DE102018101070A1 - Radial or axial plain bearing element with surface structure on the bearing seat surface - Google Patents

Abstract

The invention relates to a radial or Axialgleitlagerelement (10) having a support layer (12) forming a bearing seat surface (14). The bearing seat surface (14) has a surface structure on at least one surface section (20), which comprises a plurality of material ejections (28, 41, 51) from the support layer (12) and differs from the structure of the bearing seat surface (14) outside the surface section (FIG. 20), wherein the surface structure of the surface portion (20) forms a machine-readable encoding. The bearing seat surface (14) has, outside the surface section (20), a roughness core profile with a core roughness around a reduced peak height R (0) measured according to DIN EN ISO 13565 (1,2), wherein the surface structure of the surface section (20) has a reduced peak height R (S) which is greater than 3.5 times the reduced peak height R (0) of the bearing seat surface (14) outside the surface portion (20).

Description

The invention relates to a radial or Axialgleitlagerelement, in particular a plain bearing shell, a plain bearing bush or thrust washer, with a support layer which forms a bearing seat surface.

As a "base layer" is usually a dimensional stability of the radial or Axialgleitlagerelementes determining material layer of a multilayer composite bearing. This usually consists of steel or in the case of a so-called solid bearing from the bearing metal. As a "bearing seat surface" is generally the sliding surface opposite surface of the radial or Axialgleitlagerelementes, so for example, the outer peripheral surface of the plain bearing shell or plain bearing bush or the rear surface of the thrust washer designated. This surface is after installation on the inner peripheral surface or the end face of the bearing seat. Under "Radial or Axialgleitlagerelement" in addition to the aforementioned bearing shells, bushes or thrust washers and combined radial Axialgleitlagerelemente included.

Radial or Axialgleitlagerelemente and in particular bearing shells, for example, for use in internal combustion engines as a main or connecting rod bearings are usually secured by a frictional connection, ie by frictional engagement against rotation during operation. To build up a sufficient frictional engagement, the two contact surfaces, ie the inner peripheral surface of the bearing seat and the bearing seat surface of the radial bearing element must have a suitable structuring, so that a sufficiently high coefficient of friction between the radial sliding bearing element and the bore surface of the bearing seat is formed when the radial sliding bearing element with the intended oversize in the Bearing seat is installed.

A suitable structuring of the connecting rod and main bearing bores is achieved in practice by Kreuzhonung. It is much cheaper to manufacture, however, if the cross honing can be omitted and the bore only has to be finely turned. Therefore, it is desirable for the engine manufacturer to eliminate the step of cross honing. However, to create a suitable patterning of the surface of the bore so that the friction between the bearing seat surface of the radial sliding bearing element and the bore is sufficient to prevent twisting during operation, finely turned drilling surfaces are known to be provided with laser markings.

From the DE 10 2012 024 141 A1 It is known that instead of or in addition to the bore, the radial sliding bearing element is at least partially provided with a friction-increasing surface structure. In particular, it is proposed to achieve the friction-increasing surface structure by machining. In this case, the average roughness of the friction-increasing surface structure should be at least Rz = 5 μm to 50 μm and the coefficient of friction of the frictional connection between the radial plain bearing element and the bearing seat should be at least μ = 0.1.

A further disadvantage, however, is that an additional step is needed to produce sufficient friction to prevent rotation. The additional work step has been passed here only from the engine to the production of bearings.

Against this background, it is an object of the present invention to provide a radial or Axialgleitlagerelement of the type mentioned, on the one hand on the bearing seat surface has sufficient structuring to produce a sufficient frictional engagement also in cooperation with a finely rotated bore, which on the other hand but also economical to produce.

The object is achieved by a radial or Axialgleitlagerelement with the features of claim 1.

In the radial or thrust bearing member of the present invention having a support layer forming a bearing seat surface, the bearing seat surface has at least one surface portion a surface structure comprising a plurality of material ejections from the support layer and different from the structure of the bearing seat surface outside the surface portion Surface structure of the surface portion forms a machine-readable encoding.

