AT522730A1 - Bearing cap - Google Patents

Abstract

Bearing cover (3) for a split bearing arrangement (1) which, in addition to the bearing cover (3), comprises a bearing block (2), the bearing cover (3) having a bearing cover body (6) which has a radial sliding bearing surface (4) and at least one axial sliding bearing surface (14 , 15), the bearing cover body (6) being formed from a metallic sintered material. The axial sliding bearing surface (14, 15) is designed as a coating on the bearing cover body (6). A transition between the axial sliding bearing surface (14, 15) and the bearing cover body (6) is rounded. In the bearing cap body (6) there are screw bolt receptacles (10) for receiving screw bolts for connecting the bearing cap (3) to the bearing block (2), the screw bolt receptacles (10) having a longitudinal extension and being limited by boundary surfaces. Centering elements (24) for centering the bearing cover (3) when mounting the bearing cover (3) on the bearing block (2) are arranged within the screw bolt receptacles (10) and extend over at least part of the longitudinal extension of the screw bolt receptacles (10).

Description

Bearing cap body is executed.

The invention further relates to a bearing arrangement with a bearing cap and a

a bearing chair attached to it.

Split bearing arrangements with a bearing block and a bearing cover are known from the prior art, for example for mounting a crankshaft. The bearing cover is screwed to the bearing bracket using screw bolts,

as described, for example, in EP 1 075 605 B1.

Often sliding bearing shells are used in the split bearing arrangement. In addition, there are also axial plain bearings to support the shaft in the axial direction.

tion.

DE 10 2016 005 472 A1 also discloses a bearing element for mounting a crankshaft on a crankcase of a reciprocating piston engine, in which an attempt was made to reduce the number of parts in the divided bearing arrangement. The bearing element has at least one bearing opening for at least partially receiving a shaft journal of the crankshaft. At least one side of a base body of the bearing element that at least partially delimits the bearing opening is at least partially provided with a sliding layer on which

the crankshaft can be supported in its axial direction.

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To create slide bearing improved split bearing assembly.

This object is achieved in that the bearing cover body is made of a metal

Lischen sintered material is formed.

Furthermore, the object of the invention is achieved with the initially mentioned split bearing arrangement in which the bearing cover is designed according to the invention

is.

The advantage here is that by designing the bearing cap body as a sintered material, the adhesion of the coating for the axial sliding bearing surface on the bearing cap body can be achieved through the porosity of the bearing cap body (the pores

serve as adhesive bridges) can be improved.

According to a preferred embodiment of the bearing cover, it can be provided that the axial sliding bearing surface has a convex shape, the greatest radial height of the axial sliding bearing surface being formed in the area of half the angle cover. An improvement can thus be achieved with regard to the avoidance of so-called edge supports, which subsequently also

if an improvement in the plain bearing is achieved.

According to another embodiment of the bearing cover, it can be provided that the axial sliding bearing surface is formed on a thickening of the bearing cover body in the axial direction. A better distribution of the stress introduced into the material of the bearing cap when it is clamped together with the bearing block can thus be achieved, especially in conjunction with the convex shape of the axial sliding bearing surface, which also enables the stresses that occur in the bearing cap to be reduced after clamping with the bearing block . As a result of this reduction, lower stresses are introduced into the bearing surfaces, which means that the loading

stratification can be achieved.

To further improve the adhesion of the axial plain bearing coating, according to

a further embodiment of the bearing cover can be provided that the

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can be achieved by lubricant in the plain bearing surface.

Likewise, to improve the lubricating effect, it can be provided that the radial plain bearing surface and / or the axial plain bearing surface are directly

layering of the bearing cap body is formed with a plain bearing material / are.

According to one embodiment variant, a sliding lacquer is preferably applied as the sliding bearing material because, in addition to being easy to apply, this also has good adaptability to the counter bearing surfaces of the sliding bearing, which means

the running-in time of the plain bearing can be shortened.

A further improvement of the sliding bearing can be achieved with a variant of the bearing cover in which a groove-shaped recess is arranged in the axial sliding bearing surface. Via this recess, it is possible to supply lubricant to the bearing surfaces, with which they can be better lubricated

or overheating can be better avoided.

A further reduction in edge supports can be achieved with a variant of the bearing cover in which a transition between the axial slide bearing

gerfläche and the bearing cover body is provided with a curve.

