stability that is as high as possible and, at the same time, the slide bearing pad is as simple as possible to remove through the removal opening.
Further, it can be provided that a slide bearing pad reception ring is configured, which serves to affix the slide bearing pads, wherein the slide bearing pad reception ring is received on the inner ring element. This results in the advantage that, through this measure, the slide bearing pads can be firmly coupled with the inner ring element.
Furthermore, it can be provided that the slide bearing pad reception ring is shrunk onto the inner ring element. Particularly for rotor shafts, this is a highly sustainable and feasible bond. In the shrinking-on process, the slide bearing pad reception ring is heated and/or the inner ring element is cooled down in order to facilitate an axial forcing-on. After the temperature equalization, and therefore the equalization of the respective thermal expansions, a tight fit of the slide bearing pad reception ring on the inner ring element can be achieved.
In an alternative embodiment variant, or additionally, it can be provided that the slide bearing pad reception ring is coupled with the inner ring element by means of a material bond, such as a welded bond, for example.
In yet another embodiment variant, it can be provided that the slide bearing pad reception ring is coupled with the inner ring element by means of an interlocking bond, such as a screwed bond, for example. In particular, it can be provided that the
It can further be provided that multiple tapped holes are configured in the slide bearing pad reception ring, which tapped holes are arranged in an axial direction of the slide bearing pad reception ring and serve to receive fastening screws, wherein pass-through holes are configured in the slide bearing pads, through which pass-through holes the fastening screws are plugged in order to clamp the slide bearing pads on the slide bearing pad reception ring by means of the fastening screws. Such a bond between the slide bearing pads and the slide bearing pad reception ring is simple to produce.
In one advancement, it can be provided that the slide bearing pads have a shoulder on their inner face, which shoulder rests against a front end of the slide bearing pad reception ring, wherein the pass-through holes are arranged in the region of the shoulder. With this measure, a sufficiently load-bearing connection between the slide bearing pad and the inner ring is achieved.
It can further be provided that a shaft nut is configured, which has an axial securing element reception, wherein at least one axial securing element per slide bearing pad is received in the axial securing element reception, which axial securing element serves to fix the slide bearing pad axially. This results in the advantage that the individual slide bearing pads can be fixed in their position by means of the axial securing elements. Furthermore, the shaft nut is simple to adjust in its axial position and can provide sufficient support for the individual axial securing elements.
In an alternative embodiment variant, it can also be provided that, instead of the shaft nut, a shaft ring, which can be forced on, for example, can serve to receive the axial securing elements.
In yet another embodiment variant, instead of the shaft nut, the rotor shaft itself can serve to receive the axial securing elements and have a corresponding shape.
In accordance with one particular embodiment, it is possible that the axial securing element is coupled with the shaft nut by means of a fastening screw acting in a radial direction, wherein the axial securing element, on at least one axial front end, has a wedge surface that tapers off towards the axis of rotation, which wedge surface corresponds with a first mating wedge surface, which is arranged on a first front end of the slide bearing pad. This measure ensures that the axial securing element can exert an axial pressure on the slide bearing pad by tightening the fastening screw, whereby the slide bearing pad can be clamped by means of the axial securing element.
It can further be provided that the wedge surface of the axial securing element, which wedge surface tapers off towards the axis of rotation, corresponds with a first mating wedge surface configured on the first front end of the slide bearing element. This measure enables the slide bearing pad not only to be clamped axially but also to be clamped radially. Furthermore, the tapering-off shape of the wedge surface and the corresponding mating shape of the first mating wedge surface enable an interlocking bond between the axial securing element and the slide bearing pad to be achieved. In particular, it can be provided that the first mating wedge surface is configured such that the slide bearing pad has a wide base on its inner face and tapers off outwardly in the region of the first mating wedge surface.
In accordance with one advantageous advancement, it can be provided that the shaft nut has a rotation surface for a shaft sealing ring on its outer face. This results in the advantage that the shaft nut can simultaneously serve as mating component for the shaft sealing ring. Furthermore, the surface properties of the rotation surface required for a shaft sealing ring, for example a surface that is ground twist-free, are simpler to produce on the shaft nut than on a rotor shaft, for example. This enables the structure of the slide bearing arrangement to be simplified and the lifetime of the slide bearing arrangement to be improved.