As "area section" in the sense of this document, for example, that contiguous partial surface of the bearing seat surface is referred to, which is occupied by a complete machine-readable encoding. The surface structure of the surface portion is also referred to herein as a "mark", which term includes both surface structures that form an encoding and those that only increase friction without simultaneously carrying information. As a "machine-readable", it becomes physical herein understood that the coding on the surface portion under certain conditions, in particular a certain lighting, forms a sufficient contrast to the surface portion surrounding bearing seat surface to capture the coding with technical aids can. In terms of information technology, this is understood to mean that the "machine-readable coding" contains information and permits an exchange of information with a machine. The machine-readable coding may in particular comprise a font, a numerical code, a one-dimensional or a two-dimensional character code, particularly preferably a barcode or a data matrix code (DMC), or a combination of several codes. The "bearing seat surface outside the surface portion" is also referred to as the "surface area of the bearing seat surface surrounding the surface portion". Of course, it is clear that this region of the bearing seat surface also has a certain structure, which as a rule is conditioned by the production method and can be characterized, for example, by a specific roughness value. For the reduced top height R _pk (0) of bearing seating surfaces may typically be assumed to be 0.1 μm to 1.0 μm, and preferably 0.2 μm to 0.6 μm. Since it is free of material build-up or other roughening requiring an additional operation, it is also referred to herein for convenience as an "unstructured surface". In contrast, the surface section with the surface structure according to the invention is also referred to as a "structured surface section".

Background of the invention is that radial or Axialgleitlagerelemente - like many other engine components - have a solid mark, based on the bearing shell can be clearly identified. The marker bears information about the manufacturer, for example, the part number, the manufacturing batch and / or dates in order to trace back the production route and thus, among other things, to make the store tamper-proof. Also, information about the exact geometry (e.g., wall thickness or wall thickness class) may be applied. Such markings are usually printed on the plain bearing inside.

The inventors have recognized, on the one hand, that such a coding can also be applied to the outer surface of the radial or axial sliding bearing element, that is, to its bearing seat surface. In a second step, the inventors have recognized that this coding can also be used to increase the coefficient of friction between the radial or axial sliding bearing element and the bore or end face sufficiently to produce an anti-rotation. Thus, two functions are combined in one element, namely the marking. As a result, the two operations Coding and applying a friction-increasing surface structure are combined, so that a total of one step is saved, which reduces the production of the radial or Axialgleitlagerelementes.

According to the invention, the surface structure not only has a roughening, but a plurality of material ejections, wherein "material deposition" is understood to mean a material accumulation firmly connected to the surface, which projects beyond the central surface of the bearing seat surface outside the surface portion, ie forms a local elevation , As a measure of the mean surface of the bearing seat surface outside the surface section, the upper dimension of the local roughness core profile is used, which is obtained when the Kernrautiefe R _k , to DIN EN ISO 13565 (1,2) determined. The norms DIN EN ISO 13565-1 and DIN EN ISO 13565-2 are collectively referred to herein as "DIN EN ISO 13565 (1,2)".

It is particularly advantageous if the bearing seat surface outside the surface section has a reduced peak height R _pk (0) measured after DIN EN ISO 13565-1 and DIN EN ISO 13565-2 , and the surface structure of the surface portion has a reduced peak height R _pk (S) measured after DIN EN ISO 13565-1 and DIN EN ISO 13565-2 which is greater than 3.5 times the reduced peak height R _pk (0) the bearing seat surface is outside the surface portion.

The inventors have thus found that a significantly increased frictional engagement of the bearing seat surface with the surface in a finely bored bearing seat over an unstructured bearing seat surface with R _pk = R _pk (0) occurs when the surface structure of the surface _{portion has} a reduced peak height R _pk (S), which is more than 3.5 times the reduced peak height R _pk (0) outside the surface portion, more preferably more than 8 times the reduced peak height R _pk (0), measured in each case DIN EN ISO 13565 (1,2), protrudes.

