EP3362696A1

EP3362696A1 - Plain bearing assembly of a rotational element on a bearing bolt, in particular of a planetary gear on a planetary gear bolt of a planetary gearbox

Info

Publication number: EP3362696A1
Application number: EP16790516.5A
Authority: EP
Inventors: Michael Plogmann; Sebastian Pachner; Sven Claus; Markus Soyka
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2015-10-12
Filing date: 2016-10-12
Publication date: 2018-08-22
Also published as: CN108138838B; WO2017063650A1; US10253817B2; CN108138838A; DE102016219800A1; US20180306247A1

Abstract

The invention relates to a plain bearing assembly of a rotational element on a bearing bolt, said assembly comprising a bearing bolt (2), a bearing sleeve (4), which is non-rotatably mounted on said bolt and which comprises a first radial bearing surface (5) formed on its outer periphery, a rotational element (3) which is rotatably mounted on the bearing sleeve (4) and which is slidingly mounted on the first radial bearing surface (5) by means of a second radial bearing surface (6). Axial bearing washers (9), which project radially beyond the bearing sleeve (4), are secured to both end faces (10) of the rotational elements (3), the washers running against axial bearing surfaces of the bearing sleeve (4), and axial flanks of the bearing sleeve (4) form axial bearing surfaces (8) for the axial bearing washers (9).

Description

Sliding bearing arrangement of a rotary member on a bearing pin, in particular a planetary gear on a Planetenradbolzen a planetary gear

The invention relates to a sliding bearing arrangement of a rotary element on a bearing element, comprising a bearing element, a rotatably mounted on this bearing sleeve having a formed on the outer circumference first radial tread, and a rotatably mounted on the bearing sleeve rotary element, the che on a second radial Laufflä- on the first radial Tread is slidably mounted.

Sliding bearings based on slide bearings are used in a wide variety of applications. Common to them is always the sliding bearing of a rotary element, for. As a gear, on a bearing element, usually in the form of a bearing pin. An example of this is the mounting of a planetary gear on a Planetenradbolzen a planetary gear. Planetary gear units are used in a wide variety of applications. Increasingly, very large-sized planetary gear are built, for example, for use in wind turbines. In particular, in such large transmissions of the longevity of the transmission is of central importance, since a simple replacement of transmission components is not readily possible.

In a known slide bearing of a planetary gear on a bearing pin, which is arranged on a planet carrier, a Radalla- gerhülse is fixed by form and / or adhesion on the bearing pin. This bearing sleeve represents the first radial tread on which the planet gear is slidably mounted via a second radial tread. At least the radial bearing sleeve can be provided on the outer circumference with a wear protection layer. Axiallagerung of axially slightly movable planetary gear usually two Axiallagerscheiben are provided as separate components, which are usually on their forehead side also wear a wear protection layer. The thrust washers are firmly connected to the planet carrier, for example via screw. The planetary gear runs with its end faces against the thrust washers. The production of such, usually application-specific or user-specific Planetenradträgers is highly complex and very expensive. The integration of a plain bearing solution of the form described requires a geometric modification to the planet carrier in order to integrate the thrust bearing in the area of the abutment shoulders, which is structurally difficult to implement, especially with regard to the screwing of the thrust washers for fixing the same.

The invention is therefore based on the problem to provide a sliding bearing assembly, which is improved in contrast and can be used without modification of an environmental structure.

To solve this problem is provided according to the invention in a sliding bearing arrangement of the type mentioned in a first alternative solution that are fixed to both faces of the rotary member radially to the bearing sleeve projecting thrust washers, which run against axial running surfaces of the bearing sleeve, wherein axial flanks of the bearing sleeve, the axial treads for form the thrust washers.