In particular, it can be advantageous if a bearing block is configured, in which the outer ring element is received, wherein a cover is configured at least at an axial front end of the bearing block, wherein a lubricating oil reservoir is configured so as to be integrated in the cover or adjoined to the cover. This has the advantage that, in a lubricating oil reservoir thus configured, a sufficient quantity of lubricating oil for a hydrodynamic slide bearing can be stocked up.
Further, it can be provided that an axial stop ring is configured. It can further be provided that at least one antitwist protection element is configured, which acts between the axial stop ring and at least one of the slide bearing pads. With this measure, it can be achieved that at least one of the slide bearing pads is secured against twisting relative to a shaft.
It can further be provided that the axial stop ring has a wedge surface, which is configured such that an interlocking bond between the slide bearing pad and the axial stop ring can be achieved. In particular, it can be provided that a second mating wedge surface is configured on the second front end of the slide bearing pad. In particular, it can be provided that the second mating wedge surface is configured such that the slide bearing pad has a wide base on its inner face and tapers off outwardly in the region of the second mating wedge surface.
Due to the first mating wedge surface and the second mating wedge surface, in case of an axial clamping of the slide bearing pad, an additional radial clamping of the slide bearing pad and/or a radial pressing of the slide bearing pad against the rotor shaft can be achieved by bringing wedge surfaces in contact with the mating wedge surfaces. This can in particular be achieved by means of the interlocking bond of the wedge surfaces with the respective mating wedge surfaces.
It can further be provided that a separate antitwist protection element is configured for each of the slide bearing pads.
It can further be provided that the axial stop ring is shrunk onto the shaft.
Furthermore, it can be provided that the axial stop ring has a rotation surface for a shaft sealing ring on its outer face. This results in the advantage that the shaft nut can simultaneously serve as mating component for the shaft sealing ring. Furthermore, the surface properties of the rotation surface required for a shaft sealing ring, for example a surface that is ground twist-free, are simpler to produce on the axial stop ring than on a rotor shaft, for example. This enables the structure of the slide bearing arrangement to be simplified and the lifetime of the slide bearing arrangement to be improved.
Also advantageous is an embodiment, in accordance with which it can be provided that the removal opening, in a circumferential direction, has an oil feed, in particular a rounding or a chamfer, which is larger than 5 mm, preferably larger than 10 mm, in particular larger than 20 mm. This results in the advantage that lubricating oil that adheres to the slide bearing pad, in particular to the bearing surface, is not scraped off by the removal opening but remains on the bearing surface.
It can further be provided that a form element, in particular a thread, is configured on the first front end of the slide bearing pad, which form element serves to receive a connection element. This results in the advantage that the slide bearing pad can thus be coupled with a slide bearing pad changing device in a simplified manner.
It can further be provided that a thrust ring segment is arranged on a second front end of the slide bearing pad. This results in the advantage that the spherical cap section can be configured to receive the radial forces and/or the axial forces acting in a first direction. The thrust ring segment can be configured to receive axial forces acting in a second direction. Here, the axial forces acting in the first direction can be greater than the axial forces acting in the second direction. In particular, it can be provided that the thrust ring segment has a sliding surface, which interacts with a corresponding mating sliding surface of the outer ring element.
In a first embodiment variant, it can be provided that the thrust ring segment is coupled with the slide bearing pad by means of fastening means, in particular by means of screws. In particular, it can be provided that the thrust ring segment is coupled with the slide bearing pad by means of at least two fastening means, preferably by means of three fastening means, in particular by means of Allen screws. Here, the fastening means can be divided up at an identical angular distance.
In another embodiment variant, it can be provided that the thrust ring segment is configured so as to be integrally formed, or formed as one piece, with the slide bearing pad.
It can further be provided that, spacers are arranged between the individual slide bearing pads, viewed in a circumferential direction. This results in the advantage that the slide bearing pads can be retained in position.
In one advancement, it can be provided that the spacers are configured so as to be arranged directly on the slide bearing pads. In an alternative embodiment variant, it can be provided that the spacers are configured as independent components, which are arranged between the slide bearing pads.