According to another embodiment of the bearing cap, it can be provided that screw bolt receptacles for receiving screw bolts for connecting the bearing cap to the bearing block are arranged in the bearing cap base body, the screw bolt receptacles having a longitudinal extension and being delimited by boundary surfaces, and the bearing cap with centering elements for centering the bearing cap the assembly of the bearing cover on the bearing block, which are arranged within the screw bolt receptacles, and extend over at least a portion of their longitudinal distribution

cover extend. The advantage here is that by avoiding from the

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negative influence on the bearing surfaces exerted by the clamping.

For a more precise centering of the bearing cap on the bearing block, it is possible according to a variant of the bearing cap that at least three centering elements are arranged in one of the two screw bolt receptacles and at least two centering elements are disposed in the other of the two screw bolt receptacles. This also avoids interchanging the axial sliding bearing surfaces when reassembling the split bearing arrangement, so that the axial sliding bearing surfaces that have already been run in can be reassembled with the correct sliding partner.

work together.

According to a further embodiment of the bearing cover, it can be provided that the centering elements are at least approximately strip-shaped. The screwing in of the screw bolts can thus be simplified. As the screw bolts are more easily screwed in, the precise repositioning of the bearing cover on the bearing block can be improved, which reduces the risk of a (slightly) incorrectly oriented axial sliding bearing surface

can.

For the same reason, it can be provided according to another embodiment of the bearing cover that the centering elements have an at least approximately trapezoidal cross section. A geometry of the centering elements that tapers in the direction of the screw bolts can thus be achieved.

the.

For an improved assembly through easier centering when assembling

The construction of the bearing cover and bearing bracket can be made according to a variant

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be effective.

To simplify the centering, it can also be provided according to a further embodiment variant that at least one of the centering elements is formed in at least one of the two screw bolt receptacles over the course of its longitudinal extension with increasing height. It is thus given

If necessary, a multi-stage centering can be realized.

For a better understanding of the invention, it will be based on the following

Figures explained in more detail.

In each case, in a simplified, schematic representation: FIG. 1 shows a cross section through a divided bearing arrangement; 2 shows a bearing cover in an oblique view;

FIG. 3 shows the bearing cover according to FIG. 2 in side view; FIG.

FIG. 4 shows the bearing cover according to FIG. 2 in plan view; FIG.

Fig. 5 the screw bolt receptacle of an embodiment of the bearing de-

ckels in cross section; 6 shows a detail from a screw bolt receptacle;

7 shows a section from a screw bolt receptacle of an embodiment

variant of the bearing cover;

8 shows a detail from a screw bolt receptacle of an embodiment

variant of the bearing cover.

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in the event of a change in position, information must be transferred to the new position accordingly.

Information in this description of standards relates to the version of these standards valid on the filing date of the relevant application, unless otherwise

something else is expressly stated.

Fig. 1 shows a split bearing arrangement 1, as it is used, for example, in a machine housing of a reciprocating piston engine. This bearing arrangement 1 comprises a bearing block 2 and a bearing cover 3, which together provide a first and a second radial sliding bearing surface 4, 5, for example for mounting a crankshaft. According to a preferred embodiment of the invention, the radial sliding bearing surfaces 4, 5 are produced by direct coating of a bearing cap body 6 or the bearing bracket in the area of the radial sliding bearing surfaces 4, 5 with a sliding bearing material. With regard to the plain bearing material, reference is made to the following statements. However, the use of plain bearing half-shells or plain bearing bushings is also possible, although this is not preferred

is.

The radial sliding bearing surfaces 4, 5 are therefore preferably formed by coating the radially inner surfaces of the bearing block 2 and the bearing cover 3. The latter surround an opening through the bearing arrangement 1 for receiving

of the component to be stored.

The bearing cover 3 has a clamping surface 7 at each of its two distal end regions and the bearing block 2 has a respective clamping surface at its two end regions

Clamping surfaces 7 opposite counter-clamping surfaces 8, which together

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but as a blind hole with an internal thread.

The projections 9 can, for example, be approximately bone-shaped or strip-shaped, with a longitudinal extension in the direction from a front side 11 to a rear side 12 of the bearing cap 3 (i.e. in an axial direction 13) as can be seen from FIG. 2, which is an oblique view of the bearing cap 3 shows.

The projections 9 can also be designed differently.

The projections 9 can be formed in one piece with the rest of the bearing cap 3

be.