According to the invention, the thrust bearing disks are arranged on the rotating element itself, ie, for example, the planetary gear and not, as is usually customary, on a surrounding construction or the bearing bolt itself. The axial bearing disks project radially towards the bearing sleeve, against which they engage with their inner bearing surfaces Start axial running surfaces. To form these axial running surfaces serve the axial edges of the bearing sleeve. The bearing sleeve can be made quasi cylindrical, so that flat end faces that form the axial flanks arise. Alternatively, the bearing sleeve can also run stepped, that is, on both sides of the sleeve circumferential steps are formed, the axial Flanks form the two axial treads. The two Axiallagerscheiben run with their inner disc surfaces against the axial edges of the bearing sleeve.

Due to the integration of the axial bearing disks directly on the rotary element, for example the planetary gear, and the formation of the axial bearing directly to the bearing sleeve itself, there are no modifications to the surrounding structure or the bearing element, e.g. Required for the bearing pin. Rather, the axial and radial bearing takes place exclusively between the rotary member and the bearing sleeve, wherein the bearing sleeve plays a dual role here, namely the radial bearing and the axial bearing. This has the advantage that the manufacturing tolerances (roughness,

Shape) can be implemented much better in the context of production, compared with the previous embodiments in which cooperate to form the radial and axial bearing a plurality of components. Since the rotary element, that is, for example, the planet gear, is no longer the mating partner for the thrust bearing, no special processing steps of the end faces of the rotary member and the like are required. Also, the radial space can be used very well due to the arrangement of Axiallagerscheiben directly on the rotating element, since there is a sufficient wall thickness to attach the thrust washers, for example by screwing, compared with a well-known from the prior art attachment of the thrust washers then sufficiently strong to be sized radial bearing sleeve. The assembly of the slide bearing assembly is much easier, since the thrust washers can be preassembled together with the radial bearing disk, so can be attached to the rotary member, after which the arrangement can be mounted as a preassembled unit on the bearing pin.

As an alternative to supporting the rotary element on a bearing element such as a bearing bolt, it is basically also conceivable to mount the rotary element, eg in the form of a shaft, in a bearing element, for example in a bearing bore of a housing. According to a second alternative of the invention, a sliding bearing arrangement of a rotary element can be provided in a bearing element for this purpose, comprising a bearing element, a rotatably arranged in this bearing sleeve having a formed on the inner circumference first radial tread, and rotatably mounted in the bearing sleeve rotary member which is slidably mounted on a second radial tread on the first radial tread, said slide bearing characterized in that the rotary member radially to the bearing sleeve projecting thrust washers are mounted, which run against axial bearing surfaces of the bearing sleeve, wherein axial edges of the bearing sleeve form the axial bearing surfaces for the thrust washers. Here are the thrust washers on the inner rotary element, so for example set the shaft and fixed it. They act in the same way as above for the first invention alternative with the outer, for example, arranged in the bearing bore of the housing part bearing sleeve together, so run axially against the axial edges. Again, the bearing sleeve can be made quasi cylindrical, so that flat end faces that form the axial edges result. Alternatively, the bearing sleeve can also be stepped here, that is, circumferential steps are formed on both sides of the sleeve, the axial flanks of which form the two axial running surfaces.

According to a particularly advantageous embodiment of the invention can be provided that the radial and axial running surfaces of the bearing sleeve with a sliding coating or a wear protection coating is formed. The fact that the bearing sleeve is a multifunctional component, which offers both the radial bearing and the axial bearing, it is particularly advantageous to provide only on the bearing sleeve, a sliding or wear protection coating over which the corresponding sleeve-side treads are formed. This is a major simplification to the prior art, where different components must be processed and coated accordingly. As such a wear protection coating, in particular hard coating, for example, a carbon layer, often called DLC layer (DLC = diamond like carbon), can be used. If appropriate, it can also be doped metallically, in which case it is then a so-called MeDLC layer, with tungsten carbide (WC) in particular being used as doping. Furthermore, a ceramic layer or a ceramic-like layer (nitride-ceramic, oxide-ceramic or carbide-ceramic, eg silicon nitride, silicon carbide or nitrides or carbenes) may be used as the hard material layer. Bide be used by metals such as titanium, chromium or their mixed phases. Also combination layers of carbon and ceramic layers are conceivable.

