DE102007058744B4 - Slide bearing shell and bearing arrangement - Google Patents

Abstract

Sliding bearing shell (1) with two partial surfaces (2a, b) and with two lateral surfaces (3a, b), with at least one sliding surface forming sliding layer (12) made of a sliding layer material and having at least one lubricant barrier (20) arranged on the inner circumference, characterized in that the lubricant barrier (20) consists of a material charge that protrudes from the sliding surface, the material of the material charge having the sliding layer material and / or a bearing metal (11) located below the sliding layer material, and that next to the lubricant barrier (20) a groove-like depression (25) is provided.

Description

The invention relates to a sliding bearing shell with two partial surfaces and with two side surfaces, with at least one sliding surface forming a sliding layer of a sliding layer material and having at least one lubricant barrier arranged on the inner circumference.

The invention also relates to a bearing arrangement.

The plain bearing shells have on the inside a sliding surface, which is formed by a sliding layer material. The plain bearing shells may consist of a monometallic, but preferred is a layered composite material. In general, the plain bearing shells on a support material, in particular a steel backing, on which a sliding layer material or a layer system is applied with a sliding layer material as the upper layer. A typical layer structure provides for a bearing metal, which is applied to the steel backing, as well as a sliding layer applied to the bearing metal, wherein optionally one or more diffusion barrier layers may be arranged between the bearing metal and the sliding layer.

Such sliding bearing shells are well known and are mainly used in internal combustion engines for mounting the crankshaft. The crankshaft main bearings are supplied via channels with lubricants, in particular lubricating oil, wherein the oil is supplied via an oil groove in the plain bearing shell and the crankshaft cheek the connecting rod journal and thus the connecting rod. It was found that only about 25% of the oil arrives at the connecting rod bearing. This is due to the fact that the oil losses are mainly in the axial direction relative to the main bearing shells, that is perpendicular to the groove direction, very large. The oil drain is favored with increasing clearance between the sliding bearing shell and the counter-rotor, such as shafts or spigots. To constantly ensure adequate lubrication, correspondingly large oil pumps are required to deliver a sufficiently large amount of oil. A shortage and thus a demolition of the oil film in the connecting rod bearing and the insufficient supply of the connecting rod with oil would lead to rapid wear or seizure of the sliding partners and premature failure of the bearing.

To remedy this, be in the DE 10 2004 028 773 B4 Lubricant barriers proposed in the form of expansion elements, which are arranged either between the bearing housing and the plain bearing shell or between the plain bearing shell and the counter rotor. It is according to the DE 10 2004 028 773 B4 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 particularly costly with regard to their thermal expansion coefficient. There are proposed expansion elements, which are made of lightweight materials, such. As polytetrafluoroethylene compounds, may be made to compensate for expansion processes of the components.

As expansion elements, therefore, those are proposed which have a greater coefficient of thermal expansion than the materials from which the bearing element and the shaft to be supported or the plain bearing shell are made.

As far as the expansion elements are arranged in the sliding surface of the plain bearing shell, they are located on the plain bearing shell edge and thus spaced from the lubricant groove.

Since the expansion elements have a high coefficient of thermal expansion, a clamping pressure can be built up at high temperatures by the expansion elements at a small gap between the sliding bearing shell and the shaft, which hinders the rotation of the shaft or increases the wear of the expansion elements, whereby their effect to lose.

Another disadvantage is that the expansion elements must be manufactured separately and then used in specially prepared grooves. The production cost is very high.

The EP 1 255 053 B1 , JP H04-39 461 Y2, DE 10 2005 011 371 A1 . US 6 082 904 A and DE 34 15 929 A1 refer to so-called groove bearings, which have distributed over the entire inner surface of the bearing shell a plurality of closely spaced grooves or grooves which are separated by pointed upwardly facing projections. For describing such groove bearings, the groove pitch p (e.g. DE 10 2005 011 371 A1 ) or pitch p ( EP 1 255 053 B1 ), which indicates the distance of the peaks. This pitch value p is in the EP 1 255 053 B1 for example, with 200 microns and in the DE 10 2005 011 371 A1 indicated with 0.01 to 1 mm. With such a dense arrangement of grooves, the sliding surface is formed by the sum of the tips of these projections. The grooves are made by material removal. According to the EP 1 255 053 B1 the grooves z. B. produced by drilling.