If present, at least the projections 9 are made of a material that is harder than the material of the bearing block 2 in the area of the counter-clamping surface 8, so that these projections 9 can be pressed into the counter-clamping surface 8 by compressing and tensioning the bearing block 2 and bearing cover 3. However, the entire bearing cover 3 is preferably made from this harder material. For example, the bearing cover 3 can be made of a ferrous material and the bearing bracket 2 can be made of a light metal. In particular, the bearing cover 3 is made from a sintered iron material. However, it is

The reverse execution of the bearing arrangement 1 with regard to the hardnesses is also possible.

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Metallic powders known in the art can be used.

The first radially inner radial sliding bearing surface 4 of the bearing cover 3 and the second radially inner radial sliding bearing surface 5 of the bearing block 2 are arranged between the clamping surfaces 7 of the bearing cover 3 and the counter-clamping surfaces 8 of the bearing block 2, respectively. They are each marked with a circular when viewed in the axial direction 13

arcuate, in particular semicircular, cross-section.

As can be seen better from FIGS. 2 and 3, an axial sliding bearing surface 14 is formed between the two screw bolt receptacles 10 of the bearing cover 3 on the front side 11 of the bearing cover body 6. According to a further embodiment of the bearing cap 3, an axial sliding bearing surface 15 can additionally or alternatively also be formed on the rear side 12 of the bearing cap body 6, as can be seen from FIG. 4. The axial sliding bearing surface (s) 14, 15 are designed as (partial) coatings on the bearing cover body 6. The axial sliding bearing surface (s) 14, 15 preferably adjoin / close directly to the radial sliding bearing surface 4 of the bearing cover 3 and are arranged at an angle thereto, in particular at an angle of 90 °. Thus, the axial sliding bearing surfaces 14, 15 follow the cross-sectional profile of this radial sliding bearing surface 4 (viewed in the axial direction 13) at least in the area immediately adjacent to the area of the radial sliding bearing surface 4 (viewed in the axial direction 13)

Support of the component to be supported, in particular a shaft.

According to a preferred embodiment of the bearing cover 3, the axial sliding bearing surface (s) 14, 15 can have a convex course, as can best be seen from FIG. 3. For this purpose, it can be provided that this axial sliding bearing surface (s) 14, 15 has a varying height 16 viewed perpendicular to the first radial sliding bearing surface 4. The axial sliding bearing surface (s) 14, 15 preferably has / have their greatest height 16 in the area of half the angle cover, in particular exactly at the location of the half angle cover, of the first radial sliding bearing surface 4. When the first radial sliding bearing surface 4 extends

The axial sliding bearing surface (s) 14, 15 thus has / have their greatest height over 180 °

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The height 16 of the axial sliding bearing surface (s) 14, 15 is always perpendicular to the first

Radial plain bearing surface 4 measured.

According to a further embodiment variant of the bearing cap 3, which can be seen in particular from FIG. 4, the axial sliding bearing surface (s) 14, 15 is / are formed on a thickening 17, i.e. on a web protruding over the bearing cap body 6. The thickening 17 preferably has a surface (viewed in the axial direction 13) which corresponds to the surface of the respective axial sliding bearing surface 14, 15.

The area of the thickening 17 can also be larger.

It is also possible for the thickening to have a higher density or compression compared to the bearing cover body 6, in order to allow the respective axial sliding

To give bearing surface 14, 15 a higher mechanical strength.

The two axial sliding bearing surfaces 14, 15 are preferably of identical design. However, they can also have a shape or geometry that differs from one another, with the described configuration of the height 16 (FIG. 3) being preferred.

is realized in both.

The axial sliding bearing surface (s) 14, 15 preferably has / have a symmetrical profile, i.e. the height 16 (Fig. 3) starting from half the angular cover of the first radially inner bearing receiving surface 4 decreases by the same value on the left and right. The axial sliding bearing surface (s) 14, 15 can thus have their lowest height 16 in the region of the start of the first radial sliding bearing surface 4, that is to say in the region of the transition from the clamping surface 7

(Fig. 3) on the first radial sliding bearing surface 4.

The axial sliding bearing surface (s) 14, 15 can have a maximum height 20, which is selected from a range of 10% to 50%, in particular 20% to 40%, a maximum height 18 (FIG. 3) of the bearing cover 3 above the first radial sliding bearing surface 4. The smallest height 16 can be selected from a range from 5% to 45%, in particular 10% to 40%, of the maximum height 16.

