DE102007044250A1 - Slide bearing shell, use of plain bearing shell, method for their preparation and bearing arrangement - Google Patents

Abstract

It is a plain bearing shell (10) for supporting a rotating counter-rotor (10) with a at least partially over the inner circumference extending lubricant channel (20) and arranged with at least one on the inner circumference, the bearing gap S between the sliding bearing shell (10) and the counter-rotor (1 ) closing guide member (30) for the lubricant (28). The guide element (30) is arranged in the lubricant channel (20) and has at least two contact surfaces for engagement with the counter-rotor. A method for producing such a slide bearing shell as well as a bearing arrangement is also described.

Description

The The invention relates to a plain bearing shell with at least one partially over the inner circumference extending lubricant channel according to the preamble of claim 1.

The The invention also relates to a particular use of a Such bearing shell and a method for the preparation of Plain bearing shells and on a bearing assembly.

Under A lubricant channel becomes an area in the plain bearing shell understood in which the lubricant, in particular lubricating oil, can flow. In particular, under a lubricant channel a lubricant groove understood.

such Plain bearing shells are well known and are mainly used in Internal combustion engines used to support the crankshaft. The Main bearings are made with channels of lubricant, lubricating oil supplied, the oil over an oil groove in the plain bearing cup over the main pin the connecting rod journal and thus the connecting rod is supplied. It has been found that only a maximum of 25% of the oil on the Connecting rod bearing arrives. This is due to, that the oil losses mainly in the axial direction relative to the main bearing shell, d. H. perpendicular to the groove direction, are very big.

The oil drain becomes with increasing play between the plain bearing shell and the Opposites, such as waves or cones, favored. To constantly ensure adequate lubrication are correspondingly large oil pumps for promotion a sufficiently large amount of oil required. A shortage and thus a demolition of the oil film in the Bearings and the insufficient supply of the connecting rod with oil would cause a quick wear or scuffing the sliding partner and lead to premature failure of the bearing.

To remedy this, be in the DE 10 2004 028 773 A1 Expander proposed, which are arranged either between the bearing housing and the plain bearing shell or between plain bearing shell and shaft. It is according to the DE 10 2004 028 773 A1 have been recognized that Spaltentstehungsprozesse can be compensated by expansion elements. In particular, it has been recognized that it is possible to dispense with the use of heavy metals, which have to be optimized in a particularly complex manner with respect to their thermal expansion coefficient. There are proposed expansion elements, which may be made of lightweight materials to compensate for expansion processes of the components.

When Elongation elements are proposed such that a larger Have coefficients of thermal expansion as the materials, from which the bearing element and the shaft to be supported or the bearing shell are made.

So far arranged the expansion elements in the sliding surface of the bearing shell are, they are located on the bearing shell edge and thus spaced to the lubricant groove. This embodiment has the disadvantage that in the bearing shell additional grooves for insertion the Dehnstreifen are required, which is the preparation of the bearing shell expensive.

There the expansion elements have a high thermal expansion coefficient can, with a small gap between the bearing shell and shaft under Circumstances at high temperatures due to the expansion elements a clamping pressure are built up, which impedes the rotation of the shaft, or increases the wear of the expansion elements, whereby they lose their effect.

It is therefore an object of the invention to provide a plain bearing shell, the no or only slight lubricant losses during operation allows and which is simple and inexpensive to be finished.

These Task is solved with a plain bearing shell, which thereby characterized in that the guide element in the lubricant channel is arranged and at least two contact surfaces to the plant having on the counter-rotor.

The Arrangement of the guide element in the lubricant channel has the advantage that the lubricant channel for receiving the guide element is used, eliminating extra measures outside the lubricant channel for mounting the guide elements can be saved.

The Both contact surfaces are preferably in the axial direction the bearing shell spaced from each other. As a result of that the guide element at least two contact surfaces has only one guiding element for the Double-sided sealing required. The assembly of the guide element is simplified.

The guide element is configured such that the contact surfaces are preferably located in each case in the edge region of the lubricant channel, wherein in the intermediate region in the guide element, a second lubricant channel is formed. In the second lubricant channel, the lubricant is guided, whereby an axial outflow and thus lubricant losses are prevented or at least minimized. Due to the design of the Führungsele ment can also be a controlled lubricant drain for lubrication of the sliding surfaces are set next to the lubricant channel.

The Guide element can be in the circumferential direction only over extend over a portion of the lubricant channel or over the entire length of the lubricant channel.