The DE 101 56 345 A1 discloses a bearing shell having an inner peripheral surface serving as a sliding surface and an oil groove. In the interior Peripheral surface are provided two recesses which rise in the axial direction, starting from the oil groove.

The US 5,363,557 A and the US 2006/0 274 982 A1 disclose ramped elevations with oil grooves interposed therebetween, also machined. To a material Aufwurf this is also not.

The JP 2005 - 249 150 A relates to creating holes or sinks in a plain bearing using a laser.

From the JP 2004 - 144 255 A discloses a sliding bearing comprising an oil reservoir, wherein the oil from the oil reservoir is intended to lubricate the sliding surface of the sliding bearing. The sliding surface is supplied with oil via a lubricant channel, which has a smaller cross-sectional area than the oil reservoir.

The US 5,817,397 A. discloses that the surface of a lining element is formed of a plurality of uneven surfaces.

From the DE 600 25 423 T2 For example, a plain bearing is known which has a plain bearing layer in which the inner surface is a structured uneven surface and is coated with a cover layer. The uneven surface is formed by multiple depressions in a zigzag pattern.

The DE 103 55 466 A1 discloses a method for machining a tread of a bearing for a rotating member with a brush, in which the brush is guided such that in the axial direction seen in the central region of the bearing intersecting grooves or structures that are curved so that they in the axial direction of the bearing seen edge regions of the bearing surface are aligned substantially rectilinearly circumferentially around the circumferential direction, are formed in the bearing surface.

The JP 2001 - 182 751 A shows a plain bearing shell with two faces and with two side surfaces, with a sliding surface-forming sliding layer of a sliding layer material and with two arranged on the inner circumference lubricant barriers, the lubricant barriers consist of a relative to the sliding surface projecting material ejection.

It is therefore an object of the invention to provide a plain bearing shell, which allows no or at most only slight lubricant losses during operation, the lubricant barriers are to be produced easily and inexpensively.

This object is achieved with a sliding bearing shell and a bearing assembly according to the independent claims.

The sliding bearing shell according to the invention comprises two partial surfaces and two lateral surfaces, at least one sliding layer, which forms a sliding surface, of a sliding layer material and at least one lubricant barrier arranged on the inner circumference. The lubricant barrier consists of a material overhang protruding from the sliding surface. The material of the material throw has the sliding layer material and / or a bearing metal located under the sliding layer material. In addition to the lubricant barrier, a groove-like depression is provided.

Materialaufwürfe have the advantage that the lubricant barrier is an integral part of the plain bearing shell and thus in contrast to separate elements no measures to fix the lubricant barriers are required.

Another advantage is the fact that a Materialaufwurf consists at least of the sliding layer material and thus has the same positive sliding properties, as the rest of the sliding surface. Depending on the nature of the layer structure of the plain bearing shell and the height of the lubricant barrier material deposition consists either exclusively of the sliding layer material or the Aufwurf contains in addition to the material of the overlay still material from the underlying layers such. As the bearing metal or possibly also from the material of the diffusion barrier layer. There is thus the possibility of deliberately changing the properties of the lubricant barrier by the proportion of materials from the lower layers.

The Materialaufwurf preferably consists of a melt charge, which can be generated by means of treatment of the sliding layer by means of a laser beam in a simple manner.

As alternatives to the melt design of the material Aufauf consist of a minting, a Rollieraufwurf or a Rändelaufwurf. Such jars are produced by mechanical methods employing a die, a roller blade or a knurling tool. The formation of the lubricant barriers occurs in the mechanical process by material displacement.

Preferably, the plain bearing shells are used in crankshaft main bearings. It has been shown that when using these plain bearing shells in crankshaft main bearings, the oil flow can be reduced by up to 30%. The advantage of the reduced oil flow therefore allows the use of smaller dimensioned oil pumps, which engines can be operated significantly more economical.

Plain bearing shells preferably have a lubricant channel. At least one lubricant barrier is arranged between the bearing shell rim and the lubricant channel.

