FI83693B - GLIDLAGERELEMENT MED OHOMOGENT GLIDSKIKT. - Google Patents

Description

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Sliding bearing element with non-uniform sliding layer Glidlagereleraent med ohomogent glidskikt

The present invention relates to a plain bearing element provided with a non-uniform sliding layer comprising a protective layer and a bearing layer made of bearing material attached thereto. as a bearing material filled with grooved recesses, the invention being particularly directed to radial plain bearings, the bearing layer 15 of which is provided with grooved recesses filled with a sliding bearing material extending over at least a part of its area.

Based on patent publication AU-PS 143 992, and in particular the relevant part of Figure 5 and the description thereof, a plain bearing with a non-uniform sliding layer 20 is provided with helical grooves extending in the circumferential direction. These grooves are filled with a soft plain bearing material with only low bearing capacity but instead good friction properties. According to AU-PS 143 992, these grooves must be dimensioned according to different operating conditions. However, no instructions are given in this context for carrying out the actual dimensioning according to the conditions of use.

AT-PS 323 476 discloses a sliding element, in particular a plain bearing, formed as a unitary compression part in which structural polymers filled with grease, such as graphite, bornitride, molybdenum sulphide or mixtures thereof, such as polyol resin, polyester, polyero, polyhet, are placed alternately. self-lubricating plastic sections comprising phenyl, etc. Also, AT-PS 323 476 does not provide guidelines for dimensioning grease-filled recesses in such a load-bearing layer 35.

2,83693

In addition, EP-PS 57 808 discloses an arrangement in which a softer bearing material is encapsulated in grooved recesses in a layer of harder bearing material, mainly running in the direction of use of the bearing, in order to combine the advantages of a harder and softer bearing material. Since the fine distribution of the harder and softer bearing material is ensured over the entire width of the contact surface by means of fixed distances between adjacent recesses, the individual bearing materials also act in combination with their separate effect in the local load areas, thus significantly eliminating the disadvantages of the individual bearing materials. The bearing material layer made of a harder material then acts as a load-bearing layer, which is relatively relieved by the softer material layer, as a result of which the longevity and wear resistance of the bearing are improved. Nevertheless, such plain bearings function in practice in the same way as a bearing with a through-going drive layer made of a substantially softer bearing material, but have the advantage over the latter bearings that they are much more wear-resistant. Thus, in the case of a plain bearing according to EP-PS 57 808, good operating results should be obtained in terms of bearing wear and fatigue, the width, depth and mutual distance of the grooves depending on the diameter of the bearing.

. . However, practice has shown that in the case of the reported very wide and scattered maximum and minimum ranges of groove dimensions, the optimal distribution of soft and hard material parts in the middle regions themselves is not achieved. Bearings manufactured in this way also do not meet the high requirements set or expected for them in the absence of important critical additional factors. Thus, for example, it has been overlooked that bearings of a certain diameter can be loaded in completely different ways, so that the diameter of the bearing is in no way suitable as a reference for carrying out sufficient measures to reduce wear and fatigue in practice.

3,83693 AU patent 143,992, FR patent 797 483 and DE operating model 69 29 557 refer to the load dependence of the structure. However, learning how to take load dependence into account is not given.

5

It is therefore an object of the present invention to provide a highly load-bearing plain bearing with a non-uniform sliding layer which fully meets the requirements for such a plain bearing, including the possibility of performing wear and fatigue reducing measures based on the specific bearing load in each case unambiguously and reproducibly defined.

This object is achieved according to the invention by means of the characteristic features set out in claims 15 to 3.

The characteristic measures stated in claim 1 are no longer related to the diameter of the bearing, but to the specific load of the bearing, which is obtained from the following formula: 20 p - specific load of the bearing [N / mm2]

: _ F

P -

25 D · B

F - bearing force (load) [N] D - bearing diameter [mm] (inner diameter) B - bearing layer width [mm] 30 In addition to the specific load p of the above bearing for dimensioning recesses for. In the context of the invention, it has been shown that the value of the specific load has a considerable effect on the placement of the groove-like recesses. This applies, on the one hand, to the design specific load of the plain bearing and, on the other hand, to the bearing capacity of the bearing material for the bearing layer corresponding to the intended use in a natural way 4 83693 and also of the plain bearing material selected for filling grooved recesses. Thus, in a particularly preferred embodiment of the invention, the width b of the grooved recesses 5, the bandwidth s between these recesses and the ratio between the groove width b and the bandwidth s can be determined mathematically by the load capacity of the selected bearing material and also the actual designed bearing specific load. Similarly, the relationship between the groove depth t of the recesses and the width b and depth t of the groove recesses can be calculated mathematically depending on the load capacity of the plain bearing material selected for filling the groove recesses, as well as the actual designed specific load of the bearing.