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The axial sliding bearing surface (s) 14, 15 can be completely uninterrupted. However, according to a further, preferred embodiment variant, there is also the possibility that the axial sliding bearing surface (s) 14, 15 is interrupted by at least one groove-shaped recess 19. The groove-shaped recess 19 preferably extends over the entire height 16 of the axial sliding bearing surface (s) 14, 15.

Thus preferably extends up to the first radial sliding bearing surface 4.

The groove-shaped recess 19 can have a depth between 0.05 mm and 3 mm and / or a width between 0.5 mm and 20 mm. The groove conveying continues

moderate depression preferably straight.

According to a further embodiment of the bearing cap 3, it can be provided that the transition between the axial sliding bearing surface (s) 14, 15 and an axial end surface 20 of the bearing cap body 6 is not abrupt, but with

a rounding is formed.

According to a further embodiment variant of the bearing cover 3, it can be provided that the axial sliding bearing surface (s) 14, 15 is / are also formed above the clamping surfaces 7, as can be seen, for example, from FIG. 2. The axial sliding bearing surface (s) 14, 15 can only extend over a partial area of a length 21 (FIG. 3) of the clamping surfaces 7 in the direction of a total length 22 (FIG. 4) of the bearing cover 3, as shown in FIG is shown in full lines, or over the entire length 21 of the clamping surfaces 7, as indicated by dashed lines in FIG. If the axial sliding bearing surface (s) 14, 15 extends / extend only over a partial area of this length 21 of the clamping surfaces 7, they can be formed so as to protrude, as is shown in FIGS. 2 to 4. In particular, the axial sliding bearing surface (s) 14, 15 can be configured to extend through the screw bolt receptacles 10 up to the level of the longitudinal central axis

be.

It can further be provided that a transition from the axial sliding bearing surface (s) 14, 15 above the clamping surfaces 7 to the axial sliding bearing surface (s) 14, 15 above the first radial sliding bearing surface 4 of the bearing cover 3 with a rounding 23

(Fig. 3) is provided.

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As already stated, the bearing cover 3 is a sintered component. This can be re-compacted after sintering, so that the surface of the bearing cover 3 is designed to be closed before the coating to form the axial sliding bearing surface (s) 14, 15 and, if necessary, the first radial sliding bearing surface 4. According to one embodiment variant, it can also be provided that the bearing cover body 6 has a porosity that is between 1% and 30%, at least in the area of the axial sliding bearing surface (s) 14, 15. The porosity is determined in accordance with DIN EN ISO 2738, February 2000 edition.

In principle, the first radial sliding bearing surface 4 (and optionally the second radial sliding bearing surface 5) and / or the axial sliding bearing surface (s) 14, 15 can have a multi-layer structure, comprising a bearing metal layer and the sliding layer, as well as possibly further layers, such as a running-in layer, diffusion barrier layers, etc. According to one embodiment of the invention, however, it can be provided that the axial sliding bearing surface (s) 14, 15 and optionally the first radial sliding bearing surface 4 is / are formed by a direct coating of the bearing cover body 6 with a sliding bearing material. The second radial sliding bearing surface 5 of the bearing block 2 can also be produced by direct coating. The plain bearing material is directly connected to the bearing cover body 6.

deposited on or on this.

According to a further embodiment variant, a sliding varnish is preferably used as the sliding bearing material, which is in particular applied by dipping or spraying or

Painting or printing, etc., is applied.

However, another slide bearing material can also be used to produce these bearing surfaces, in particular a metallic slide bearing material such as a tin-based alloy, an aluminum-based alloy, etc. The metallic slide bearing material can be deposited on the bearing cover body 6 by plasma spraying, such as atmospheric plasma spraying in particular. However, there are also other coating methods for forming the axial sliding bearing surface (s) 14, 15 and, if necessary, the radial sliding bearing

area 5 can be used.