The lubricant barrier is preferably arranged at the edge or at a distance from the edge of the sliding bearing shell. For bearings with lubricant channel, the lubricant barriers can be moved inward to the extent that they are located at the edge or adjacent to the edge of the lubricant channel.

The lubricant barrier preferably extends at least over a portion of the inner periphery. The lubricant barrier may also have interruptions and thus include a plurality of barrier sections along the circumference. Interruptions of the lubricant barrier have the advantage that targeted small amounts of oil can flow in the axial direction and thus dirt particles can be discharged.

The lubricant barrier preferably extends from the partial surface over a portion of the inner circumference. The arrangement of the lubricant barrier in this area is advantageous because it has been determined that the largest oil losses occur there.

This is especially true when the plain bearing shell has an exposure in this area. Exposures extend from an end region of the sliding bearing shell to the partial surface and are arranged either in front of a partial surface or in front of both partial surfaces. The lubricant barrier in this embodiment preferably extends from the partial surface at least over the region of the exposure.

A further advantageous embodiment of the plain bearing shell provides that the lubricant barrier extends over the entire inner circumference of the plain bearing shell.

Preferably, at least one lubricant barrier is arranged at each edge or spaced from each edge.

The seal can be significantly increased if at least two lubricant barriers are arranged in the axial direction of the plain bearing shell. It creates a kind of labyrinth seal in this way. This arrangement is particularly advantageous if it is to be reckoned with a significant wear of the lubricant barriers during operation and thus a deterioration of the sealing effect. A staggered arrangement of lubricant barriers in the axial direction, preferably also with different heights H of the lubricant barriers, improves the sealing effect.

Lubricant barriers can be carried out arbitrarily. Preference is given to straight-line lubricant barriers, undulating lubricant barriers and zigzag lubricant barriers, it also being possible to combine different designs.

It has proven to be advantageous if the lubricant barrier turns in the direction of the partial surface to the outside. If lubricant barriers are provided on both sides, this increases the flow cross section of the lubricant in the direction of the partial surface. The dynamic pressure can be reduced thereby targeted.

It is also possible to bend the lubricant barriers in the direction of partial surfaces inwards. Accordingly, in the case of an arrangement of two lubricant barriers, the flow cross section is correspondingly reduced, as a result of which an increase in pressure in the area between the lubricant barriers can be achieved.

A Materialaufwurf goes along with a reduction in material elsewhere. In this respect, forms a groove-like depression in the preparation of the lubricant barriers next to the lubricant barrier. This groove-like depression can be advantageously used if it is arranged on the inwardly facing side of the lubricant barrier and thus is overflowed by the lubricant, in particular the lubricating oil. It has been found that dirt particles in the lubricant collect in this groove-like depression and thus can be removed from the lubricant in a simple manner.

The groove-like depression can also be arranged on the outwardly facing side of the lubricant barrier.

According to a further embodiment, the groove-like depression may be arranged between two lubricant barriers. Such an arrangement can be produced for example by means of a laser beam, which is directed perpendicular to the inner surface of the sliding bearing shell, so that a material aufaufet forms on both sides of the laser beam.

The height H of the lubricant barrier is preferably from 5 to 60 μm and depends essentially on the gap between the plain bearing shell and the counter rotor. Preferred heights of the lubricant barrier are 10 to 50 μm, 30 to 50 μm and 30 to 40 μm.

The width B of the lubricant barrier is advantageously 0.5 to 2 mm, in particular 0.75 to 1.5 mm. Wider lubricant barriers have the advantage that during operation a lesser removal of the lubricant barriers takes place than is the case with narrower lubricant barriers.

A bearing arrangement according to the invention provides for two plain bearing shells and a rotating counter-rotor mounted in the sliding bearing shells, wherein a bearing gap S is present between the counter-rotor and sliding surface of the sliding bearing shell, wherein at least one sliding bearing shell has a lubricant channel and at least one bearing gap S between the sliding bearing shell and the at least one arranged on the inner circumference Counteractor has closing lubricant barrier. At least one sliding bearing shell of this bearing arrangement has a lubricant barrier, which consists of a material throw, wherein the material of the material throw-up comprises the sliding layer material and / or a bearing metal located below the sliding layer material. In addition to the lubricant barrier, a groove-like depression is furthermore provided. During operation, the lubricant barrier contacts the counter-rotor.