It can also have at least two guide elements in Circumferentially arranged one behind the other in the lubricant channel be.

Preferably the guide element dresses at least one longitudinal section of the lubricant channel. The lining of the lubricant channel means that the guide element the bottom and the side edges, at a lubricant groove the groove bottom and the groove edges, at least partially covered.

Preferably the guide element consists of a strip-shaped Element that is inserted into the lubricant channel. Especially preferred is a strip-shaped element with U-profile, the a bottom portion and two upstanding from the bottom portion leg having. In this embodiment are the Contact surfaces at the free end of the legs.

In order to the guide element the bearing gap S between the plain bearing shell and the counter runner are two Embodiments preferred.

According to one first embodiment is the guide element movably arranged in the lubricant channel. This means that the guide element, for example, inserted in the channel is and can move in the radial direction. In operation becomes the guide element of the lubricant, in particular the Lubricating oil, rinsed and lifted out of the channel, so that the contact surfaces of the guide element abut the counter-rotor.

The pressing against the counter rotor is effected by the pressure difference of the lubricating oil in the first and in the second lubricant channel. The pressure P ₁ in the first lubricant channel and thus below the guide element is greater than / equal to the pressure P ₂ in the second lubricant channel. The pressure ratios P ₁ to P ₂ can be influenced by the design of the guide element, so that a controlled outflow of the lubricant for the own lubrication of the bearing shell can be adjusted.

Preferably is the guide element elastic, in particular bendable, so that it can adapt to the opposite of the whole Can create length and unfold the required sealing effect can.

According to one second embodiment is the guide element set in the lubricant channel. The guide element For example, it can be clamped or snapped into the channel. So that the guide element with the contact surfaces can invest in the counter-rotor and close the bearing gap can, at least one spring device is preferably provided. The spring device is preferably in the area below the respective Contact surface provided.

The Spring device preferably acts in the radial direction to the Close bearing gap. About the spring force of Spring device, the contact pressure to the counter-rotor and thus also the permissible discharge quantity of the lubricant be set.

The Spring device can also -. B. a clamping action in the lubricant groove - in the axial direction be effective. Preferably, both types of spring devices realized in a guide element.

at a U-shaped profile, the spring means are preferably on or in the bottom section and / or on or in at least one leg intended.

The Spring device, for example, a V-shaped section include.

Further Embodiments of the spring device include a bent Thighs or resilient heels or lugs, projections or formations on the thighs.

The Leg height H of the legs of the U-shaped profile is preferably ≤ the groove depth T. This is especially true when no spring device is provided on the legs. If the legs are equipped with spring devices is the leg height H is greater than the groove depth T. The spring device is yielding, so that in the radial direction constantly the optimal adaptation to the counter-runner is guaranteed.

If the guide element fixed in the lubricant channel is arranged, it is necessary that the leg height H is greater than the channel depth T, with the leg height to adjust via the spring devices.

The guide element prevents leakage of the lubricant in the axial direction. In order to supply the areas laterally of the guide element, ie the sliding surface of the sliding bearing shell with a metered amount of lubricant is in each Leg, in particular of the U-profile, at least one hole or an edge recess, z. B. in the form of a notch provided. Through these holes or edge recesses, the lubricant can escape specifically in the axial direction and enters the area between the sliding surface of the plain bearing shell and the counter rotor and provides there adequate lubrication available. This controlled drainage of the lubricant can also be used to specifically set the pressure P ₂ and thus the pressure difference between P ₁ and P ₂ .

Around a displacement of the guide element in the lubricant channel to prevent in the circumferential direction, is preferably a holding element intended. Since the lubricant channel usually over at least a lubricant hole for the supply and removal of lubricant has, the guide element is preferably arranged in the region of the lubricant hole.

The Retaining element is preferably engaging in the lubricant hole arranged on the guide element tab. Preferably at least two holding elements provided on the guide element, in particular during transport and installation of the plain bearing shells to guarantee a firm hold of the guide element.

According to a further embodiment, the sliding bearing shell may be formed from two shell-shaped sections, which are spaced from each other. Between the sections, the lubricant channel is formed, in which the guide element is arranged. These are plain bearing shells, such as those from the DE 10 2005 030 307 A1 are known.

A Another embodiment provides that the bearing shell has at least one slot in the circumferential direction, which is the lubricant channel forms and in which the guide element is inserted. Of the Lubricant channel extends over the entire wall thickness the sliding bearing shell.