The height of the individual Materialaufwerfungen over the central surface of the bearing seat surface is a multiple, preferably at least one order of magnitude R _pk (0). If the material ejections protrude so much beyond the central surface of the bearing seat surface and also over the remaining roughness peaks of the unstructured bearing back, it is ensured that in contrast to a simple roughening of the bearing seat surface even with friction-reducing influences still a sufficient frictional engagement is present. Friction-reducing influences can arise, for example, due to the penetration of oil into the contact area between the bearing element and the bore, which results in an oil film or oil-carbon structure which can cover the lower roughness peaks (such as arise in a simple roughening). This carbonization as a result of penetrating oil with subsequent coking by the temperature loads during operation is often observed in such camps. Further friction-reducing influences can arise, for example, due to the smoothing of the roughness during operation, caused by micro-gliding due to component deformations. The Materialaufwerfungen invention oppose this Einlättungsprozess, as they suppress the micro slide by the particularly good frictional engagement with the bore or at least reduce. Furthermore, it is ensured by the Materialaufwerfungen invention, that in contrast to a simple roughening even with a relatively rough surface of the mating body (bore surface) the warping penetrate far enough into the mating profile and "interlock" with this, so that it does not lead to a sliding effect two rough surfaces can come together. In particular, the amount of the peak height is determined by the material throws according to the invention R _pk (S) ensured that they protrude beyond the core region of the profile "up" and thus come into contact with the counter-body. This distinguishes the invention from Reibschlusserhöhung by a "roughening" of the bearing seat surface, the roughness parameters such as the roughness profile height R _z (eg according to DIN ISO 4287), since an increase of R _z Also by "depressions" (furrows) in the roughness profile can be effected, but which do not contribute to an increase in the frictional engagement with the counter body.

The material in the Materialaufwerfungen can be formed both by deformed material from the support layer, including in parts by reaction products or foreign material, in particular oxidation products of the support layer material. A characteristic of the Materialaufwerfungen is, for example, in contrast to an imprint that their hardness at least the hardness of the base material, ie the material of the support layer corresponds.

The material is transformed by locally introduced energy. In particular, the energy can preferably be introduced mechanically by means of a stamping tool, such as a needle punch, or thermally by means of a laser. In the latter case, the material is locally melted and relocated. By way of example, the black engraving is mentioned, in which a punctiform depression with a dark oxidized surface and an ejection of the melt at the edge is formed by means of a laser.

In mass production, the thermal can be preferred to the mechanical process because it is not subject to wear.

Methods for roughening surfaces by means of laser ablation are known from the production of camshafts, cf. DE 10 2009 060 352 , In the method described there, strip-like craters are formed, the roughness pattern from the crater bottom to the tips of the adjoining ramparts having a maximum amplitude of 2 to 20 μm and on average about 5.5 μm and from the level of the unprocessed surface to the tips of the ramparts a maximum difference of 1 to 10 microns and an average of about 2.5 microns.

In contrast to laser ablation, an essential element of material ejection is that they are produced predominantly free from abrasion. Although it can not be completely avoided during melting by laser evaporation of material. However, it is known that a high power and a low pulse duration of the laser leads to a high energy input in conjunction with low heat dissipation, which favors the evaporation of the material. By a suitable choice of the power and pulse duration of the laser, therefore, the proportion of material removal can be minimized, so that it is ensured that the predominant material is melted and displaced from the center of the impinging laser beam to the edge region and not evaporated. As a rule, when producing a material, no matter whether by means of mechanical or thermal energy, wells or craters are formed in addition to the ejection.

The form of material deposition can be determined by the manufacturing process. For example, this may be formed conical-pointed or frusto-conical with a central crater, if in each case a selective energy input takes place by means of mandrel or laser in the material of the support layer. For example, it can also be wall-like elongated when a continuous wave laser or an elongated tool is used or when closely adjacent punctual effects occur.

In terms of numbers, "material" in the sense of this description is considered to be connected. As "coherent" the material throw is again called, as far as they are without Breaking the upper dimension of the roughness core profile of the bearing seat surface outside the surface portion surmounted.

Although a toothing of the contact surfaces of the radial or Axialgleitlagerelementes and the bearing seat can be adjusted from the first material launch on the bearing seat surface for a rotation, a minimum number of 20 material ejections on the support layer is preferred. At least 35 material ejections are particularly preferred.