In connection with the invention, it is possible to use both simple grooved recesses running in the direction of use of the bearing and grooved recesses arranged in different groups, for example in two transversely extending groups, especially also when the opposite distances of the grooved recesses belonging to different groups must be different.

20

Experiments have shown that by taking into account the specific load of the bearing in the dimensioning of the grooved recesses according to the invention, optimal results have been achieved in terms of bearing durability, wear and emergency use.

".V 25: Various embodiments of the invention will be described in more detail below with reference to the accompanying drawings, in which:

Figure 1 shows a perspective view of a plain bearing according to the invention formed of two plain bearing flanges;

Figure 2 shows a plain bearing according to the invention in the form of a bearing sleeve; Fig. 3 schematically shows the quantities required for calculating the area of the bearing operating surface with recesses; 5,83693

Fig. 4 shows the area 5 of Fig. 1 greatly enlarged;

Fig. 5 shows the area 5 of Fig. 1 in a modified embodiment greatly enlarged; 5

Fig. 6 shows a greatly enlarged plan view of the area 6 of Fig. 1;

Fig. 7 shows a modified embodiment of the invention according to Fig. 6;

Fig. 8 shows a plan view corresponding to Fig. 6 of a further embodiment of the invention; Fig. 9 shows a one-piece ring-sliding bearing formed according to the invention; and

Figure 10 shows a perspective view of a bearing flange and two half-ring-shaped spacers for a bearing according to the invention.

20

A plain bearing 20 according to Figs. 1-8, for example a plain bearing or plain bearing housing 23 formed by two bearing flanges 21 and 22, which may be seamless or curved and provided with an axial slot 24, is provided with grooved recesses 26 formed in the bearing layer 25 of its bearing surface 25. The central shaft of the bearing is marked with the number 28.

In the example according to Figure 1, the plain bearing 20 is formed by two bearing flanges 21 and 22, the bearing layer 27 of which has groove-like recesses 26.

Various embodiments can be used for the grooved recesses 26, such as circular circumferential grooves as shown in FIG. The grooved recesses 26 can also be made 35 helical with a small angle of inclination of up to 15 °. Between the grooved recesses 6 83693 26 and the lanes 29 therebetween - as can be seen in particular from Figure 3 - the following quantities are important: a: The distance between the center lines of the lanes; 5b: Width of the recess in the area of the sliding surface; s: Bandwidth in the area of the sliding surface; t: Depth of recess.

Of the relationships between these quantities, the relationship between the width-10 den b of the recess and the bandwidth s is particularly important. To calculate the relationship between these quantities and the recess width b and the band width s, the minimum, maximum and average values obtained from the bearing specific load p shall be used, where 15 p [N / mm21 is calculated from the formula:

F

p - -

D · B

20 where F - bearing force (load) [N] D - bearing diameter [mm] (inner diameter) B - bearing bearing width [mm] '·' In this way the following is calculated: 25 a) The width b [pm] of the grooved recesses 26; for load-bearing load-bearing layers with a load capacity of more than 50 N / mm2 from the projected bearing surface, the maximum width may be equal to or less, but preferably equal to 30 p + 20 b ™ - 200 - - P + 12.5 for low-load-bearing load-bearing layers with a load-35 measurability of less than 35 N / mm2 from the projected bearing surface, the minimum width value may be equal to or greater than, but preferably equal to -> 83693 p + 20 b ™ n “56.25 - - p + 12.5 5 for load-bearing load-bearing layers with an average load capacity of about 30-55 N / mm2 based on the projected bearing surface, the average value of the width may be less or greater, but preferably equal to 10 p + 20 - 75 --- P + 12,5 15 (b) Intermediate bandwidth s [/ jm]: for low-load-bearing load-bearing layers with a load capacity of less than 35 N / mm2 of projected bearing from the rim, the maximum value of the width may be equal to or less, but preferably equal to 20 2050 (p + 20) s —-- 1-1-1- 118.06 + 9,652 · p + 6,528 · 10'2 p 2 + 3,889 · 10'3 · p 3 For 25 load-bearing load-bearing layers with a load capacity greater than 50 N / mm2 from the projected bearing surface, the minimum width value may be equal to or greater than, but preferably equal to, 525 (p + 20) 30 Snin- ----- = - 118.06 + 9,652 · p + 6,528 · 10'2 · p 2 + 3,889 · 10'3 · p 3 for load-bearing load-bearing layers with an average load capacity of approximately 30 to 55 N / mm2 calculated from the projected bearing pin, the average value of the width may be smaller or larger, but preferably equal to 750 (p + 20) 40 st.k -------- 118.06 + 9.652 · p + 6.528 · 102 p 2 + 3,889 · 103 · p 3 8 ^ _ 83693 c) Recess depth t [μπι]: fillers that can withstand high loads, i.e. for plain bearing materials with a load capacity of more than 40 N / mm2 from the projected bearing surface, the maximum depth value may be equal to or less, but preferably equal to 1350 t --- z- 10 p + 12.5 low load-bearing fillers, i.e. for plain bearing materials with a load capacity of less than 20 N / mm2 from the projected bearing surface, the minimum depth value may be equal to or greater than 15, but preferably equal to 900 μm min p = 12.5 20 average load-bearing fillers, i. for plain bearing materials with a load capacity of approximately 20-45 N / mm2 •: ··· based on the projected bearing surface, the average depth may be less than or greater, but preferably equal to 25 than 1125

^ kMk ”Z

p + 12.5 30 d) Ratio between the width b of the recess and the width s of the band between them: for load-bearing load-bearing layers with a load-35 measurability greater than 50 N / mm2 from the projected bearing surface (Vs) ™, - (between 1 , 95 - 2,0) - (1,757 + 3,1-10 · * · p + 7,233-10 · «· p 2) 9 83693 for low-load-bearing load-bearing layers with a load capacity of less than 35 N / mm2 of the projected from the bearing surface (b / s) ^ - (between 0.50 and 0.55) - (0.5100 + 0.9-103 · p + 2.1-104 · p 2) 5 for load-bearing layers bearing average loads, with a load capacity of approximately 30-55 N / mm2 from the projected bearing surface (b / s) ^ - 0,9444 + 1,6667 · 10 ° · p + 3,8889 · 10 "4 · p 2 10 and the selected recess width (b ) dependence on the depth (t) of the recess for heavy-duty fillers, ie plain bearing materials with a load capacity of more than 40 N / mm2 from the projected 15 bearing surfaces (b / t) ^ - 4, 167 · ΙΟ'2 p + 0.8333 low load-bearing fillers, i.e. For plain bearing materials with a load capacity of less than 20 N / mm2 from the projected bearing surface (b / t) - (- between 1.95 and 2.0) 10.834 · 10'2 · p + 2.1666 fillers with average load capacity, i. for plain bearing materials with a load capacity of approximately 20-45 N / mm2 from the pro-25 bearing surface (b / t) ^ - 6,667 · ΙΟ'2 · p + 1,333 In this context, it should be noted that when dimensioning the grooved recesses of such a plain bearing in principle 30 not only the diameter of the bearing is used, but above all the pressure of the lubricating diaphragm. In a simplified form, the specific load of the bearing can be set instead of the pressure of the lubricating diaphragm. In this case, it has been found that in the case of high specific loads, more favorable quantities are obtained for grooved recesses (width, depth, distance) than in the case of low specific loads. This fact has an amazing effect on the structural formation of the width and depth of the recesses together with the choice of the bearing material for the load-bearing layer * 10 83693 and the filler for the grooved recesses. In this way, the longevity and wear resistance of the plain bearing can be influenced in the most advantageous way. The use of different materials for the base course and different fillers thus require different sizing of the recesses. The properties of these materials in this regard have been described above.

Experiments have shown that by following the sizing instructions for the above grooved recesses 10, optimal results have been obtained in terms of the longevity, wear resistance and emergency use of the plain bearing.

The grooved recesses can be formed as closed annular grooves, however, the most preferred way is to make the annular recesses screw-shaped.

As can be seen from the magnification of the area 5 of Figure 1 shown in Figure 5, the plain bearing material 20 for filling the grooved recesses 26 can be placed in regular ribs or fields 29 to form a closed layer 30. A diffusion barrier or bonding layer 31 having a thickness of 0.5-4 .mu.m can be placed between the sliding material forming the carrier layer 27 and the material filling the grooved recesses 26 and possibly forming the sliding layer 30. The magnification of the area 4 of Fig. 1 shown in Fig. 4 25 shows an alternative solution in which the sliding layer 30 or the filling of the grooved recesses 26 is formed by means of interconnected ribs 29.