The hard material layer should have a Vickers hardness HV of at least 800 HV, preferably the Vickers hardness should be at least 1500 HV. It is preferably harder than the second radial tread, which is formed on the inner circumference of the rotary member and the Axiallagescheiben, which in turn should have a hardness of not more than 800 HV. The first radial running surface, that is to say the hard material layer, preferably has at least twice to three times the hardness of the running surface of the rotating element. It is also conceivable to provide the second radial tread additionally with an inlet layer. This could be, for example, a burnishing layer, a phosphate layer and / or a plastic-based sliding layer / bonded coating.

The bearing sleeve-side hard material layer is preferably applied to a bearing sleeve substrate having an edge hardness of at least 50 HRC. The thickness of the hard material layer is preferably less than 20 μιτι, preferably it is in the range between 1 - 10 μιτι and in particular in the range between 2.5 - 4 μιτι. Particularly suitable has a hard diamond-like coating, as it is known under the trademark "Triondur®" from the house of the applicant, for example, "Triondur® CX +".

In order to form the sliding bearing assembly as compact as possible axially seen, provides an expedient development of the invention, that the rotary member is stepped formed on its front side, wherein the thrust washers are inserted into the stage. This offers the possibility for an axially compact construction, wherein the steps provided on the rotary element can be designed so that the outer surfaces of the axial bearing plates are flush with the end faces of the rotary element. The bearing sleeve is dimensioned accordingly, so it can also be made correspondingly shorter, since, of course, due to the integration of Axiallagerscheiben in the end faces of the rotary member, the sleeve side provided axial running surfaces are also arranged correspondingly closer to each other. As an alternative to the stepped construction of the rotary element, it may be provided that a receiving groove is provided on the rotary element, wherein the axial bearing washers are inserted into the receiving grooves with a circumferential axial projection. In this alternative, axial space can also be saved, since the thrust bearing discs can be designed slightly narrower overall, because as a result of the circumferential axial projection they are dimensioned sufficiently strong for a fixed screw in this area. The rotational element is not reduced in the tread area in the front side in its width, so that the hydrodynamically effective width is still large for a good radial bearing.

In the embodiments described above, the rotary element itself has the second radial running surface, it is therefore mounted with its inner circumference on the first radial running surface of the bearing sleeve, or vice versa in the context of the second alternative with its outer circumference on the inner running surface of the outer bearing sleeve , According to an alternative embodiment, the axial bearing disks can also be used to form the second radial running surface of the rotary element. To make this possible, as further provided according to the invention, the thrust washers in cross-section T-shaped with a longitudinal and a transverse leg be formed, the two longitudinal legs are formed via hollow cylindrical Axialflan- see, for example, in the first alternative on the inner circumference of the rotary member are arranged and with its inner periphery, forming the second radial tread, slide on the bearing sleeve. The thrust washers thus have a double function here. On the one hand, they serve of course the axial bearing, on the other hand, the radial bearing by quasi lining the rotary element on the inner circumference and form with their hollow cylindrical axial flanges respectively the inner periphery of the rotating element side tread. They may abut each other with their axial flanges or be slightly spaced so as to form a circumferential annular groove which may serve as a lubricant reservoir. This embodiment of the axial bearing washers can be provided both with a direct attachment of the discs on the flat faces of the rotary member, but also with the arrangement of the thrust washers, then with the transverse leg, in corresponding end-side stepped recesses of the rotary member, or provided with a transverse leg Henen circumferential axial projection which is inserted into a rotary element-side receiving groove. Again, no sliding or wear protection coating on the axial bearing washers is required in this case, but it is sufficient here, if only the bearing sleeve is coated with their radial and axial treads. The same applies to the second alternative with internal rotary element and external fixed bearing element.

As already described, the axial bearing disks are preferably fixed to the rotary element via fastening screws, which applies to all different configurations of the axial bearing disks. Alternatively, a frictional connection (interference fit) and material closure (gluing, soldering, welding) for connection is also conceivable.