Furthermore, it can be provided that a lubricating oil transport groove is configured in the region of the bearing surface on a first circumferential face of the slide bearing pad. Such a lubricating oil transport groove has the advantage that the lubricating oil can be conveyed upwards from the lubricating oil reservoir by means of the lubricating oil transport groove and can therefore be distributed across the mating surface of the outer ring element.
Further, it can be provided that a reception for a lifting device is configured in the slide bearing pad, on its inner face. This can facilitate the initial assembly of the slide bearing pads.
In accordance with the invention, a method for changing a slide bearing pad of a slide bearing arrangement is provided. The method comprises the method steps:
The method in accordance with the invention results in the advantage that the individual slide bearing pads can be changed even in the assembled state of the slide bearing arrangement. This enables the maintenance process to be simplified substantially.
In accordance with the invention, a nacelle for a wind turbine is provided. The nacelle comprises:
Particularly in nacelles of wind turbines, the slide bearing in accordance with the invention is of advantage due to its ease of maintenance.
In accordance with one particular embodiment, it is possible that the rotor bearing arrangement comprises a bearing block, in which the outer ring element is received, wherein the bearing block has an axial stop for the outer ring element, wherein the axial stop is configured at an axial front end of the bearing block facing away from the rotor hub. This has the advantage that the axial stop acts in a main load direction of the rotor bearing arrangement.
In accordance with one advantageous advancement, it can be provided that a removal opening is configured in the outer ring element, which removal opening extends from a first front end of the outer ring element at least up to the apex of the slide bearing element, wherein the removal opening is configured on the end of the bearing block facing away from the rotor hub. This results in the advantage that the individual slide bearing pads can be removed in a simple manner in the assembled state of the nacelle in order to change the individual slide bearing pads.
In particular, it can be advantageous if the axial stop has a recess in the region of the removal opening of the outer ring element, which recess corresponds with the removal opening. This results in the advantage that the individual slide bearing pads can be fitted and/or removed in a simple manner.
In an alternative embodiment variant, it can be provided that the outer ring element is configured so as to be formed as one piece, or integrally, with the bearing block. In other words, it can be provided that the bearing block can simultaneously serve as outer ring element. All features which are described for the outer ring element, such as the removal opening, for example, can therefore also be configured directly in the bearing block.
The bearing block can have a bearing block base and a bearing block cover. This results in the advantage that the bearing block cover is simple to remove, whereby a simplified removal of the slide bearing pads in case of maintenance can be achieved. In particular, this measure enables the slide bearing pads to be removed radially from the inner ring element. Furthermore, this measure enables the individual slide bearing pads to be arranged on the inner ring element in a simplified manner upon assembly of the slide bearing arrangement by lifting the individual slide bearing pads radially through the opening of the bearing block cover in the space between the inner ring element and the outer ring element. In particular, it can be provided that, during operation of the slide bearing arrangement, the outer ring element is stationary and that the slide bearing pads are affixed to the inner ring element and are rotated together with the inner ring element.
Further, it can be provided that the bearing surface interacts with the outer ring element, wherein a mating surface of the bearing surface is configured in the outer ring element. This results in the advantage that the sliding surface and/or also the mating surface can be manufactured in a simple manner.
It can further be provided that an antitwist protection is configured on at least one of the slide bearing pads, by means of which antitwist protection this slide bearing pad is secured against twisting relative to the inner ring. Such an antitwist protection can be, for example, an elevation, a depression or also another element acting in an interlocking manner between the slide bearing pad and the inner ring element, such as a pulling pin, for example.
In accordance with one advancement, it is possible that at least individual of the slide bearing pads are coupled with one another by means of a connection element. This results in the advantage that the individual slide bearing pads can be fixed relative to one another. Therefore, the position of the individual slide bearing pads can be fixed.
Further, it can be provided that the outer ring element has a recess and/or a reinforcement, which serves to change a position of a shear center of the outer ring element. This results in the advantage that the deforming of the outer ring element, which is caused by the force acting on the slide bearing arrangement, can be influenced. Therefore, this measure enables the surface pressure, which is caused by the stress, to be reduced and/or displaced.