Preferably has the plain bearing shell in the circumferential direction at least two slots on, in which the guide elements are inserted. Between two slots is a bridge available, preferably in the apex area of the plain bearing shell, reducing the stability the sliding bearing shell is increased.

Between the two slots can in this connection area a connecting groove may be provided so that a continuous lubricant groove is created.

Preferably takes the thickness of the bottom section of the U-shaped profile Guide element in the direction of at least one partial surface the sliding bearing shell too. The bottom section may be at the partial surface reach the level of the sliding surface. The high of Legs of the U-profile loops are reduced in this area corresponding. This prevents leakage in the end area and at the same time a large support surface created, so that the guide element in the lubricant channel not can move.

Preferably the guide elements consist of copper, aluminum, steel, Steel alloy or plastic, wherein z. B. copper strips, aluminum strips or steel strips are preferred.

When Plastic is especially suitable for PTFE. Made of plastic can be particularly simple extruded profiles z. B. by extrusion, which are cut to length according to the channel or groove lengths become. Guide elements made of thermoplastic materials based on POM (polyoxymethylene), PA (polyamide), PVDF (polyvinylidene fluoride), PPS (polyphenylene sulfide) or PEEK (polyether ether ketone) optionally with additives can be fast, accurate and cheap z. B. also be produced by injection molding.

The Sliding bearing shell according to the invention is suitable in particular as a main bearing shell in internal combustion engines. With the Sliding bearing shell according to the invention are the oil losses significantly reduced in the main bearing of internal combustion engines and the Supply of conrod bearings improved.

The Method for producing such a sliding bearing shell provides that a board is made that in the board at least a groove or a slot is introduced, that at least one guide element manufactured and inserted into the groove or slot and that the board together with the at least one inserted guide element is formed into a plain bearing shell.

It is thus not required, the guide element before the Replace insertion in the lubricant groove. This can be easy Way in one step with the transformation of the board in a plain bearing shell respectively.

A bearing arrangement with two plain bearing shells and a rotating counter-rotor mounted in the sliding bearing shells can have one or two such sliding bearing shells according to the invention. At least one sliding bearing shell has a lubricant channel and at least one guide element for the lubricant arranged on the inner circumference and closing the bearing gap S between the sliding bearing shell and the counter rotor. The bearing assembly is characterized in that the Guide element is arranged in the lubricant channel and has at least two contact surfaces for engagement with the counter-rotor.

exemplary Embodiments of the invention are described below explained in more detail in the drawings.

Show it

1a , b perspective views of a sliding bearing shell,

2 a bearing assembly with a plain bearing shell according to the 1b in cross section,

3 a bearing arrangement in cross-section according to a werteren embodiment,

4 a bearing assembly according to the 4 in section along the line IV-IV in 3 .

5 to 9b several embodiments of guide elements in section, partially inserted in a plain bearing shell,

10 and 11 two further embodiments of guide elements in perspective,

12 a section through a sliding bearing shell according to a further embodiment,

13 an enlarged sectional view of a plain bearing shell with lubricant hole and retaining element,

14 a plan view of a plain bearing shell with two slots,

15 a section through the in 14 shown plain bearing shell along the line XV-XV in 14 .

16 a plain bearing shell consisting of two shell-shaped sections in section and

17 a circuit board in top view.

In the 1 is a plain bearing shell 10 shown in perspective. The plain bearing shell 10 can be constructed of a solid material or of a composite material. The plain bearing shell 10 has a bearing back 16 and on the inner circumference a sliding surface 14 on. The bearing shell ends are divided by partial surfaces 12a . 12b educated. On the inner circumference is a lubricant channel 20 in the form of a lubricant groove 20 with groove bottom 22 and groove sides 24a , b provided. In the apex area is an oil hole 18 for the supply of lubricating oil in the lubricant channel 20 , Into the lubricant channel 20 is a guide element 30 used in the field of oil drilling 18 a lubricant opening 46 having. The guide element 30 consists of a strip-shaped element with a U-shaped profile. The strip has a bottom section 32 and two from the bottom section 32 towering thighs 34a , b (see also 2 )

In the 1b is another embodiment of a plain bearing shell 10 represented by the in 1a only differs in that instead of a single guide element 30 three guide elements 30 are arranged in the circumferential direction one behind the other.