The degree of toothing depends in addition to the height and the number substantially on the lateral extent and orientation of the individual material posing relative to the circumferential direction of the radial or Axialgleitlagerelements and their relative arrangement to each other. For example, a linear material launch, which is arranged perpendicular to the circumferential direction, a higher degree of toothing and thus produce a better rotation than a punctiform or a linear material posing, which extends in the circumferential direction. Basically, a number of 20 and better still 35 material ejections provides improved security against twisting, because in the idealized case of a "100% gearing" of each material launch with the mating body, the strength of each material launch is critical to the transmissible torque against twisting. In the idealized case, one can imagine that the tolerable torque against torsion is multiplicatively composed of the number and the respective cross section of the material ejections, the material strength of the material drops and the effective radius (half the diameter of the receiving bore).

In addition, as the number of material ejections increases, so does the codable information content, assuming that each individual material ejection represents a symbol of a code. By way of example, reference is made to the "GS1 Data Matrix Guideline", in which the information content is described as a function of the number of symbols for DMC codes.

The height P of the material ejections over the roughness core profile of the bearing seat surface outside the surface section, that is to say over its "middle surface", is preferably less than 250 μm, particularly preferably less than 150 μm.

And preferred is the reduced peak height R _pk (S) in the structured surface portion smaller than 200 microns, more preferably less than 100 microns and most preferably less than 50 microns.

The reduced top height R _pk (S) should not exceed the limit of 200 microns advantageously, because it may lead to insufficient contact of the bearing shell with the bore also outside the surface portion associated with negative effects of structural support of the bearing through the hole or the dissipation of frictional heat from the bearing element into the housing. With decreasing reduced peak height R _pk (S) to below 50 microns, the properties mentioned improve significantly, without this being accompanied by a significant deterioration of the security against rotation.

The reduced top height R _pk (0) the bearing seat surface outside the surface portion is preferably less than 1.5 microns, more preferably less than 1 micron.

In this area of roughness is usually the außenumfängliche steel surface of a converted to a bush or a bearing shell bearing composite material.

Preferably, the surface portion occupies at least 0.8%, more preferably at least 1.0% of the bearing seat surface.

The area portion, as already stated, denotes the contiguous area occupied by a complete readable code, not just the sum of the areas of the individual material dislocations. For example, the extent of the surface portion of a DMC code with the extension 10 mm x 10 mm for the purposes of this invention, 100 mm ² , while the contained therein, for example, 40 material ejections (including dots) with an area of 1 mm ^{2 in} total not more than 40 take ² mm. However, this does not mean that not several such surface sections, each with a complete readable coding spatially separated on the bearing seat surface can be arranged. Also, in addition to one or more surface portions each having a complete readable coding, one or more structured surface portions with the above-described requirements for the surface structure can be present, which carry no information and solely the increase of the entire friction increasing surface portion of the bearing seat surface, ie the sum of all structured Surface sections, serve. If a plurality of structured surface sections are provided on the bearing seat surface, then one or more optionally one or more, in particular also all, structured surface sections, must form an encoding. In the case of a plurality of surface sections forming the coding, the coded information can be distributed among these and / or be distributed partially or completely redundantly thereon.

Further preferably, the surface portion extends in a radial sliding bearing element in the axial direction over a width of at least 15%, more preferably at least 20% of its overall width. Correspondingly, the surface section in the case of an axial sliding bearing element extends in the radial direction over a width of at least 15%, particularly preferably at least 20%, of its radial extent.

It is understandable that the size of the structured surface portion expediently depends on the size of the entire bearing seat surface and thus on the size of the radial or Axialgleitlagerelementes. As already stated above, for the increase in friction, the expansion of the material ejections perpendicular to the circumferential direction plays a more significant role than that in the circumferential direction, in any case when the individual material ejections are close to one another in the circumferential direction. If there is a distance of at least three times the height P of the elevations between these elevations, the material ejections arranged one behind the other in the circumferential direction also contribute to the same extent to increase the friction.

However, since it is not free in terms of coding to arrange the material ejections preferably in the circumferential or longitudinal direction, because the position of the individual Materialaufwerfungen by the format of the coding and the information is given, a sufficient increase in friction under all circumstances only by a sufficient extent the Materialaufwerfungen perpendicular to the circumferential direction and be ensured by sufficient distance in the circumferential direction. It has been concretely stated that from a relative width of the surface section of 15% relative to the radial or axial plain bearing element, sufficient toothing of the contact surfaces of the radial or axial plain bearing element and the bearing seat can be achieved. Preferably, the structured surface portion is located in the circumferential direction outside of the main load range of the radial or Axialgleitlagerelements. In the case of a plain bearing shell, the surface portion is therefore preferably arranged in an angular range of 5 ° to 65 °, measured from a partial surface of the plain bearing shell.