Preferably, lubricant barriers in the form of material drops are provided on both sides at least in the region of the lubricant groove.

• - Bereitstellen einer vorgefertigten Gleitlagerschale, und
• - Ausbilden mindestens einer Schmiermittelbarriere mittels mindestens eines Laserstrahls, der unter einem Winkel α auf die Innenfläche der Gleitlagerschale gelenkt und längs einer vorbestimmten Bahn über die Innenfläche geführt wird, wobei der Winkel α zwischen dem Laserstrahl und der Senkrechten auf der Innenfläche gemessen wird.

A method for producing plain bearing shells may comprise the following steps:

• - Providing a prefabricated plain bearing shell, and
• - Forming at least one lubricant barrier by means of at least one laser beam which is directed at an angle α on the inner surface of the sliding bearing shell and guided along a predetermined path over the inner surface, wherein the angle α between the laser beam and the perpendicular to the inner surface is measured.

The use of laser beams has the advantage that after the provision of the sliding bearing shell without mechanical stress, the lubricant barriers can be produced. This means that the sliding bearing shell can already be calibrated and only has to be subjected to this mechanically non-incriminating process step.

Another advantage is that the laser beam can be directed to any point of the inner surface of the plain bearing shell, so that at any point the lubricant barriers can be generated.

On the other hand, various properties of the lubricant barriers and the groove-like depression adjacent to the lubricant barrier can be adjusted via the power of the laser beam on the one hand and over the angle α on the other hand.

The power of the laser and thus the energy input by the laser beam can be used to control the level of the melt charge. It is thus possible to keep the height of the material charge constant or to vary the height according to a predetermined pattern.

Along the path, it is possible to adjust both the height of the lubricant barrier and its width by changing the power and possibly also by changing the angle α. The larger the angle α is chosen, the wider the groove-like depression, from which the material is provided for the material throw-up. In the case of normal incidence (angle α = 0), material deposition is created on both sides of the groove-like depression, so that a double barrier is formed.

The prefabricated plain bearing shell may already have the sliding layer according to a first exemplary method. Subsequently, the formation of the lubricant barriers can be performed. This method is suitable for plain bearing shells whose sliding layer has a corresponding thickness. This is the case, for example, with plain bearing shells which carry a sliding layer several 100 μm thick on the steel backing.

According to another exemplary method, thinner sliding layers can also already be applied to the plain bearing shell. Such overlays can be plated or applied by electroplating. These applied to a bearing metal sliding layers are usually in the range of a few 10 microns. In this exemplary method, it is advantageous to choose the angle α as large as possible, so that the underlying layer is not affected by the laser beam and thus no material of this underlying layer is removed. However, if it should be necessary to remove this material and incorporate it in the melt charge to adjust the properties of the lubricant barrier accordingly, a correspondingly smaller angle α can be selected.

For example, the prefabricated slide bearing shell can not yet comprise a sliding layer, so that the melt deposition is formed from the material of the layer located below the sliding layer, for example a bearing metal layer. The sliding layer is applied in this embodiment of the method after the formation of the lubricant barrier. The sliding layer thus also covers the Grease barrier. The sliding layer can be applied galvanically, for example.

Preferably, a pulsed laser, in particular a pulsed solid-state laser is used. By means of a pulsed laser, a high power is briefly introduced, which generates the desired material Aufauf. Preferably, the laser is pulsed at a frequency of 50 to 100 hertz, in particular 60 to 80 hertz. This leads to a scale-like formation in the region of the groove-like depression, which is related to the fact that the pulsed laser beam is moved continuously over the inner surface of the sliding bearing shell.

The laser beam is preferably directed at an angle α between 0 ° and 50 ° to the inner surface. Preferred angles lying at 25 ° to 35 °.

Exemplary embodiments of the invention are explained below with reference to the drawings.