In order to enable lubrication of the plain bearing area, the invention may be provided in a development that the bearing element is designed in the form of a bearing pin, which has at least one opening on the outside of the bolt lubricant channel, and that the bearing sleeve formed on the inner circumference, communicating with the radial lubricant channel Radialnut and at least one radially branching from this, open to the rotary member opening, which merges into a formed on the outer circumference radial groove. This channel and groove configuration makes it possible to bring lubricant through the bearing pin into the plain bearing area. The fed to a longitudinal bore of the bearing pin

Lubricant, usually an oil, passes via the bolt-side radial bore into the radial groove formed on the inner circumference of the bearing sleeve, where the lubricant is distributed. This radial groove also serves as a lubricant reservoir. From this radial groove branches off from at least one opening, which opens at the outer periphery of the bearing sleeve, wherein preferably a plurality of such apertures are provided distributed circumferentially. Over this the lubricant gets into the direct plain bearing area. In order to be able to distribute the lubricant in the plain bearing area, the opening preferably opens in an outer circumferential groove. This circumferential groove also serves as a lubricant reservoir. For axial distribution, at least one axial groove may be provided into which the lubricant passes from the circumferential groove. Furthermore, a circumferential annular groove may be provided on the inner periphery of the rotary member or between the two axial contiguous axial flanges, which communicates with the open aperture of the bearing sleeve. This annular groove is thus also supplied with lubricant, it likewise forms a circulating lubricant reservoir, so that overall a considerably large volume of lubricant absorption results via the perforation or bore and groove structure.

These embodiments of the channel and groove geometries for lubricant supply described above relate to the first alternative of the invention. In the second alternative of the invention, the lubricant could be supplied via the internal rotary element, or via the external bearing element, e.g. the housing, etc. In both cases, appropriate channels or annular and axial grooves are provided on the relevant components in order to allow a lubricant flow.

Axial bearing washers are also of particular importance in connection with the lubrication of the sliding bearing. Because due to the fact that they extend radially to the bearing sleeve and open only a short distance to the radial step edges or the rotary member or arranged on spacers, they serve as a lubricant retaining discs at the same time. Because they prevent to some extent drainage of the lubricant from the storage area. This in particular, when the planetary gear rotates, because then the given centrifugal force and gravity hinders the outflow of the lubricant from the radial and Axialgleitla- gerbereiche and the lubricant is inevitably held in large part in the storage area.

In order to further improve the lubrication in the axial bearing region, it is expedient if at least one radial groove opens out at each of the axial running surfaces of the bearing sleeve. These radial grooves are also filled with lubricant, they have a similar function as the axial groove in the radial bearing area. The grooves are preferably arranged offset to the load zone of the thrust bearing, wherein the interpretation of concrete positions for the applied loads is selected depending on the application or situation. It is useful if the lubricant is supplied just before the convergent gap, so that then the lubricant is present in the contact area. The lubricant must always flow through the radial bearing area before it is discharged via the axial bearings so that the lubricant flow is optimally utilized.

As described, the circumferential grooves, etc. serve on the bearing sleeve and optionally on the rotary element as a contact-near lubricant reservoir. In any rotational position, even after a standstill, they will contain a residual lubricant volume so that the lubricant can be kept close to the sliding contact even in "coldclimate" conditions.The lubricant warms up during operation and then to the bearing with its different Delivered areas so that even in such a case lubrication is ensured, as well as a sufficient residual lubricant volume is given in Gleitkontaktnähe.

As described, the rotary element itself is preferably a planetary gear, which is part of a planetary gear. The invention will be explained below with reference to embodiments with reference to the drawings. The drawings are schematized representations and show:

Figure 1 is a schematic representation of a sliding bearing assembly according to the invention in section

FIG. 2 shows a representation corresponding to FIG. 1 with a sectional plane which lies in the region of the bore and groove configuration serving for the lubricant supply,

Figure 3 is an end view of the agerhülse showing the radial groove on the axial edge 4 shows a Phnzipdarstellung a second embodiment of a slide bearing assembly according to the invention, and Figure 5 is a schematic diagram of a third embodiment of a slide bearing assembly according to the invention.