In the 2 is a section through a plain bearing shell 10 together with a backlash 1 shown, which is a rotating shaft and in the case of a main bearing can be a rotating pin of a Kurbelweile.

The dimensions in the 2 as well as in the following figures are not to scale to better explain the peculiarities of the bearing shell can.

The lubricant groove 20 has a groove bottom 22 and right-angled groove flanks 24a . 24b , In the lubricant groove 20 there is a guide element 30 in the form of a U-shaped profile with a bottom section 32 and two towering thighs 34a , b, the contact surfaces at the top 40 exhibit.

The groove depth is T and the height of the guide element, ie the leg height is marked H. The leg height H is equal to the groove depth T, so that when installed, the contact surfaces 40 the thigh 34a , b with the sliding surface 14 the sliding bearing shell 10 aligned.

In operation, the guide element 30 with lubricating oil 28 undermined and by the oil pressure from the first lubricant channel 20 lifted. The bearing gap S, which is between the sliding surface 14 and the counter-runner 1 is achieved by lifting the guide element 30 closed. The guide element 30 is removed from the lubricant channel 20 lifted out until the contact surfaces arranged at the top 40 the thigh 34a , b on the counter-runner 1 issue.

The guide element 30 is constructed in one piece and thus can be easily in the lubricant channel 20 place. Between the two legs is a second lubricant channel 31 formed in which the lubricant is trapped and in the axial direction of the sliding bearing shell, which is the longitudinal axis of the counter-rotor 1 does not match can escape. It is guaranteed in this way an optimal seal.

In the 3 is another embodiment of a guide element 30 shown in section. The guide element 30 is in contrast to the guide element 30 of the 2 stationary in the lubricant channel 20 arranged. In order to close the bearing gap S in operation, have the two legs 34a , b spring devices 36 in the form of V-shaped sections. The spring devices 36 act in the radial direction and cause the contact surfaces 40 to the counter-runner 1 be pressed. Changes of the bearing gap S are caused by the spring devices 36 collected, so that an optimal seal is guaranteed. The arrows indicate the flexibility of the thighs 34a , b in the vertical direction.

In the 4 is a section along the line IV-IV through the in 3 shown bearing arrangement, wherein the lower sliding bearing shell in a bearing housing 5 is arranged. The bearing assembly may for example be a main bearing 2 be. It can be seen that the entire counter-runner 1 at the contact surfaces 40 both cups 10 is applied. In the case of a main camp becomes the counter-runner 1 formed by the journal of a crankshaft.

In the 5 a further embodiment is shown, in which also the bottom portion 32 via a spring device 38 in the form of a V-shaped section. The spring device 38 acts in the axial direction and leads to jamming of the guide element 30 in the lubricant channel 20 ,

In the 6 another embodiment is shown. The spring device 38 is through an M-shaped section in the bottom section 32 educated.

In the 7 own the thighs 34a , b in cross-section triangular, outwardly facing lugs, which act as a spring device 38 act in the axial direction to the lateral leakage in the groove flanks 24a to avoid b, and jamming of the guide element 30 in the lubricant groove 20 to effect.

In the 8th a further embodiment is shown, in which the lubricant channel 20 obliquely oriented groove edges 24a , b. Accordingly, the guide element has 30 except the thighs 34a , b at the bottom section 32 molded outwardly facing wing-like structures, which under bias to the groove sides 24a , b abut and in this way the guide element 30 in the groove 20 fix.

In the 9a another embodiment is shown in which the two legs 34a . 34b are arranged obliquely inclined outwards and thus to the bottom portion 32 take an angle> 90 °. As a result, a spring effect is achieved, so that the legs 34a . 34b under pressure on the groove sides 24a . 24b attack. In this embodiment, the spring means 38 in the thighs 34a . 34b integrated due to the inclination.

At the bottom section 32 are pointed, pointing inwardly facing lugs, which cause a spring action in the radial direction. In this respect, these approaches are also spring devices 36 that the entire guide element 30 and thus the thighs 34a . 34b upwards and thus press against the opponent.

In the 9b a further embodiment is shown, wherein on the legs 34a . 34b similar to the 9a are arranged obliquely, inwardly pointing, tapered approaches 39 are formed, the ends of the contact surfaces 40 form. These approaches 39 are due to the inclination with respect to the lower portion of the legs 34a . 34b resilient and thus form spring devices 36 which act in the radial direction.

In the 10 is another embodiment of a guide element 30 to be seen in perspective. The thigh 34a , b have holes in the upper area 42 , through which a targeted lubricant outlet from the lubricant channel 31 is guaranteed.