• 1 eine perspektivische Darstellung einer Gleitlagerschale gemäß einer ersten Ausführungsform, in der Mitte aufgeschnitten und aufgeklappt,
• 2 eine perspektivische Darstellung eines Endabschnitts einer Gleitlagerschale gemäß einer weiteren Ausführungsform, vergrößert,
• 3 eine perspektivische Darstellung eines Endabschnitts einer Gleitlageschale gemäß einer weiteren Ausführungsform, vergrößert,
• 4 eine perspektivische Darstellung einer Gleitlagerschale gemäß einer weiteren Ausführungsform, in der Mitte aufgeschnitten und aufgeklappt,
• 5a - 5f verschiedene Ausführungsformen von Schmiermittelbarrieren anhand von halbierten Lagerschalen in perspektivischen Darstellungen,
• 6 - 14 verschieden Querschnittsformen und Anordnungen von Schm ierm ittelbarrieren,
• 15 die Teildraufsicht auf eine Schmiermittelbarriere mit benachbarter nutartiger Vertiefung mit geschuppter Oberfläche in vergrößerter Darstellung,
• 16 die Seitenansicht einer Gleitlagerschale mit einer Schmiermittelbarriere gemäß einer weiteren Ausführungsform,
• 17 - 18 schematische Darstellungen verschiedener mechanischer Herstellungsverfahren im Schnitt,
• 19 eine Lageranordnung in Seitenansicht,
• 20 eine Lageranordnung im Längsschnitt in der Ebene XX-XX der 19, und
• 21 ein Diagramm, das den Ölfluss in Abhängigkeit von der Umdrehungsgeschwindigkeit des Gegenläufers und des Öldruckes zeigt.

Show it:

• 1 a perspective view of a plain bearing shell according to a first embodiment, cut open in the middle and opened,
• 2 3 a perspective view of an end section of a sliding bearing shell according to a further embodiment, enlarged,
• 3 a perspective view of an end portion of a sliding bearing shell according to another embodiment, enlarged,
• 4 a perspective view of a sliding bearing shell according to another embodiment, cut open in the middle and opened,
• 5a - 5f various embodiments of lubricant barriers based on halved bearings in perspective views,
• 6 - 14 various cross-sectional shapes and arrangements of lubricant barriers,
• 15 the partial plan view of a lubricant barrier with adjacent groove-like recess with scaly surface in an enlarged view,
• 16 the side view of a sliding bearing shell with a lubricant barrier according to another embodiment,
• 17 - 18 schematic representations of various mechanical production processes in section,
• 19 a bearing arrangement in side view,
• 20 a bearing arrangement in longitudinal section in the plane XX-XX of 19 , and
• 21 a diagram showing the oil flow as a function of the speed of rotation of the counter-rotor and the oil pressure.

In the 1 is a plain bearing shell 1 shown in perspective, the two ends at its two ends 2a . b and at the front sides two side surfaces 3a . b having. The inner surface of the plain bearing shell 1 is with 5 while the rear outer surface is the reference numeral 4 wearing. Along the inner circumference is a lubricant channel 15 arranged, over an oil well 17 in the area of the vertex 7 the plain bearing shell with lubricant, especially lubricating oil, is supplied.

In the in the 1 shown embodiment are in the end regions of the plain bearing shell 1 spaced to the edge 8th two lubrication barriers each 20 presented in the form of Materialaufwürfen.

The lubricant barriers 20 extend from the faces 2a . b as straightforward barriers towards the vertex 7 and terminate at a distance from the vertex 7 , Immediately adjacent to the lubricant barriers 20 are groove-like depressions 25 provided in connection with the 6 to 18 be described in more detail. By means of these lubricant barriers 20 becomes the uncontrolled oil drain in the direction of the axis 6 the plain bearing shell effectively prevented.

In the 2 is an enlarged view of another embodiment of the sliding liner 1 shown in the end below the subarea 2a an exposure 16 having. This exposure is continuous in the inner surface 5 over and ends in front of the lubricant channel 15 whose groove depth is continuously in the direction of the partial surface 2a reduced. The lubricant barrier 20 extends from the subarea 2a through the exposure area into the inner surface 5 and ends below the exposure area 16 ,

The plain bearing shell of 3 differs from the embodiment according to the 2 only in that the lubricant channel 15 down to the partial area 2a extends.