As a "partial surface" of a sliding bearing shell whose end-side peripheral end surfaces are referred to, which are pressed during installation due to a slight oversize on the respective partial surfaces of the opposite plain bearing shells, whereby the necessary frictional engagement between the contact surfaces of the bearing shells and the bearing seat is generated.

The bearing seat surface particularly preferably has two structured surface sections, wherein a first surface section in the angular range of 5 ° to 65 °, measured from a first partial surface, and a second surface section in the angular range of 5 ° to 65 °, measured from one of the first partial surface related is arranged on the vertex of the sliding bearing shell, opposite second partial surface.

As a result, the force distribution is distributed by the frictional engagement more uniformly over the peripheral surface of the sliding bearing shell.

It is further preferred if the structured surface portion or the structured surface portions are arranged in the case of a sliding bearing shell substantially symmetrical to the axial center line on the bearing seat surface. This also serves a uniform force distribution by the frictional engagement, this time seen over the axial width of the bearing shell.

• 1 eine Darstellung einer erfindungsgemäßen Gleitlagerschale in perspektivischer Ansicht;
• 2 ein Rauheitsprofil im Bereich einer einzelnen Materialaufwerfung;
• 3 ein erstes Beispiel einer Codierung;
• 4 ein zweites Beispiel einer Codierung;
• 5 einen ersten Rauheitsmessschrieb auf einem unstrukturierten Oberflächenabschnitt der Lagersitzfläche und
• 6 einen zweiten Rauheitsmessschrieb gemessen entlang einer Messstrecke durch einen Flächenabschnitt mit der erfindungsgemäßen Oberflächenstruktur;

Further features and advantages of the invention will be described below with reference to embodiments. Show it:

• 1 an illustration of a plain bearing shell according to the invention in a perspective view;
• 2 a roughness profile in the area of a single material launch;
• 3 a first example of coding;
• 4 a second example of coding;
• 5 a first roughness measurement chart on an unstructured surface portion of the bearing seat surface and
• 6 a second roughness measurement record measured along a measurement path through a surface section having the surface structure according to the invention;

1 shows a sliding bearing shell according to the invention 10 with a base course 12 that has a bearing seat area 14 formed. The bearing seat area 14 is the outer peripheral surface of the plain bearing shell 10 and ends in the circumferential direction of the end-side end surfaces, including partial surfaces 16 . 16 ' called. The main load area of the plain bearing shell 10 is usually in the area of the vertex, characterized by the crest line 18 , Outside this main load area is located on the bearing seat surface 14 a structured surface section 20 , This is more accurate in an angular range 22 arranged, ranging from 5 ° to 65 °, measured from a partial area 16 extends. The area section 20 is also symmetrical to the midline 24 the sliding bearing shell 10 arranged with respect to the axial direction.

On the crest line 18 opposite side of the bearing shell 10 is measured from the opposite partial surface 16 ' a similar angular range 22 ' from 5 ° to 65 °, in which there may be another structured surface portion with a surface structure according to the invention. Neither the second angle range nor the second structured surface portion are drawn in this perspective.

The area section 20 has a surface structure containing a plurality of material ejections from the backing layer 12 includes and differs from the structure of the bearing seat surface 14 outside the area section 20 differs, wherein the surface structure of the surface portion 20 forms a machine-readable encoding, in this case schematically indicated as a two-dimensional code. The second structured surface section (not illustrated) on the opposite side of the bearing shell may optionally also contain the same machine-readable coding, or another or a surface structure without information.

2 shows a schematic section of a roughness measurement profile, as is the case when the bearing seat surface 14 in the area of a single material launch 26 For example, could represent by means of a stylus tip of a surface measuring device. It can be seen that the material throw 26 significantly above the roughness profile of the surrounding area 28 , which represents the unstructured bearing seat area, rises. If you wear, as described above, the height P of individual material puffs above the upper dimension of the roughness kernel profile R _k (0) (in 2 when R _k designated) of the unstructured bearing seat surface, measured according to DIN EN ISO 13565 (1,2), this is about an order of magnitude above the reduced peak height R _pk (0) (in 2 when R _pk designated).