As further shown in Figures 4 and 5, the support layer 27 is attached 30 to a suitable substrate 32, for example a steel flange or housing.

The shape of the grooved recesses can be changed, for example, by making them crosswise, whereby diamond-shaped or otherwise rectangular fields 29 are formed between the recesses 26, as shown in Fig. 7. In addition to the cross-section, the grooved recesses 26 can also be provided with transverse grooves 26a to form triangular regular fields 11,83693 as shown in Fig. 8. The opposite distances of the transverse groove recesses 26 are shown in Figures 7 and 8 as equal. However, it is possible to use a different groove distance in one group of recesses 26 than in the groove group 26 crossing it 5.

Fig. 9 shows an annular bearing flange 22a provided in its radial bearing part with a sliding surface 25, the bearing layer 27 of which has grooved recesses 26. Also formed in the bearing layer 27 of the ring 35 are grooved grooves 26, which in this embodiment are helical, i.e. circumferentially expandable. In this example, the grooved recesses 26 could also be formed concentric with the central axis of the bearing. Like the radial bearing part, the grooved recesses 26 in the ring 35 are also filled with a plain bearing material 15a, so that this bearing material can still cover the ribs or fields formed between the grooved recesses. The second ring 36 of the annular bearing flange 22 according to Fig. 9 can be formed like the first ring or also in its conventional bearing layer on a smooth upper surface. To form a complete plain bearing, an annular bearing flange according to Fig. 9 is placed on another annular bearing flange, which may be similar to the flange shown in Fig. 9 or formed in a conventional manner.

In a similar or similar manner to the one-piece ring bearing 25 22a, a plain bearing can also be formed in which the ring flanges are separate spacer plates 38 and 39 placed directly on the radial bearing portion by means of connecting plates.

The example according to Fig. 10 is directed to a bearing structure in which the spherical bearing part is formed by two plain bearing flanges 21 and 22 (Fig. 1). The plain bearing flanges 22 include a sliding surface 25 provided with a bearing layer having grooved recesses 26. Separately from this radial bearing part, axial bearing parts and spacers 38 and 39 are placed at a lateral distance from the side edges of the radial bearing part 35 in the bearing structure. The bearing layer of the intermediate plate 38 or both intermediate plates 38 and 39 has grooved recesses i2 83 693 arranged concentrically with the central axis of the bearing. Helix-like grooved recesses could also be used in this context.

In all such application examples, different combinations of plain bearing material can be used, for example the support layer 27 can be made of lead bronze. The sliding bearing material filling the grooved recesses 26 may be a white metal bearing alloy, it is most preferred to use a zinc-antimony alloy of the SnSb7 type in this connection.

Instead of the sliding layer 30 shown in Fig. 4, the solid ribs or fields 29 can also be coated with a layer made of lead-zinc alloy or zinc-anti-alloy with a thickness of 0.5-2.

As another preferred material solution in the plain bearing flange 22 15 or housing 23, an arrangement may be used in which the support layer 27 is made of an aluminum alloy, preferably AlZn4,5SiCuPbMg, and the grooved recesses are filled with a white metal-drug mixture, preferably based on PbSnCu. In such a case, a layer 31 of nickel or a mixture of copper and zinc is made of CuSn.

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Drawing markings 20 Plain bearing 21 Plain bearing flange 5 22 Plain bearing flange 22a Ring bearing flange 23 Plain bearing housing 24 Axial slot 25 Bearing running surface 10 26 Grooved recesses 32a Slotted grooves 26a Cross-grooves 31 Support layer 20 38 Spacer plate 39 Spacer plate a The distance between the center lines of the lanes. b Recess width s Bandwidth 25 t Recess depth

Claims (6)