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The lubricating lacquer layer formed from the lubricating lacquer can contain at least one polymer or its precursor as the main component. This can be selected from a group comprising polyimides, especially aromatic, polyamide-imides, especially aromatic, polyaryletherimides, optionally modified with isocyanates, phenolic resins, polyaryletheretherketones, polyamides, especially aromatic, epoxy resins, polytetrafluoroethylene, fluorine-containing resins, such as, for example, polyfluoroalkoxy-polytetrafluoroethylene copolymers -tetrafluoroethylene, fluorinated ethylene-propylene copolymers, polyvinylidene difluoride, polyvinyl fluoride, allylene sulfide, poly-triazo-pyromellithimides, polyesterimides, polyarylsulfides, polyvinylensulfides, polysulfones, polyarylsulfones, polyaryloxides, mixtures and copoly-

more from it.

The proportion of polymer in the anti-friction lacquer layer can be selected from a range with a lower limit of 30% by weight and an upper limit of 95

Wt%.

The anti-friction varnish layer can contain at least one additive selected from a group comprising lubricants such as MoSz2, h-BN, WSz2, graphite, polytetrafluoroethylene, Pb, Pb-Sn alloys, CF2, PbF2, hard materials such as CrOs, Fe3sO4 , PbO, ZnO, CdO, Al2Os, SiC, SisNa, SIO2, SisN4, clay, talc, TiO2, mullite, CaC2, Zn, AlN, FezP, Fe2B, Niz2B, FeB, mixed oxides, especially rutile-based, metal sulfides such as ZnS , Agz2S, CuS, FeS, FeSz, Sb2S3, PbS, Bi2S3 :, CdS, metal particles such as Cu, Cr, Al, Co, Fe, Ni, Bi, Sn particles, fibers, in particular inorganic, such as glass, carbon, potassium titanate, whiskers, such as SiC, metal fibers, such as Cu or steel, and mixtures thereof. The additive can be added in a proportion selected from a range with a lower limit of 5% and an upper limit of 30%.

The additives can have a particle size between 20 nm and 10 μm

and are preferably in a defined form and distribution.

The fibers can be stretched from 1 µm to 300 µm in the longitudinal direction

exhibit.

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The sliding lacquer layer preferably comprises or consists of a polyimide resin, in particular a polyamide-imide resin, molybdenum disulfide (MoS2) and graphite, the proportion of the polyimide resin with solvent being selected from a range with a lower limit of 60% by weight and an upper limit of 80% by weight, the proportion of MoSz2 is selected from a range with a lower limit of 10% by weight and an upper limit of 30% by weight and the proportion of graphite is selected from a range with a lower limit of 2% by weight and an upper limit of 20% by weight, with the proviso that

add 100% by weight to all components of the anti-friction coating.

The direct coating (the lubricating lacquer layer) can have a layer thickness selected from a range with a lower limit of 5 μm and an upper limit of 300 μm, in particular from a range from 10 μm to 100 μm

µm, preferably from a range from 15 µm to 60 µm.

Fig. 5 shows a further variant of the bearing cap 3, this Fig. A section of the bearing cap 3 in the area of the right screw bolt

Recording 10 of the bearing cap 3 shows in cross section.

In this embodiment variant, the bearing cover 3 has a plurality of centering elements 24 in the screw bolt receptacles 10 (i.e. within the screw bolt receptacles 10). The centering elements 24 are used to center the bearing cap 3 when the bearing cap 3 is mounted on the bearing bracket 2. In this embodiment variant, the bearing cap 3 preferably has no further centering elements in addition to the centering elements 24 in the screw bolt receptacles 10, so that in particular the clamping surfaces 7 of the bearing cap 3 or the counter-clamping surfaces 8 of the bearing block 2 can be made free of such elements and smooth. In this context, smooth means that these surfaces can have the surface roughness resulting from the manufacturing process. In this embodiment, centering elements 24 are therefore preferred exclusively in the screw bolt

Zen receptacles 10 arranged or formed.

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After the bearing cover 3 is designed as a sintered component, its clamping surfaces 7 can be designed as sintered rough. The clamping surfaces 7 (and also the counter-clamping surfaces 8) can optionally have a further surface treatment

be to degrade the roughness.

The centering elements 24 extend over at least a partial area of the entire longitudinal extension (height) of the respective screw bolt receptacles 10. The centering elements 24 can extend over a region between 5% and 90%, in particular between 30% and 80%, of the entire longitudinal extent of the screw bolt receptacles 10 . However, it is also possible that the centering elements 24 extend over the entire longitudinal extent of the screw bolts.

took 10 stretch.

The centering elements 24 can have a maximum height, measured against the respective boundary surface 13 of the screw bolt receptacles 10, which is selected from a range from 0.1 mm to 3 mm, in particular from a

Range from 0.1 mm to 0.5 mm.