3 shows a "DMC" (for DataMatrix code) as a first embodiment of a machine-readable coding formed by the surface structure on the bearing seat surface of a radial or Axialgleitlagerelements invention. The concrete example is a square 2D code containing 18x18 characters. However, codes containing fewer or more characters may also be used. The contiguous partial surface of the bearing seat surface occupied by the complete machine-readable coding, here for illustration as a dashed frame not belonging to the code 30 marks, forms the area section.

The reduced top height R _pk (S) of this surface structure within this surface section 30 it applies by means of roughness measurement to DIN EN ISO 13565 (1,2) and with the reduced peak height determined by the same method R _pk (0) the bearing seat surface outside the surface portion 30 to compare. For this purpose, the surface structure within this surface section 30 along two mutually perpendicular measuring sections 32 . 34 retracted, optionally tactile by means of probe or optically by means of laser. The larger of the two measured values for R _pk (S) is compared to the reduced peak height R _pk (0) of the unstructured area section used.

This has the following background, based on 4 is explained. Herein, a one-dimensional bar code (or "bar code") is selected as the second exemplary embodiment of a machine-readable code formed on the bearing seat surface of a radial or axial sliding bearing element according to the invention. The area occupied by the complete machine-readable coding surface portion of the bearing seat surface is illustratively again as a dashed, not belonging to the code frame 40 marked.

Would the reduced top height R _pk (S) the surface structure within this surface section 40 Measured along an arbitrary measuring path, it can not be ruled out that this measuring path coincides with the direction of the bars of the code. The thus determined reduced peak height R _pk (S) would not be representative of the coefficient of friction increase achieved by the bar code and, in the limiting case, perhaps not even higher than the reduced peak height R _pk (0) of the unstructured area section. This systematic error can be found in the measurement procedure described above, according to which the surface structure within this area section 40 along two mutually perpendicular measuring sections 42 . 44 and the larger of the two measured values thus obtained for R _pk (S) for comparison with the reduced peak height R _pk (0) of the unstructured surface section is excluded.

Practically, from a measured surface of the unstructured bearing seat surface, the roughness profile according to the recommendations, for example, for the reference length for the measuring section, in the relevant Standard DIN EN ISO 13565 (1,2) and determined by separation of the primary profile in roughness and waviness and from this the reduced peak height R _pk (0) extracted ("reference measurement"). 5 shows the result of such a roughness measurement carried out on an unstructured surface portion of the bearing seat surface of a thrust washer according to the invention. The measurement was performed tactilely with a TK300 probe over a measuring distance of 4.8 mm. It contains a roughness measurement chart in the upper part 50 , bottom left a material share curve (Abbott curve) 52 and below right, a frequency distribution 54 , each in the usual representation. The parameters of the roughness profile determined from the measurements DIN EN ISO 13565 (1,2) are given in Table 1 below. Table 1 Ra 0.62 μm March 4.66 μm rpk 0.34 μm rvk 1.85 μm Rk 1.34 μm Rmax 5.78 μm M r1 7.1% Mr2 79.1%

The specific values determined here are typical for the surface or bearing seat surface of a steel support layer. The reduced top height R _pk For example, (0) is typically 0.34 μm, which is below the upper limit of 0.8 μm preferred for the unstructured bearing seat surface.

In an analogous way shows 6 the result (Rauheitsmessschrieb 60 Material share curve (Abbott curve) 62 and frequency distribution 64 ) of an identical roughness measurement carried out on a surface section with the surface structure, more precisely on a DMC applied by means of a laser to the bearing seat surface of a thrust washer according to the invention. The measured contiguous surface section with the coding had an edge length of 5 mm, so that the measuring section with 4.8 mm length was completely within the surface section, around the reduced peak height R _pk (S) to determine the surface structure. The parameters of the roughness profile determined from the measurements DIN EN ISO 13565 (1,2) are given in Table 2 below. Table 2 Ra 2.79 μm March 24.67 μm rpk 7.99 μm rvk 6.84 μm Rk 5.71 μm Rmax 28.02 μm M r1 14.8% Mr2 82.5%

The determined reduced top height R _pk (S) is 7.99 μm and is thus more than 20 times higher than the determined value Rpk ( 0 ).