A plain bearing element provided with a non-uniform sliding layer, comprising a protective layer and a bearing layer 5 made of a bearing material attached thereto, having substantially axially spaced groove-like recesses for example a radial plain bearing, the bearing layer of which is provided with grooved recesses filled with a plain bearing material extending over at least part of its area, characterized in that the groove width b of the recesses, the width s is more than 50 N / mm2 from the projected bearing surface (a) the groove width b [μπι] is equal to or less than, but preferably 20 is equal to p + 20. : b - 200 - (MX _. p + 12,5 25 where p - bearing specific load [N / mm2] b) the remaining bandwidth s [Mm] is equal to or greater than, but preferably equal to, 30 525 (p + 20 ) Smin “------- 118.06 + 9,652 · p + 6,528 · 10J · p 2 + 3,889 · 10 ° · p 3 35 c) the ratio between the width b of the recesses and the bandwidth s (b / s) M - (between 1.95 and 2.0) - (1.757 + 3.1-103 · p + 7.233-110-4 · p 2) 15 83693 2. A plain bearing element provided with a non-uniform sliding layer, comprising a protective layer and a bearing layer attached to it bearing a groove-like recess a radial plain bearing, the bearing layer 10 of which is provided with grooved recesses filled with a plain bearing material extending over at least part of its area, characterized in that the groove width b of the recesses, the width s of the strips between the recesses and the is less than 35 N / mm2 from the projected bearing surface annealed as follows: a) the width b [/ tm] of the grooved recesses is equal to or greater than, but preferably equal to, 20 'p + 20 - 56.25 —- P + 12.5 25 b) the remaining bandwidth s [/ im] is equal to or less than, but preferably equal to, 2050 (p + 20) - ------- 30 118.06 + 9.652 · p + 6.528 · 102 · p 2 + 3.889 · 103 · p 3 c ) the ratio between the groove width b and the bandwidth s 35 (b / s) ^ - (between 0.5-0.55) - (0.5100 + 0.9103 · p + 2.1-10 ^ · p 2) 3. A plain bearing element provided with a non-uniform sliding layer, comprising a protective layer and a bearing layer made of bearing material 16 83693, having substantially axially spaced groove-filled grooves , for example a radial plain bearing, the bearing layer of which is provided with grooved recesses filled with at least part of its area of plain bearing material, characterized in that the the measurability is about 30-55 N / mm2 of the projected bearing pin is determined as follows: 15 a) the width b [/ im] of the grooved recesses is smaller or larger, but preferably equal to p + 20 btak - 75 —- 20 p + 12.5 b) the remaining bandwidth s [μιη] is less than or greater than, but preferably equal to, 25 750 (p + 20) ^ keak "* _ __ _ 118.06 +9.652 · p + 6.528 · 10 * · p 2 + 3.889 · 103 p 3 c) the ratio between the groove width b and the bandwidth s 30 (b / s) ta.k - 0.9444 + 1.6667 · 10 * p + 3.8889 · 10- * · p 2 Plain bearing element according to one of Claims 1 to 3, characterized in that the groove depth t [μπι] 35 of the grooved recesses and the ratio between the groove width b of the grooved recesses and the groove depth t for high-load-bearing plain bearing materials 8 for filling grooved recesses greater than 40 N / mm2 from the projected bearing surface, is determined as follows: d) the groove depth t [pm] is equal to or less, but preferably 5 is equal to 1350 tn-x - 1 and 10 p + 12.5 e ) ratio between the groove width b of the groove-like recesses and the groove depth t (b / t) ^ - 4,167 · ΙΟ'2 p + 0,8333 Plain bearing element according to one of Claims 1 to 3, characterized in that the groove depth t [μm] of the grooved recesses and the ratio between the groove width s and the groove depth t of the grooved recesses for low-load-bearing plain bearing materials for filling grooved recesses with a load capacity of less than 20 25 N / mm2 from the projected bearing surface, is determined as follows: d) the groove depth t [pm] is equal to or greater than, but preferably equal to, 25,900 tmin ”-Z- JS p + 12.5 30 e) the ratio of the groove width b of the recesses to the groove depth t (b / t) ^ - (between 1.95-2.0) (10.834 · 102 · p + 2.1666). Plain bearing element according to one of Claims 1 to 3, characterized in that the groove depth t [μm] of the grooved recesses and the ratio between the groove width s and the groove depth t of the grooved recesses for medium-load-bearing plain bearing materials for filling grooved recesses with a load capacity of approx. -45 N / mm2 from the projected bearing surface, is determined as follows: d) the groove depth t [pm] of the recesses is either smaller or larger, but preferably equal to 1125 ttak --—- And P + 12.5 10 e) the ratio of the groove width b of the recesses to the groove depth t (b / t) ^ = 6,667 · ΙΟ'2 · p + 1,333. 15 i9 83693