An alternative embodiment for a targeted lubricant outflow in the axial direction is in 11 shown. The thigh 34a , b have at the upper edge triangular edge recesses 44 z. B. in the form of notches. The contact surfaces 40 be this way through the edge recesses 44 interrupted, so that lubricant can flow away in the axial direction and thus the contact surfaces 40 lubricate.

In the 12 a further embodiment is shown, wherein the bottom portion 32 of the guide element 30 to the partial surfaces 12a . 12b thickened out. The bottom surface of the bottom section 32 approaches in the thickened end section 33 continuously the contact surfaces 40 the thigh 34a . 34b so that an unwanted oil drain in the area of the faces 12a . 12b effectively avoided. The thickened end section 33 lies on the upper, not profiled plain bearing shell 10 ' and is supported on the part surface. The depth of the second lubricant channel 31 in the guide element 30 runs to the subareas zero.

In the 13 is another embodiment for fixing the guide element 30 shown. In the field of oil drilling 18 has the guide element 30 also a lubricant opening 46 on, in which a tab as a holding element 50 is provided, which is bent down and thus into the oil hole 18 intervenes. The guide element 30 is fixed in this way in the circumferential direction.

In the 14 is another embodiment of a plain bearing shell 10 shown in plan view. The lubricant channel 20 is through two slots 60a . 60b in the plain bearing shell 10 educated. These two slots 60a , b are interrupted in the middle area by a web, in which a connecting groove 21 is arranged. The entire lubricant channel 20 is thus through the connecting groove 21 and the two slots 60a . 60b educated. Into the channel sections in the area of the oblong holes 60a . 60b is in each case a guide element 30 arranged.

The guide elements 30 fill the slots 60a . 60b completely off, leaving the bearing back 16 the sliding bearing shell 10 with the back surfaces of the guide elements 30 Aligns as in the 15 you can see. spring means 36 . 38 are not shown.

In the 16 is another embodiment of a bearing shell 10 shown, consisting of two bearing shell sections 11 . 11 ' is formed. Both bearing shell sections 11 . 11 ' are spaced in the housing 5 arranged to each other, so that between the bearing shell sections 11 . 11 ' a lubricant channel 20 is formed. In this Schmiermittekanal is a guide element 30 used the thighs 34a . 34b also have spring devices 36 on.

In the 17 is a circuit board 70 shown as the starting product for the production of a plain bearing shell 10 serves. The plane board 70 has a groove in which already a guide element 30 is used. This flat board will be together with the guide element 30 transformed into a plain bearing shell.

1

expeller

2

main bearing

5

bearing housing

10 10 '

plain bearing shell

11 11 '

Bush section

12a, b

subarea

14

sliding surface

16

bearing backing

18

oil well

20

lubricant channel

21

communicating

22

groove base

24a, b

flank

28

oil

30

guide element

31

second lubricant channel

32

bottom section

33

thickened end

34a, b

leg

36

spring means

38

spring means

39

approach

40

contact area

42

hole

44

edge recess

46

lubricant opening

50

retaining element

60a, b

Long hole

70

circuit board

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• - DE 102004028773 A1 [0006, 0006]
• DE 102005030307 A1 [0034]

Claims (28)