In the figures, a sliding bearing assembly of a Planetenradgetrie- bes is described by way of example, comprising a planetary gear (= rotating element) and a planetary wheel (= bearing pin), the planetary gear is mounted on a bearing on the Planetenradbolzen bearing sleeve. The Planetenradbolzen in turn is arranged on a planet carrier.

Figure 1 shows in the form of a partial view of a section of a Planetenradgetrie- be comprising a sliding bearing assembly according to the invention. On a planet carrier 1, a bearing pin forming a Planetenradbolzen 2 is arranged, which serves as a bearing axis for a rotary element forming a planetary gear 3. On the Planetenradbolzen 2, a bearing sleeve 4 is set, which is rotatably connected to the Planetenradbolzen 2. The bearing sleeve 4, for example, be positively, positively or materially secured to the Planetenradbolzen 2.

For this purpose, it has a first radial running surface 5, which is provided with a sliding or wear protection coating or which is formed over this slip or wear protection coating. Preferably, a wear-resistant hard material coating is provided for this purpose.

The bearing sleeve 4 is used in addition to the radial bearing and the axial bearing. For this purpose, it is provided on both sides in each case with a step 7 which rotates and whose axial flanks form the respective axial running surfaces 8 for the axial bearing of the planetary gear 3. These axial flanks are also covered with the corresponding hard material coating. The axial flanks or running surfaces 8 serve as contact surfaces for thrust washers 9, which are arranged according to the invention on the planetary gear 3 at the end faces 10. For this purpose, two stages 11 are formed on the planetary gear 3, into which the two axial bearing discs 9 are inserted. The steps 1 1 are dimensioned such that the outer surfaces of the axial bearing washers 9 are flush with the end faces 10 of the planetary gear 3. The thrust washers 9 are fastened via fastening screws 12, which are screwed into corresponding threaded bores on the planetary gear 3. Alternatively, a friction or material connection is conceivable.

As FIG. 1 clearly shows, the axial bearing disks 9 jump radially inward and engage in the steps 7 of the bearing sleeve 4. Their inner surfaces 13 are parallel to the axial edges of the bearing sleeve 4, they run against the axial treads 8 formed thereon. Over this, the axial bearing of the planetary gear 3 takes place on the Planetenradbolzen. 2

Obviously, the bearing sleeve 4 has a dual function, namely on the one hand as a radial bearing component, on the other hand as a thrust bearing component. Only the bearing sleeve 4 is to occupy with the hard material layer, so only a single component, which is technically very advantageous manufacturing, since all three functional surfaces, namely the radial and the two axial treads are protected against wear and the corresponding treads are formed. Also, a simple assembly is given, since the bearing sleeve 4 can be pre-assembled with the planetary gear 3 and the thrust washers 9 and then the entire construct can be placed on the Planetenradbolzen 2.

To provide the sliding bearing area with lubricant, a central channel 14 is provided on Planetenradbolzen 2, of which a radial bore, the one

Lubricant channel 15 forms, runs to the bolt outside. On the inner circumference of the bearing sleeve 4, a circumferential radial groove 16 is formed, depart from the at least one, preferably more to the planetary gear 3 running holes or openings 17, which open on the outside of the bearing sleeve 4. Further communicates with the one or more openings 17 a circumferential radial groove 20 formed on the inner wall of the planetary gear 3. With this radial groove 20 communicate respective axial grooves 19 through which the lubricant is distributed in width. The lubricant is supplied via the central channel 14 and the lubricant channel 15. It is distributed in the first lubricant reservoir forming radial groove 16. About the one or more openings 17 it passes into the circumferential on the outside of the bearing sleeve circumferential groove 18, which is optional and can serve as a second lubricant reservoir. From the openings 17 and the optional radial grooves 18, the axial grooves 19 are fed. The third lubricant reservoir is the radial groove 20 on the planetary gear wheel 3. In this way, sufficient lubricant supply is provided. The lubricant is also very well maintained in the sliding area, as a direct outflow into the transmission via the radially inwardly extending thrust washers 9 is prevented. Due to the weight force, the entire lubricating oil can never run out of the radial / thrust bearing and a large part is held in the bearing. In addition, the centrifugal force is the

Lubricant anyway urged radially outward, so that it collects mainly in the region of the grooves.