The centering elements 24 or at least individual ones preferably extend

of the centering elements 24 up to the respective clamping surface 7. Accordingly, the centering elements 24 are preferably spaced from an opening 25 of the respective screw bolt receptacle 10, which opposes its opening 26 in the clamping surface 7.

is superimposed, as can best be seen from FIG.

However, there is also the possibility that the centering elements 14 are spaced apart from the opening 26 in the clamping surface 7 and optionally in the opening 25 of the

Screw bolt receptacle 10 are arranged beginning, as can be seen from Fig. 6, the design variants of the bearing cover 3 excerpts in the transverse

cut shows.

A plurality of centering elements 24 are preferably arranged per screw bolt receptacle 10. It is particularly preferred if, according to an embodiment

variant in one of the two screw bolt receptacles 10 at least three centering

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elements 24 and in the other of the two screw bolt receptacles 10 at least two centering elements 24 are arranged. In general, a screw bolt receptacle 10 can have more centering elements 24 than the other screw

bolt receptacle 10, in particular by a centering element 24 more.

In this case, the two centering elements 24 are preferably arranged in the at least two centering elements 24 having screw bolt receptacle 10 on the boundary surface of the screw bolt receptacle 10 that they are opposite one another, that is, offset from one another by 180 ° (based on the central axis through the centering elements 24), and that them in the direction of the axial direction

13 are opposite each other through the bearing cover 3.

The three centering elements 24 in the at least three centering elements 24 having screw bolt receptacle 10 are preferably arranged on the boundary surface of the screw bolt receptacle 10 that one of the centering elements 24 is offset at an angle of 90 ° to the arrangement of the two centering elements 24 in the other screw bolt receptacle 10. The two remaining centering elements 24 are then preferably offset by 120 ° each (based on the central axis through the centering elements 24) to the first-mentioned centering element 24. Overall, the centering elements 24 are therefore preferably symmetrical

arranged distributed over the circumference of the boundary surface.

However, more than two or three centering elements 24 can also be arranged or formed in the screw bolt receptacles 10, for example three, four, five, etc. It is also possible that in each of the screw bolt receptacles 10

an equal number of centering elements 24 is arranged.

According to another embodiment of the bearing cover 3, the centering elements 24 are designed as webs 27 protruding beyond the boundary walls of the screw bolt receptacles 10. The centering elements 24 are preferably at least approximately strip-shaped, so that they have a significantly greater length than their width, as can be seen from FIGS. 5 and 6. As a general rule

can have a maximum width 28 of the centering elements 24 in the circumferential direction of the

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Bolt receptacles 10 can be selected from a range from 0.5 mm to

5 mm, in particular from a range from 1 mm to 2.5 mm.

The centering elements 24 can, however, also have a different shape, for example they can be in the direction of the boundary surfaces of the screw bolt

Zen receptacles 10 viewed triangular, oval, etc., be formed.

However, it is possible that the centering elements 24 of a screw bolt receptacle 10 differ with regard to their width 28 in the circumferential direction of the boundary surface and / or with regard to their height. Preferably, however, all centering elements 24 within each (or the) screw bolt receptacle (s) 10 are equally balanced.

educated.

The centering elements 24 preferably have a higher plastic deformability than the screw bolts, i.e. at least the thread of the screw bolts. This can be achieved in that the centering elements 24 consist of a softer material, the screw bolts and / or that the centering elements 24 have cavities, for example pores, which are at least partially compressed during plastic deformation. For this purpose, the centering elements 24 can in particular consist of a sintered material. As already stated, however, the entire bearing cover 3 is preferably made of the material from which

the centering elements 24 are made.

In particular, the centering elements 24 and the bearing cover 3 can be made of a metallic material, for example aluminum or an aluminum alloy

tion or a magnesium alloy be made or consist of it.

Since the centering elements 24 can consist of a softer material than the screw bolts, one embodiment of the bearing arrangement 1 can provide that the thread of at least one of the screw bolts overlap with at least one of the centering elements 24 of at least one screw bolt socket 10. This over-

with each of the centering elements 24 in the respective screw

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took 10 into which the bolt is inserted. Because of this overlap, material displacement of the centering elements 24 occurs when the screw bolts are screwed in, as a result of which a type of thread is formed or cut into the centering elements 24. By adapting the centering elements 24 during the initial assembly of the bearing block 2 and bearing cap 3, the reassembly and realignment of the bearing cap 3 is also

Simplified relative to bearing block 2.