In the 4 an embodiment is shown in which the lubricant barriers 20 over the entire inner circumference of a partial surface 2a to the other part surface 2 B extend. The lubricant barriers are designed as straight-line barriers. A lubricant channel 15 is with this plain bearing shell 1 not provided. All embodiments of lubricant barriers 20 can on plain bearing shells 1 with and without lubricant channel 15 will be realized.

In the 5a to 5f Different versions are shown schematically. In the 5a are on both sides of the lubricant channel 15 two lubricant barriers each 20 intended. These can be the same or different height H respectively.

In the 5b to 5f are the depressions 25 have been omitted for clarity.

In the 5b are lubricant barriers 20 shown having breaks. This embodiment has the advantage that a targeted oil drain is permitted over the length of the individual lubricant barrier sections and the corresponding interruptions in order, for example, to discharge dirt particles.

In the 5c are lubricant barriers 20 shown, the end sections 21 have, which are arranged inclined outwardly, so that the cross section between the lubricant barrier 20 in the direction of the partial area 2a is enlarged. In the 5d is a wave-shaped embodiment of the lubricant barriers 20 shown. In the 5e are the end sections 22 the lubricant barriers 20 inclined inwards, so that a cross-sectional reduction is achieved.

In the 5f are zigzag lubricant barriers 20 shown.

In the 6 is shown schematically as by means of a laser beam 30 , which is perpendicular to the inner surface 5 directed material spills to form lubricant barriers 20 can be generated. By the vertical impact of the laser beam 30 becomes a groove-like depression 25 generated, which has on both sides of this recess material Aufwürfe. Since the material from the groove-like depression 25 on two lubricant barriers 20 These are lower than if they were the same material for a single lubricant barrier 20 is used, as in the 7 is shown. There, the laser beam at the angle α of about 30 ° relative to the vertical 32 on the inner surface 5 directed. As a result, the molten material is only on one side of the groove-like depression 25 piled up.

In the 7 are heights and widths of the lubricant barrier 20 located. Typical values for the height H are 5 - 60 microns, with values between 35 and 45 microns are preferred. The width B of the lubricant barrier is between 0.5 and 2 mm.

When the angle α is made larger, the groove-like depression becomes shallower and wider as shown in FIG 8th is shown.

When the laser beam 30 in contrast to the embodiment of 7 and 8th from the right side to the surface 5 is directed, arises on the left side of the groove-like depression 25 the lubricant barrier 20 (please refer 9 ).

In the 10 is the embodiment of 9 shown again, wherein the groove-like depression 25 with dirt particles 26 is filled up. This embodiment provides that the lubricant barrier 20 adjacent to the edge 8th is arranged and the groove-like depression 25 insofar provided inside, so that the groove-like depression 25 is overflowed by the lubricant. The groove-like depression 25 serves as a reservoir for dirt particles of the skid.

In the 11 is shown a further embodiment in which the groove-shaped recess 25 is arranged outside lying. The groove-like depression 25 is located between the edge 8th the sliding bearing shell 1 and the lubricant barrier 20 , According to the 11 exists the plain bearing shell 1 from a steel back 10 and a sliding layer 12 , z. B. from AlSn20 shown. The sliding layer 12 has a thickness of about 250 microns to 400 microns, so that the groove-like depression 25 exclusively in the overlay 12 located. Accordingly, the lubricant barrier becomes 20 exclusively of the material of the sliding layer 12 educated.

In the 12 a further embodiment is shown, which is a plain bearing shell 1 with a composite material consisting of three layers. On the steel back 10 is a bearing metal 11 applied to the example by electroplating a sliding layer 12 is applied. The bearing metal can for example consist of CuNi2Si, on which a sliding layer 12 made of the material SnCu6. The sliding layer 12 has a thickness of 15 microns to 20 microns.

To a lubricant barrier 20 With a height in the range to produce up to 60 microns, it is necessary that a corresponding amount of material is melted. The thickness of the sliding layer 12 is not enough, so that also material of the bearing metal 11 participates in the melting process. This causes the lubricant barrier 20 both material of the sliding layer 12 as well as material of the bearing metal 11 having. This is in the 12 only shown schematically.

In the 13 a further embodiment can be seen, according to which the sliding layer 12 only after the formation of the lubricant barrier 20 and thus the groove-like depression 25 is applied, preferably galvanized. This method has the advantage that the sliding layer 12 largely uniform all areas including the groove-like depression 25 and the lubricant barrier 20 covered. The thickness of the sliding layer 12 is therefore almost the same size at all points.