Furthermore, it can be provided that the mating surface of the outer ring element and/or the bearing surfaces of the slide bearing pads have a shape diverging from an ideal spherical cap by between 0.001 mm and 10 mm, in particular between 0.5 mm and 5 mm, preferably between 0.5 mm and 1 mm, which shape is configured such that stress-related deformations of the inner ring element and/or of the outer ring element and/or of the slide bearing pad are equalized and, in the load-bearing state, the bearing surfaces of the slide bearing pads rest flatly against the mating surface of the outer ring element. This results in the advantage that, through this measure, a stress-related deforming of individual components of the slide bearing arrangement can be anticipated, so that the bearing surface and the mating surface rest against each other as flatly as possible during operation in order to avoid the surface pressure.
In an alternative embodiment variant, it can be provided that the inner ring element is configured so as to be formed as one piece, or integrally, with the rotor shaft. In other words, it can be provided that the rotor shaft can simultaneously serve as inner ring element. All features which are described for the inner ring element can therefore also be configured directly in the rotor shaft.
Also advantageous is an embodiment, in accordance with which it can be provided that that the slide bearing arrangement is configured as a hydrodynamic slide bearing arrangement. Particularly a hydrodynamic slide bearing arrangement has a low frictional resistance and therefore a high efficiency.
The apex in accordance with this document is the point that has the largest diameter of the bearing surface, viewed in the longitudinal section of the slide bearing pad. This point is guided around the axis of rotation with rotational symmetry and therefore forms an envelope and/or envelope line, viewed over the entire slide bearing pad.
Further, it is conceivable that a slide coating is arranged on one of the surfaces of the rotor shaft and/or of the bearing block and/or of the outer ring element and/or of the slide bearing pads. The slide coating can be produced by means of an additive manufacturing method. In particular, it is conceivable that the slide bearing coating is produced by one of the following methods: metal wire transfer, electron-beam welding, friction welding, laser deposition welding, 3D metal print, direct energy deposition, binder jetting, material jetting, cold gas spraying, selective laser melting, material extrusion, direct metal laser sintering, direct metal laser melting, cold metal transfer, metal inert gas (MIG) welding, tungsten inert gas (TIG) welding, vat photopolymerization.
Further, it is conceivable that the slide coating is produced by means of a thermal spraying method, such as, for example: plasma spraying; flame spraying; wire flame spraying; electric arc spraying; atmospheric plasma spraying and high velocity oxygen fuel spraying.
Further, it is conceivable that the slide coating is produced by means of any one of the following methods: detonation spraying; laser spraying; galvanic coating; powder coating; electromagnetic pulse welding, electron beam physical vapor deposition.
Possible materials for a slide coating are: bronze alloys; aluminum-tin alloys; white metal; metal-matrix composites with dry lubricants, and also combinations thereof.
For the purpose of better understanding of the invention, it will be elucidated in more detail by means of the figures below.
These show in a respectively very simplified schematic representation:
First of all, it is to be noted that, in the different embodiments described, equal parts are provided with equal reference numbers and/or equal component designations, where the disclosures filled into in the entire description may be analogously transferred to equal parts with equal reference numbers and/or equal component designations. Moreover, the specifications of location, such as at the top, at the bottom, at the side, chosen in the description refer to the directly described and depicted figure, and in case of a change of position, these specifications of location are to be analogously transferred to the new position.
Further, a rotor 5 is configured, which has a rotor hub 6 with rotor blades 7 arranged thereupon. The rotor hub 6 is considered part of the nacelle 2. The rotor hub 6 is received on the nacelle housing 4 by means of a rotor bearing arrangement 8 so as to be rotatably movable. In particular, it is provided that a slide bearing arrangement 9 in accordance with the invention, which slide bearing arrangement 9 will be described in more detail below, is used as rotor bearing arrangement 8. In particular, it can be provided that the rotor hub 6 is arranged on a rotor shaft 16, wherein the rotor shaft 16 is mounted in the rotor bearing arrangement 8.