Plain bearing shell ( 10 ) for supporting a rotating counter-rotor ( 1 ) with an at least partially over the inner circumference extending lubricant channel ( 20 ) and arranged with at least one on the inner circumference, the bearing gap S between the plain bearing shell ( 10 ) and the counter-runner ( 1 ) closing guide element ( 30 ) for the lubricant ( 28 ), characterized in that the guide element ( 30 ) in the lubricant channel ( 20 ) and at least two contact surfaces ( 40 ) to invest in the counter-rotor ( 1 ) having. Slide bearing shell according to claim 1, characterized in that the guide element ( 30 ) at least one longitudinal section of the lubricant channel ( 20 ). Slide bearing shell according to one of claims 1 or 2, characterized in that the guide element ( 30 ) consists of a strip-shaped element Slide bearing shell according to claim 3, characterized in that the strip-shaped element has a U-profile, which has a bottom portion ( 32 ) and two from the bottom section ( 32 ) towering legs ( 34a , b). Slide bearing shell according to claim 4, characterized the leg height H ≤ the groove depth T is. Slide bearing shell according to one of claims 1 to 5, characterized in that the guide element ( 30 ) movable in the lubricant channel ( 20 ) is arranged. Slide bearing shell according to one of claims 1 to 6, characterized in that the guide element ( 30 ) is elastic. Slide bearing shell according to one of claims 1 to 6, characterized in that the guide element ( 30 ) in the lubricant channel ( 20 ). Slide bearing shell according to claim 8, characterized in that the guide element ( 30 ) in the lubricant channel ( 20 ) is pinched or latched. Slide bearing shell according to one of claims 1 to 9, characterized in that the guide element ( 30 ) at least one spring device ( 36 . 38 ) having. Slide bearing shell according to claim 10, characterized in that the spring device ( 36 ) is effective in the radial direction. Slide bearing shell according to claim 10, characterized in that the spring device ( 38 ) is effective in the axial direction. Slide bearing shell according to one of claims 10 to 12, characterized in that the spring device ( 36 . 38 ) on or in the bottom section ( 32 ) and / or on or in at least one leg ( 34a , b) is provided. Slide bearing shell according to one of claims 10 to 13, characterized in that the spring device ( 36 . 38 ) comprises a V-shaped section. Slide bearing shell according to one of claims 10 to 14, characterized in that the spring device ( 38 ) a bent leg ( 34a , b). Slide bearing shell according to one of claims 1 to 15, characterized in that each leg ( 34a , b) the U-profile has at least one hole ( 42 ) or a marginal recess ( 44 ) having. Slide bearing shell according to one of claims 1 to 16, characterized in that the lubricant channel ( 20 ) at least one lubricant opening ( 46 ) for the supply or removal of lubricant and that the guide element ( 30 ) in the area of the lubricant opening ( 46 ) a holding element ( 50 ) having. Slide bearing shell according to claim 17, characterized in that the retaining element ( 50 ) one in the lubricant hole ( 46 ) engaging, on the guide element ( 30 ) arranged tab is. Slide bearing shell according to one of claims 1 to 18, characterized in that the plain bearing shell ( 10 ) of two bowl-shaped sections ( 11 ) is formed, between which the guide element ( 30 ) is arranged. Slide bearing shell according to one of claims 1 to 18, characterized in that the plain bearing shell ( 10 ) in the circumferential direction at least one slot ( 60a , b) into which the guide element ( 30 ) is used. Slide bearing shell according to claim 20, characterized in that the plain bearing shell ( 10 ) in the circumferential direction at least two slots ( 60a , b), in the guide elements ( 30 ) are used. Plain bearing shell according to claim 21, characterized characterized in that between the two oblong holes ( 60a , b) a connecting groove ( 21 ) is provided. Slide bearing shell according to one of claims 1 to 22, characterized in that the thickness of the bottom portion of the U-shaped guide element ( 30 ) in the direction of at least one partial area ( 12a , b) the plain bearing shell ( 10 ) increases. Slide bearing shell according to one of claims 1 to 23, characterized in that the guide element ( 30 ) consists of copper, aluminum, steel, steel alloy or plastic. Slide bearing shell according to claim 24, characterized in that the guide element ( 30 ) PTFE, POM, PA, PVDF, PPS or PEEK or consists of these materials. Use of a plain bearing shell according to claim 1 as a main bearing shell in internal combustion engines. Method for producing a sliding bearing shell ( 10 ), characterized in that a board ( 70 ) is manufactured, that at least one groove ( 20 ) or a slot ( 60a , b) into the board ( 70 ) is introduced, that at least one guide element ( 30 ) and into the groove ( 20 ) or the slot ( 60a , b) and that the board ( 70 ) together with the at least one inserted guide element ( 30 ) to a plain bearing shell ( 10 ) is transformed. Bearing arrangement with two plain bearing shells ( 10 ) and one in the plain bearing shells ( 10 ) mounted rotating counter-runners ( 1 ), whereby between counterparts ( 1 ) and sliding surface ( 14 ) of the sliding bearing shell ( 10 ) a bearing gap S is present and wherein at least one sliding bearing shell ( 10 ) a lubricant channel ( 20 ) and at least one arranged on the inner circumference, the bearing gap S between the plain bearing shell ( 10 ) and the counter-runner ( 1 ) closing guide element ( 30 ) for the lubricant ( 28 ), characterized in that the guide element ( 30 ) in the lubricant channel ( 20 ) and at least two contact surfaces ( 40 ) to invest in the counter-rotor ( 1 ) having.