In the 14 is another embodiment of a three-layer bearing shell 1 shown. In this embodiment, the laser beam becomes 30 at a large angle α to the surface 5 directed so that only the material of the sliding layer 12 used up and used for the formation of the Schmelzaufwurfs.

In the 15 is the top view of a lubricant barrier 20 with juxtaposed groove-like depression 25 shown. It can be seen that the groove-like depression 25 a structure with scales 27 having. Preferably, a pulsed laser is used, the laser beam continuously over the surface of the plain bearing shell 1 to be led. The scale structure is created by the laser pulses.

In the 16 another embodiment is shown in which the lubricant barrier 20 has a wavy contour. The height H of the lubricant barrier 20 varies along the circumference, which can be achieved by a corresponding control of the laser with respect to its performance. This embodiment has the advantage that over the troughs of the lubricant barrier 20 can selectively drain a defined amount of oil and thus also dirt particles.

In the 17 and 18 mechanical production processes are shown. In the 17 becomes a stamp 40 with a lead 42 and a depression 44 on the surface of the sliding layer 12 pressed. When the stamp is pressed on a material displacement takes place, so that a lubricant barrier 20 with adjoining groove-like depression 25 is produced.

In the 18 becomes a roller blade 50 used at the angle α in the surface of the layer 12 is pressed in order to produce in this way a material Aufwurf.

In the 19 is a bearing arrangement with upper shell 1' and lower shell 1 and shown with a counter-runner in side view.

In the 20 is the bearing assembly along the section line in 19 with two of the plain bearing shells 1 . 1' and the counter-runner 8th represented in the form of a rotating shaft. Between the inner surface 5 the sliding bearing shells 1 . 1' and the shaft passes a gap S, which is the barrier of the lubricant 20 side of the plain bearing shells 1 . 1' closed, leaving the lubricant 9 can not drain away laterally. In this arrangement has only the upper shell 1' a lubricant channel 15 ,

In the 21 is a diagram of the oil loss at the main bearing shell as a function of the speed and the oil pressure shown. It can be seen that the oil loss in a plain bearing shell without lubricant barriers is significantly higher than in a plain bearing shell with lubricant barriers. The oil savings are approximately 15% to 30% over the entire speed range. Here, a plain bearing shell with lubricant barriers according to the 3 used.

LIST OF REFERENCE NUMBERS

1, 1 '

plain bearing shell

2a, b

subarea

3a, b

side surface

4

outer surface

5

palm

6

Axle of the plain bearing shell

7

Vertex of the plain bearing shell

8th

expeller

9

lubricant

10

support material

11

bearing metal

12

Overlay

15

lubricant channel

16

exposure

17

oil well

20

lubricant barrier

21

Section of the lubricant barrier

22

Section of the lubricant barrier

25

groove-like depression

26

dirt

27

shed

30

laser beam

32

vertical

40

stamp

42

head Start

44

deepening

50

rolling knife

Claims (27)