The rotor bearing arrangement 8, which serves to mount the rotor hub 6 on the nacelle housing 4 of the nacelle 2, is configured for receiving a radial force 10 and an axial force 11. The axial force 11 is a result of the force of the wind. The radial force 10 is a result of the weight of the rotor 5 and acts on the center of gravity of the rotor 5. As the center of gravity of the rotor 5 lies outside of the rotor bearing arrangement 8, a tilting moment 12 is caused in the rotor bearing arrangement 8 by the radial force 10. The tilting moment 12 can equally be caused by an uneven load on the rotor blades 7. This tilting moment 12 can be absorbed by means of a second bearing arrangement, which is arranged at a distance to the rotor bearing arrangement 8. The second bearing arrangement can be configured in the region of the generator, for example.
Subsequently, the slide bearing arrangement 9 is described by means of a combination of
As can be seen from
In the exemplary embodiment which is represented in
As can be seen particularly readily from
Further, it can be provided that the bearing block 17 serves directly as outer ring element 14.
Therefore, the rotor shaft 16 is received in the nacelle housing 4, by means of the slide bearing arrangement 9, so as to be rotatable.
As can further be seen from
Due to the structure shown in
The bearing surface 20 of the slide bearing pad 18 and the mating surface 21 of the outer ring element 14 are configured as sliding surfaces, which slide against each other during operation of the slide bearing arrangement 9. In particular, it can be provided that the mating surface 21 of the outer ring element 14 is configured as a hard, wear-resistant surface, which can be formed by a hardened steel, for example. The bearing surface 20 of the slide bearing pad 18 can be formed from a slide bearing raw material that is soft in comparison to the mating surface 21. Of course, it is also conceivable that the bearing surface 20 has a slide coating.
As can be seen particularly readily from
As can further be seen from
Starting from the apex 25, the bearing surface 20 can have a diameter decrease towards a second front end 27 of the slide bearing pad 18. In the region of the second front end 27, the bearing surface 20 can have a second diameter 28.
In particular, it can be provided that a spherical cap section 29 is configured between the first front end 23 and the apex 25. The spherical cap section 29 can have the basic form of a spherical cap with a spherical cap radius 30.
Between the second front end 27 and the apex 25, a transition section 31 can be configured. The transition section 31 can have a transition radius 32. In particular, it can be provided that the transition radius 32 is smaller than the spherical cap radius 30.
It can further be provided that the apex 25 is arranged at a distance 33 from a second front end 27 of the slide bearing pad 18. The slide bearing pad 18 can have an axial extension 34.
As can further be seen from
As can further be seen from
As can further be seen from
In
As can be seen from
In
As can be seen from
As can further be seen from
As can be seen particularly readily from a combination of
In another exemplary embodiment, which is not represented, it can also be provided, of course, that the removal opening 41 completely penetrates the outer ring element 14 radially.
As can be seen from a combination of
As can be seen particularly readily from
It can further be provided that the axial securing elements 51 have a wedge surface 54 on an axial front end 53. On the first front end 23 of the slide bearing pad 18, a first mating wedge surface 55 can be configured. In particular, it can be provided that the wedge surface 54 interacts with and/or rests against the first mating wedge surface 55.
As can further be seen from
In particular, the individual slide bearing pads 18 can be clamped between the axial stop ring 56 and the axial securing element 51 and/or between multiple axial securing elements 51.
As can be seen from
As can be seen from
As can be seen from
As can further be seen from
In the assembled state of the slide bearing arrangement 9, the outer ring element 14 is received in the bearing block 17. Here, it can be provided that the outer ring element 14 is clamped axially between the second cover 61 and the axial stop 62 in the bearing block 17. Here, it can be provided that the second cover 61 is screwed axially against the bearing block by means of fastening means.
The axial stop ring 56 can be affixed to the rotor shaft 16. Further, the shaft nut 49 can be screwed onto the rotor shaft 16. As can be seen from
To change the individual slide bearing pads 18, the cover 36 can be removed from the bearing block 17. Alternatively, it is also conceivable that a maintenance opening is configured in the cover 36, which maintenance opening can be uncoupled from the cover 36, whereby the interior of the bearing block 17 is accessible.
In another alternative, it is also conceivable that the cover 36 is configured so as to be divided, so that it can be removed radially from the rotor shaft 16 and need not be displaced along the rotor shaft 16 in an axial direction. Here, the cover 36 can be configured so as to be divided in a center plane, for example.
When the interior components of the bearing block 17 are accessible in accordance with the representation according to
Subsequently, the inside of the bearing block 17 can be closed up again by means of the cover 36 and thus the slide bearing arrangement 9 can be made operational again.