The centering elements 24 can have a constant cross section over their entire longitudinal extension, as is shown by the variant embodiment of the bearing cover 3 according to FIG. 6. According to a further variant of the bearing cover 3, however, it is also possible for the centering elements 24 to be at least partially tapered over their longitudinal extension, as can be seen from FIG. 7, or to be provided with a facet. In particular, the centering elements 24 can be provided with a cross-section tapering away from the clamping surface 7 (FIG. 7), so that an “upper” area of the centering elements 24, which first comes into contact with the screw bolt when the screw bolt is screwed in, tapers or me a facet is formed, for example is tapered. It can thus screw in the

Bolt 8 can be simplified.

For better plastic deformability, the centering elements 24 of the bearing cover 3 can at least over a range of 20% to 100% of their longitudinal

stretching have a conically tapering course.

The centering elements 24 can have a rectangular, square, etc. cross section (viewed in plan view of the clamping surfaces 7). In order to simplify the screwing in of the screw bolts or to simplify the plastic deformation described above in the event of an overlap with the threads of the screw bolts, according to an embodiment of the bearing cover 3 it can be provided that the centering elements 24 tapers away in the direction of the boundary surfaces Have cross-section. In particular, the centering elements 24 or at least individual

thereof, have an at least approximately trapezoidal cross-section.

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For the same reason, it can be provided according to a further embodiment of the bearing cover 3 that a transition area 29 from the boundary surfaces of the screw bolt receptacles 10 into the centering elements 24 is beveled or rounded, as shown in FIG. 8. The transition area 29 is formed at the beginning of the centering elements 24, i.e. that area which, when the screw bolts are screwed in, is first in contact with the screw bolts 8

emotion comes.

As an alternative or in addition, other transition areas from the boundary surface of the screw bolt receptacles 10 can be rounded or beveled along their longitudinal extension, that is, in the area of side walls 30 of the centering elements 24 adjoining the boundary surface, such as

this is shown in FIG. 6.

To simplify the introduction of the screw bolts or to simplify the plastic deformation in the event of an overlap with the threads of the screw bolts 8, according to one embodiment of the bearing cover 3 it can be provided that the centering elements 24 in at least one of the two screw bolt receptacles 10, preferably all Centering elements 24 of the bearing cover 3 are formed over the course of their longitudinal extent with increasing height 31 above the boundary surface, as shown in FIG. 8 by dashed lines. The height of the centering elements 24 increases in the direction of the clamping surfaces

7 TO.

As already stated, the centering elements 24 are arranged according to an embodiment variant of the bearing cover 3 at a distance from the insertion opening for the screw bolt. According to a variant of the bearing arrangement 1, it can be provided that the screw bolts in the areas of the screw bolt receptacles 10 that adjoin the centering elements 24 in the direction of the longitudinal extension of the screw bolt receptacles 10 are designed without threads, e.g. are designed with a cylindrical shaft. The screw bolts can thus be made smooth starting with a screw bolt head in the first section of a shaft. At least this thread-free area can be used for better de-

mountability of the screw bolts also be conical, ie

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with decreasing diameter from the screw bolt head. The

The length of the smooth shaft can be between 0.5 cm and 5 cm.

It is also possible for the centering elements 24 to have a recess 32, for example a longitudinal groove, in the front wall, as shown in dashed lines on the basis of the embodiment variant of the bearing cover 3 according to FIG. 7, and / or in at least one of the side walls 30, whereby the plastic deformability of the

Centering elements 24 can also be improved.

According to another embodiment of the bearing cap 3, for the same reason, it can be provided that such a recess is formed in at least one of the areas of the boundary surfaces of the screw bolt receptacles 10 (directly) adjoining the side walls 30 of the centering elements 24, for example a longitudinal groove in the direction of the longitudinal extent the screw

pin receptacles 10.

The longitudinal extent of the centering elements 24 is preferably greater than their width, as has been explained above. It can be provided that the longitudinal extension of the centering elements 14 is greater by a value that

selects is from a range from 1:10 to 1: 100 in width. In general, a ratio of the longitudinal extension of the centering elements 24 to their width can be selected

be from a range of 1: 1 to 1: 100.