In order to carry out a lubrication of the axial bearing areas, 4 radial grooves 21 are provided on the axial running surfaces 8 of the bearing sleeve, as shown in Fig. 3. These are preferably arranged in front of the actual load zone of the thrust bearing areas, so that the lubricant is supplied just before the convergent gap, whereby the direct sliding contact is lubricated. Figure 4 shows a second embodiment of a sliding bearing assembly 1 according to the invention, wherein the same reference numerals are used for the same components. Shown here is the planetary gear 3 and the bearing sleeve 4 and the two Axiallagerscheiben 9. Again, only the bearing sleeve 4 is provided on its outer surfaces with the wear protection layer, such as the hard material layer.

For attachment of the thrust washers 9, the planet gear on both end faces 10 receiving grooves 22, in each of which a circumferential axial projection 23, so a Type axial flange, engages. By this axial projection 23, the fastening screws are guided and screwed in the planetary gear 3. Alternatively, a friction or material connection is conceivable. From the axial projections 23 radially inward then extend the remaining portions of the thrust washers 9, which run parallel along the end faces 10 of the planetary gear 3 in the steps 7 on the bearing sleeve 4. With their inner surfaces 13 they also slide here on the axial treads 8, about which the axial bearing is given.

In this embodiment, on the one hand a secure attachment can be achieved by the relatively wide-dimensioned axial projection 23. However, this axial projection 23 also allows the formation of a press fit or a solder joint. On the other hand, the planetary gear 3 is not reduced in its width, since no step is formed here, so that an uninfluenced hydrodynamically effective width is given in the radial sliding region. Nevertheless, here too results in a compact construction, whereby also here the bearing sleeve 4 multifunctional provides both the radial and the axial bearing. The statements relating to the manner of lubricant supply apply identically also with respect to the embodiment according to FIG. 3.

Finally, FIG. 5 shows an embodiment of a further embodiment of the plain bearing arrangement, again using the same reference numerals for the same components. Shown is the planetary gear 3 and the bearing sleeve 4, which in turn has corresponding stages 7 and formed thereon axial treads 8. By way of example, two differently deep steps are shown, by which it should be shown that the step depth can ultimately be dimensioned arbitrarily. Again, only the bearing sleeve 4 is provided with the sliding or wear protection coating. The thrust washers 9 are here executed in cross-section T-shaped, they each have the actual, the axial bearing serving transverse leg 24 and an axially projecting from this longitudinal leg 25 which is formed via a corresponding, hollow cylindrical axial flange 26. With these two axial flanges 26, the thrust washers 9 engage in the inner circumference of the planetary gear 3. The inner circumferences of the Axialflansche 26 form in this embodiment, the second radial tread 27, so the tread on the side of the rotary member, ie here the planet 3. That is, the planetary gear 3 via these axial flanges 26 fixed to the planetary gear 3 via the screw connection of the axial bearing washers 9 are connected in the end faces 10 of the planetary gear 3, supported radially. The Axiallagerscheiben 9 so here is a double function, namely on the one hand, the pure axial bearing, on the other hand, the radial bearing.

As can be seen, the axial flanges 26 do not abut each other directly, but rather a narrow annular gap, that is to say an annular groove, which in turn serves as a lubricant collecting space, remains. Here, therefore, the planetary gear 3 is not stored directly on the bearing sleeve 4, but on the Axialflansche 26. Again, the comments apply to the

Lubricant supply via the corresponding bore and groove configurations, as described for Figures 1 and 2, alike.