As can be seen from
Independent of the other features and as can further be seen from
As can be seen from
As can be seen from
As can further be seen from
In the exemplary embodiment according to
Between the second front end 27 and the apex 25, a transition section 31 can be configured. The transition section 31 can have a transition radius 32. In the exemplary embodiment according to
In addition to the transition section 31, a thrust ring segment 68 can be arranged on the second front end 27 of the slide bearing pad 18, which thrust ring segment 68 can serve to receive axial forces.
As can be seen from
As can be seen from
As can be seen from a combination of the
Further, it can be provided that a seal is arranged on both sides of the lubricating oil distribution groove 77, which seal serves to seal the lubricating oil distribution groove 77 between the outer ring element 14 and the bearing block 17.
As can be seen particularly readily from
It can further be provided that the filler element 80 can be coupled with the outer ring element 14 by means of an interlocking bond 81, in particular by means of a connecting groove. It can further be provided that the filler element 80 is secured in its position by means of a securing element, which is not represented.
As can be seen from
Also the spacers 73 can readily be seen in
As can be seen particularly readily from
As can be seen from
Further, it can be provided that a recess 82 is configured in the region of the form element 69, which recess 82, in interaction with the form element 69, serves to couple the slide bearing pad 18 with the slide bearing pad changing device.
For the sake of simplicity, only a single slide bearing pad 18 is represented in
As can be seen from
In particular, it can be provided that the individual slide bearing pads 18 have a shoulder 114 on their inner face 72. The shoulder 114 can form a contact surface, so that the slide bearing pad 18 can rest against a first front end 115 of the slide bearing pad reception ring 110 in the region of the shoulder 114. This ensures that the slide bearing pad 18 can be positioned relative to the slide bearing pad reception ring 110 in an axial direction.
It can further be provided that the shoulder 114 bounds a recess 116, which is configured on the inner face 72 of the slide bearing pad 18. The recess 116 can extend up to the shoulder 114 starting from the second front end 27 of the slide bearing pad 18. The recess 116 and/or the shoulder 114 can be configured so as to be rotationally symmetric.
In particular, it can be provided that, in the integrated state of the slide bearing pad 18, the slide bearing pad reception ring 110 is at least partially received in the recess 116 of the slide bearing pad 18.
It can further be provided that multiple tapped holes 111 are configured on the first front end 115 of the slide bearing pad reception ring 110. Corresponding with the tapped holes 111, one, in particular multiple, pass-through holes 112 can be configured in each of the slide bearing pads 18.
Further, fastening screws 113 can be guided through the pass-through holes 112, which fastening screws 113 can be screwed into the tapped holes 111 and can therefore serve to affix the slide bearing pads 18 to the slide bearing pad reception ring 110.
As can further be seen from
The exemplary embodiments show possible embodiment variants, wherein it should be noted in this respect that the invention is not restricted to these particular illustrated embodiment variants of it, but that rather also various combinations of the individual embodiment variants are possible and that this possibility of variation owing to the teaching for technical action provided by the present invention lies within the ability of the person skilled in the art in this technical field.
The scope of protection is determined by the claims. However, the description and the drawings are to be adduced for construing the claims. Individual features or feature combinations from the different exemplary embodiments shown and described may represent independent inventive solutions. The object underlying the independent inventive solutions may be gathered from the description.
Any and all specifications of value ranges in the description at issue are to be understood to comprise any and all sub-ranges of same, for example the specification 1 to 10 is to be understood to mean that any and all sub-ranges starting from the lower limit 1 and from the upper limit 10 are comprised therein, i.e. any and all sub-ranges start at a lower limit of 1 or larger and end at on upper limit of 10 or less, e.g. 1 to 1.7, or 3.2 to 8.1, or 5.5 to 10.
Finally, as a matter of form, it should be noted that for ease of understanding of the structure, elements are partially not depicted to scale and/or are enlarged and/or are reduced in size.
| Number | Date | Country | Kind |
|---|---|---|---|
| A51044/2020 | Nov 2020 | AT | national |
| A50259/2021 | Apr 2021 | AT | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/AT2021/060451 | 11/29/2021 | WO |