The exemplary embodiments show possible design variants of the bearing arrangement 1 or of the bearing cover 3, it being noted at this point that also

Combinations of the individual design variants with one another are possible.

For the sake of order, it should finally be pointed out that for a better understanding of the structure of the bearing arrangement 1 or the bearing cover 3, these

are not necessarily shown to scale.

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20th

List of reference symbols

Bearing arrangement 31 Height of the bearing block 32 Recess of the bearing cover Radial plain bearing surface Radial plain bearing surface Bearing cover body Clamping surface Counter-clamping surface Protrusion of the screw bolt seat front

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Axial direction axial sliding bearing surface axial sliding bearing surface height

Thickening maximum height

deepening

Face

length

overall length

Rounding centering element

opening

opening

web

width

Transition area

Side wall

N2019 / 06300-A T-00

Claims (1)

Claims 1. Bearing cover (3) for a split bearing arrangement (1) which, in addition to the bearing cover (3), comprises a bearing block (2), the bearing cover (3) having a bearing cover body (6) which has a radial sliding bearing surface (4) and at least one axial sliding bearing surface (14, 15), wherein the axial sliding bearing surface (14, 15) is designed as a coating of the bearing cover body (6), characterized in that the bearing cover body (6) is made of a metallic sintered material is formed. 2. Bearing cover (3) according to claim 1, characterized in that the axial sliding bearing surface (14, 15) has a convex shape, the greatest radial height (16) of the axial sliding bearing surface (14, 15) in the region of half the Winkelabde- is trained. 3. Bearing cap (3) according to claim 1 or 2, characterized in that the axial sliding bearing surface (14, 15) is formed on a thickening (17) of the bearing cap body (6) in the axial direction (13). 4. Bearing cap (3) according to one of claims 1 to 3, characterized in that the bearing cap body (6) in the region of the axial sliding bearing surface (14, 15) has a porosity that is between 1% and 30%. 5. Bearing cover (3) according to one of claims 1 to 4, characterized in that the radial sliding bearing surface (4) and / or the axial sliding bearing surface (14, 15) by a direct coating of the bearing cover body (6) with a sliding bearing gerwerkstoff is / are formed. 6. bearing cover (3) according to claim 5, characterized in that the Plain bearing material is a bonded varnish. N2019 / 06300-AT-00 7. Bearing cover (3) according to one of claims 1 to 6, characterized in that a groove-shaped recess (19) in the axial sliding bearing surface (14, 15) is arranged. 8. bearing cap (3) according to one of claims 1 to 7, characterized in that a transition between the axial sliding bearing surface (14, 15) and the Bearing cover body (6) is provided with a rounding. 9. bearing cap (3) according to any one of claims 1 to 8, characterized in that in the bearing cap body (6) screw bolt receptacles (10) for receiving screw bolts for connecting the bearing cap (3) to the bearing block (2) are arranged, wherein the Screw bolt receptacles (10) have a longitudinal extension and are delimited by boundary surfaces, and with centering elements (24) for centering the bearing cover (3) when mounting the bearing cap (3) on the bearing block (2), which are arranged within the screw bolt receptacles (10) , and covering at least part of the Ren longitudinal extension of the screw bolt receptacles (10) extend. 10. Bearing cap (3) according to claim 9, characterized in that in one of the two screw bolt receptacles (10) at least three centering elements (24) and in the other of the two screw bolt receptacles (10) at least two Centering elements (24) are arranged. 11. bearing cap (3) according to claim 8 or 9, characterized in that the centering elements (24) are at least approximately strip-shaped are. 12. Bearing cover (3) according to one of claims 8 to 11, characterized in that the centering elements (24) have an at least approximately trapezoidal have gene cross-section. N2019 / 06300-AT-00 13. Bearing cap (3) according to one of claims 8 to 12, characterized in that the centering elements (24) in one of the screw bolt receptacles (10) are longer than the centering elements (24) in the other screw bolt receptacle (10). 14. Bearing cap (3) according to one of claims 8 to 13, characterized in that at least one of the centering elements (24) in at least one of the two screw bolt receptacles (10) over the course of its longitudinal extension is formed with increasing height (31). 15. Bearing arrangement (1) with a bearing cover (3) and an abutting bearing block (2), characterized in that the bearing cover (3) according to one of claims 1 to 14 is formed. N2019 / 06300-AT-00