These measurements were carried out in a total of 18 example cases on surface sections with the surface structure in the form of a DMC coding and in 9 example cases on the unstructured surface. The results are compared in Tables 3 and 4. The respectively determined roughness parameters Ra, Rz, Rmax, R _k . R _pk and R _vk were averaged over the 9 and 18 measurements and then compared. Table 3 also contains information on the proportion that the structured surface section has over the entire measuring path. In order to prove the significance, Table 4 contains in each case the quotient of the averaged roughness parameters from the structured surface sections and the averaged roughness characteristics from the unstructured surfaces. Table 3 msg Ra March Rmax Rk rpk rvk Share of DMC at the measuring section No. (Microns) (Microns) (Microns) (Microns) (Microns) (Microns) structured surface section with DMC 1 2.46 20.66 25.93 5.33 6.83 6.13 100% 2 3.09 21.14 33.29 5.46 7.07 8.56 100% 3 3.22 23.17 34.08 5.78 6.91 10.44 100% 4 3.11 24,09 31.56 5.12 6.85 9.93 100% 5 1.65 14.02 17.71 4.14 4.31 3.66 100% 6 2.25 17.90 32.92 2.75 7.01 8.26 60% 7 1.46 15.57 27.54 1.62 4.73 4.93 50% 8th 3.20 22.86 32.87 6.10 7.05 10.19 100% 9 2.70 16.58 25.02 6.07 4.50 5.81 100% 10 2.88 23.52 34.37 5.74 7.07 7.99 100% 11 2.31 22,07 33.47 2.67 5.82 9.76 75% 12 0.63 7.39 16.18 1.22 3.41 1.86 30% 13 2.67 23,12 29.76 5.01 7.97 8.58 100% 14 2.75 20.78 34.35 5.47 5.89 8.09 100% 15 2.79 24.67 28,02 5.71 7.99 6.84 100% 16 2.17 16.97 21.91 4.09 5.99 6.61 100% 17 2.49 21.94 32.83 4.35 5.57 8.94 100% 18 0.81 8.60 16,52 1.30 3.31 2.36 40% Average 2.37 19.17 28.24 4.33 6.02 7.16 Std deviation 0.77 5.12 6.37 1.69 1.44 2.61 Std.- dev. / Mittelw. 33% 27% 23% 39% 24% 36% Table 4 msg Ra March Rmax Rk rpk rvk No. (Microns) (Microns) (Microns) (Microns) (Microns) (Microns) unstructured area without DMC 1 0.49 4.02 4.66 1.29 0.39 1.16 2 0.54 4.70 5.72 1.24 0.47 1.54 3 0.48 3.87 4.48 1.20 0.24 1.32 4 0.34 2.63 4.27 0.47 0.29 1.10 5 0.58 6.03 9.65 1.38 1.18 1.96 6 0.62 4.65 5.78 1.34 0.34 1.85 7 0.47 3.81 5.79 1.21 0.27 1.34 8th 0.37 3.07 4.69 0.72 0.17 1.09 9 0.42 3.07 3.97 0.65 0.18 1.34 Average 0.48 3.98 5.45 1.06 0.39 1.41 Std deviation 0.09 1.04 1.72 0.34 0.31 0.31 Std.- dev. / Mittelw. 19% 26% 32% 32% 79% 22% comparison Middle: with / without DMC 4.9 4.8 5.2 4.1 15.3 5.1

The results clearly show that the quotient R _pk (S) / R _pk (0) is significantly different from the quotients of the other roughness characteristics R _a . R _z . R _max . R _k , and R _vk takes off.

It also shows that R _pk (S) is not even very sensitive to a measuring section that extends beyond the surface section with the surface structure. Because not always had the measured contiguous surface section with the coding an edge length that was greater than the measuring section. The corresponding proportion occupied by the structured area section over the entire measuring section is given for each measurement in the right-hand column of Table 3. It turns out that its influence on R _pk (S) is within the range of other variations due to the irregularity of the code-dependent surface structure. A lower limit for the proportion of the structured surface section at the measuring section is nevertheless to be drawn at 30%.