Sliding bearing shell (1) with two partial surfaces (2a, b) and with two lateral surfaces (3a, b), with at least one sliding surface forming sliding layer (12) made of a sliding layer material and having at least one lubricant barrier (20) arranged on the inner circumference, characterized in that the lubricant barrier (20) consists of a material charge that protrudes from the sliding surface, the material of the material charge having the sliding layer material and / or a bearing metal (11) located below the sliding layer material, and that next to the lubricant barrier (20) a groove-like depression (25) is provided. Slide bearing shell after Claim 1 , characterized in that the material throw consists of a melt charge. Slide bearing shell after Claim 1 , characterized in that the Materialaufwurf consists of a minting or Rollieraufwurf. Plain bearing shell according to one of Claims 1 to 3 , characterized in that the lubricant barrier is arranged on the edge (8). Plain bearing shell according to one of Claims 1 to 3 , characterized in that the lubricant barrier spaced from the edge (8) of the sliding bearing shell (1) is arranged. Slide bearing shell after Claim 4 , characterized in that the sliding bearing shell has a lubricant channel (15) and that at least one lubricant barrier (20) between the edge (8) and the lubricant channel (15) is arranged. Plain bearing shell according to one of Claims 1 to 6 , characterized in that the lubricant barrier (20) extends over at least a portion of the inner circumference. Plain bearing shell according to one of Claims 1 to 7 , characterized in that the lubricant barrier (20) extends from the partial surface (2a, b) over a portion of the inner circumference. Plain bearing shell according to one of Claims 1 to 8th , characterized in that the sliding bearing shell (1) on the inner circumference at least one up to a partial surface (2a, b) extending exposure (16) and that the lubricant barrier (20) of the partial surface (2a, b) at least over the exposure (16) extends. Plain bearing shell according to one of Claims 1 to 9 , characterized in that the lubricant barrier (20) extends over the entire inner circumference of the sliding bearing shell (1). Plain bearing shell according to one of Claims 1 to 10 , characterized in that at least one lubricant barrier (20) is arranged at each edge (8) or at a distance from each edge (8). Plain bearing shell according to one of Claims 1 to 11 , characterized in that in the axial direction of the sliding bearing shell (1) at least two lubricant barriers (20) are arranged. Slide bearing shell after Claim 12 , characterized in that in the axial direction juxtaposed lubricant barriers (20) have different heights H. Plain bearing shell according to one of Claims 1 to 13 , characterized in that the lubricant barrier (20) is designed straight. Plain bearing shell according to one of Claims 1 to 13 , characterized in that the lubricant barrier (20) is wave-shaped. Plain bearing shell according to one of Claims 1 to 13 , characterized in that the lubricant barrier (10) is designed zigzag. Plain bearing shell according to one of Claims 1 to 16 , characterized in that the lubricant barrier (20) in the direction of the partial surface (2a, b) turns outward. Plain bearing shell according to one of Claims 1 to 17 , characterized in that the lubricant barrier (20) in the direction of the partial surface (2a, b) turns inwards. Slide bearing shell after Claim 18 , characterized in that the groove-like depression (25) is arranged on the inwardly facing side of the lubricant barrier (20). Sliding tray after Claim 18 , characterized in that the groove-like recess (25) on the outwardly facing side of the lubricant barrier (20) is arranged. Plain bearing shell according to one of Claims 1 to 20 , characterized in that the groove-like depression (25) between two lubricant barriers (20) is arranged. Plain bearing shell according to one of Claims 1 to 21 , characterized in that the height H of the lubricant barrier is 5 to 60 microns. Plain bearing shell according to one of Claims 1 to 22 , characterized in that the width B of the lubricant barrier (20) is 0.5 -2 mm. Plain bearing shell according to one of Claims 1 to 23 , characterized in that the sliding bearing shell (1) consists of a carrier material (10) and a sliding layer (12) located thereon, and that the lubricant barrier (20) consists of sliding layer material. Plain bearing shell according to one of Claims 1 to 23 , characterized in that the sliding bearing shell comprises a carrier material, a bearing metal (11) and a sliding layer (12) applied thereto and in that the lubricant barrier (20) consists of sliding layer material or of sliding layer material and bearing metal (11). Bearing arrangement with two plain bearing shells (1, 1 ') and one in the sliding bearing shells (1, 1') mounted rotating counter-rotor (8), wherein between counter-rotor (8) and sliding surface of the plain bearing shell (1, 1 ') a bearing gap S is present, wherein at least one sliding bearing shell (1, 1 ') has a lubricant channel (15) and at least one lubricant barrier (20) arranged on the inner circumference and closing the bearing gap S between the sliding bearing shell and the counter rotor, characterized in that the lubricant barrier (20) comprises one the sliding surface of the bearing shell (1, 1 ') projecting Materialaufwurf consists, wherein the material of the Materialaufwurfs the sliding layer material and / or under the sliding layer material befindlichem bearing metal (11) and in that next to the lubricant barrier (20) has a groove-like recess (25) is provided and in operation, the lubricant barrier (20) contacts the counter-rotor (8). Bearing arrangement after Claim 26 , characterized in that the sliding bearing shell (1, 1 ') at least in the region on both sides of the lubricant channel (15) each have at least one lubricant barrier (20).

Images