Although not shown in detail, according to the second basic alternative of the invention, the rotary element or the like in a bearing bore of a bearing housing. be stored. The bearing sleeve would then be arranged in the bearing bore. The basic explanations above also apply with respect to such a quasi-inverted arrangement of rotary element and bearing element. List of Reference Planetary Carriers

pinion pin

planet

bearing sleeve

radial tread

step

axial tread

axial bearing

front

step

fixing screw

area

channel

lubricant channel

radial groove

perforation

circumferential groove

axial groove

radial groove

receiving groove

axial projection

transverse leg

longitudinal leg

axial flange

tread

Claims

claims

Sliding bearing arrangement of a rotary element on a bearing element, comprising a bearing element (2), a rotatably mounted on this bearing sleeve (4) with a formed on the outer circumference first radial tread (5), and on the bearing sleeve (4) rotatably mounted rotary member (3) via a second radial tread (6) on the first radial tread (5) is slidably mounted, characterized in that on both end faces (10) of the rotary member (3) radially to the bearing sleeve (4) projecting Axiallagerscheiben (9) are fixed against axial running surfaces of the bearing sleeve (4) start, wherein axial flanks of the bearing sleeve (4) form the axial running surfaces (8) for the Axiallagerscheiben (9).

Sliding bearing arrangement of a rotary element in a bearing element, comprising a bearing element, a rotatably mounted in this bearing sleeve (4) having a formed on the inner circumference first radial tread (5), and in the bearing sleeve (4) rotatably mounted rotary member (3) via a second Radial bearing surface (6) on the first radial bearing surface (5) is slidably mounted, characterized in that on the rotary member (3) radially to the bearing sleeve (4) projecting Axiallagerscheiben (9) are fixed, which run against axial running surfaces of the bearing sleeve (4), wherein axial flanks of the bearing sleeve (4) form the axial running surfaces (8) for the thrust washers (9).

Slide bearing assembly according to claim 1 or 2, characterized in that the radial and axial running surfaces (5, 8) of the bearing sleeve (4) is formed with a sliding or wear protection coating.

4. Sliding bearing arrangement according to claim 3, characterized in that the radial and axial running surfaces (5, 8) of the bearing sleeve (4) is formed by means of a hard material coating.

5. plain bearing arrangement according to one of the preceding claims, characterized in that the rotary element (3) at its end faces (10) stepped (1 1) is formed or provided with a receiving groove (22), wherein the thrust washers (9) in the stages ( 1 1) or inserted with a circumferential axial projection (23) in the receiving grooves (22).

6. plain bearing arrangement according to one of the preceding claims, characterized in that the axial bearing discs (9) in cross-section T-shaped with a longitudinal and a transverse leg (24, 25) are formed, wherein the two longitudinal limbs (25) via hollow cylindrical axial flanges (26 ) are formed, which are arranged on the inner circumference of the rotary member (3) and with its inner periphery, forming the second radial tread, slide on the bearing sleeve (4).

7. Sliding bearing arrangement according to one of the preceding claims, characterized in that the axial bearing discs (9) via fastening screws (12) or by friction or material connection are attached to the rotary member.

8. plain bearing assembly according to claim 1 and one of claims 3 to 7, characterized in that the bearing element is a bearing pin (2) having at least one opening on the outside of the bolt lubricant channel (15), and that the bearing sleeve formed on the inner circumference, with radial groove (16) communicating with the radial lubricant channel (15) and at least one aperture (17) which branches off radially from the latter and has a circumferential groove (18) formed on the outer circumference, with or without at least one axial groove (17). 19) communicates.

9. plain bearing assembly according to claim 8, characterized in that on the inner circumference of the rotary member (3) or between the two axially adjoining Axialflanschen (26) is provided a circumferential annular groove (20) with the open aperture (17) or the axial groove ( 19) of the bearing sleeve (4) communicates. Slide bearing arrangement according to one of the preceding claims, characterized in that at least one radial groove (21) is provided on the axial running surfaces (8) of the bearing sleeve (4).