LIST OF REFERENCE NUMBERS

10

plain bearing shell

12

base course

14

Bearing seat surface

16, 16 '

subarea

18

crest line

20

Surface section with surface structure

22, 22 '

angle range

24

center line

26

raised material

28

surrounding area

30

Frame, partial surface, surface section

32

measuring distance

34

measuring distance

40

Frame, partial surface, surface section

42

measuring distance

44

measuring distance

50

Roughness measuring

52

Material share curve (Abbott curve)

54

frequency distribution

60

Roughness measuring

62

Material share curve (Abbott curve)

64

frequency distribution

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102012024141 A1 [0005]
• DE 102009060352 [0020]

Cited non-patent literature

• DIN EN ISO 13565 [0013, 0015, 0045, 0047, 0050, 0052]
• DIN EN ISO 13565-1 [0013, 0014]
• DIN EN ISO 13565-2 [0013, 0014]
• Standard DIN EN ISO 13565 [0050]

Claims (13)

Radial or axial sliding bearing element (10) having a support layer (12) forming a bearing seat surface (14), characterized in that the bearing seat surface (14) has on at least one surface portion (20) a surface structure comprising a plurality of material ejections (28, 28). 41, 51) comprises the support layer (12) and differs from the structure of the bearing seat surface (14) outside the surface portion (20), the surface structure forming a machine-readable encoding. Radial or axial sliding bearing element (10) according to Claim 1 , characterized in that the bearing seat surface (14) outside the surface portion (20) has a roughness _{core profile} with a reduced peak _height R _pk (0), measured according to DIN EN ISO 13565 (1,2), and that the surface structure of the surface portion (20 ) has a reduced peak _height R _pk (S), measured according to DIN EN ISO 13565 (1,2), which is greater than 3.5 times the reduced peak _height R _pk (0) of the bearing seat surface (14) outside the surface portion ( 20). Radial or axial sliding bearing element (10) according to Claim 2 , characterized in that the reduced peak _height R _pk (S) is less than 200 microns, preferably less than 100 microns and more preferably less than 50 microns. Radial or axial sliding bearing element (10) according to one of Claims 2 or 3 , characterized in that the reduced peak _height R _pk (S) is greater than 8 times the reduced peak _height R _pk (0) of the bearing seat surface (14) outside the surface portion (20). Radial or axial sliding bearing element (10) according to one of Claims 2 to 4 , characterized in that the reduced peak _height R _pk (0) of the bearing seat surface (14) outside the surface portion (20) is less than 1.5 microns, preferably less than 1 micron. Radial or Axialgleitlagerelement (10) according to any one of the preceding claims, characterized in that the surface portion (20) occupies at least 0.8%, preferably at least 1.0%, of the bearing seat surface (14). Radial or Axialgleitlagerelement (10) according to any one of the preceding claims, characterized in that the surface portion (20) has at least 20, preferably at least 35, Materialaufwerfungen. Radial or Axialgleitlagerelement (10) according to any one of the preceding claims, characterized in that the surface portion (20) extends in the axial direction over a width of at least 15%, preferably at least 20%, of the width of the radial sliding bearing element (10). Radial sliding bearing element (10) according to one of the preceding claims, characterized in that the radial sliding bearing element (10) is a sliding bearing shell. Radial sliding bearing element (10) according to Claim 9 , characterized in that the surface portion (20) in an angular range of 5 ° to 65 °, measured from a partial surface (16) of the sliding bearing shell (10), is arranged. Radial sliding bearing element (10) according to Claim 10 , characterized in that the bearing seat surface (14) has at least two surface sections (20) with the surface structure, wherein a first surface section (20) in the angular range of 5 ° to 65 °, measured from a first partial surface, and a second surface section (20). in the angular range of 5 ° to 65 °, measured from one of the first partial surface, relative to the vertex of the sliding bearing shell, opposite second partial surface, is arranged. Radial or Axialgleitlagerelement (10) according to any one of the preceding claims, characterized in that the plurality of Materialaufwerfungen (28, 41, 51) by means of embossing tool, in particular by means of needle embossers, or by means of laser was generated. Radial or Axialgleitlagerelement (10) according to any one of the preceding claims, characterized in that the machine-readable coding comprises a DataMatrix code.

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