FI118740B - Sliding bearing and procedure for its use - Google Patents

Description

118740

The present invention relates to a plain bearing according to the preamble of claim 1, which may have a variable number of sliding surfaces 5 on top of one another, as well as a method for operating a plain bearing.

Known plain bearings generally have one bearing interval. Therefore, the sliding velocity between the two sliding surfaces hydrodynamically lubricated with a low friction coefficient of about 0.002-0.0045 is limited to a sliding 10 velocity range of 0.5-5 m / s. In this case, the perfect low friction coefficient for hydrodynamic lubrication at a low slip range of 0.05-0.5 m / s cannot be achieved, but lubrication is more sensitive to mixed friction lubrication. The viscosity of the oil increases the coefficient of friction at high sliding speeds in the hydrodynamic sliding range of 5-50 m / s and above 15. On the other hand, if a low viscosity fluid, such as water, is used, it is difficult to start the bearing, and it is possible due to mixed lubrication.

An alternative to hydrodynamic lubrication is hydrostatic lubrication, where *; ··: 20 lubrication film is produced by a hydraulic pump-produced: * ·· lubricating fluid pressure at the pressurized contact point of the sliding surfaces. ... f This produces a load bearing lubricant film as in hydrodynamic s "*: lubrication but at low slip speeds 0-7 m / s with low friction coefficient, and avoids mixed lubrication. Slip range 7-. · **. 25 50 m / s still with higher friction coefficient hydrodynamic Also, the pressure of the fluid in the static bearing must be at least equal to the load per square millimeter, thus consuming energy.

Other known bearings do not achieve high bearing capacities with respect to size: V 30, but the coefficient of friction can be very low even at full speed -:, ***: in the range 0-50 m / s , eg hydrodynamic gas bearings (though: · ·, do not operate at low speed), static gas bearings and magnetic • · f !!!. These special types of bearings are expensive, not to mention size.

The bearing of GB 2021701A, which utilizes a floating sleeve, acts as a crankshaft bearing on which a rotary cranking roll is caused by the crank cam 35 118740 2. However, this is not the case in normal bearing applications where the load direction is the same.

DE 35 37 449 A1 discloses a lubrication which is quite effective 5 because it has a continuous oil lubrication through the floating bearing sleeve (holes 27) which distributes the lubricating oil everywhere and the heat is well transferred with the oil.

EP 0 021 738 B1 also discloses a lubrication solution of almost the same type. The publication has a speed of 150,000k / min. The figure 10 of my publication 10 typically has an inner diameter of sleeve 17 and 18 of 9-13 mm and a sliding speed of more than 70-100 m / s and a total sliding speed of more than 100 m / s. The inside and outside of the sleeve have a sliding clearance of 0.05-0.077 mm, which is quite large compared to the diameter. Here, simultaneous sliding of both slides is possible due to high friction coefficients and 15 simultaneous very low load pressures. At a pressure of about 0.25 N / square millimeter, the sliding intervals may slip if the coefficient of friction is 0.025. During the start-up phase, the bearing operates differently from normal running, ie, it slides on the sliding surfaces. First, the inside slider of the sleeve slides out because it has a smaller diameter and thus requires 20 smaller torques. As the sliding speed increases, the friction coefficient also rises from about 0.018 to 0.025 and causes the outer ring of the sleeve to move. The low-friction start-up friction is already reduced because of the fact that there is always vibration and axial eccentricity, whereby "the two sliding surfaces slide simultaneously and the coefficient of friction drops between about» · '· * 25 0.016-0.022 but remains two slides · * ... · * do not work at sliding speeds of 1.2 to 10 m / s and load pressures of * ·. * ·: 1.5 to 16 N / mm2 on sliding surfaces.

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The object of the invention is to eliminate these disadvantages and to provide; Y; 30 plain bearing with varying number of bearing spacing which. * ··. most commonly are formed by opposing sliding surfaces. The sliding bearing according to the invention is characterized in what is stated in the characterizing part of * ί '*: claim 1. The second bearing spacing at a radial distance from the bearing section of the rotatable part has a lower frictional torque and • ·. ··. at rest and up to a certain sliding speed in motion, and so this second bearing interval first sets off. By moving the bearing clearance 118740 3, it is meant that its opposite surfaces start to move relative to one another, in particular with one surface in place and the other being substantially concentric with the axis of rotation. The bearing interval included in the rotatable part can then perform a lubrication lubrication due to a second movable bearing interval which is radially spaced from the bearing distance of the rotatable part.

If the rotatable part is in the center of the sliding bearing, i.e. in the case of a rotating shaft 10, for example, a shaft connected to a motor drive or other power take-off, the gently moving bearing gap is radially outward. If the rotatable part is outside the sliding bearing, i.e., the part which is rotatable on the fixed shaft, the bearing which is easily movable is radially inward. Because of the smaller diameter, the inner bearing interval also has a smaller starting torque in this latter case.

The more sliding surfaces in the squeeze roll, the higher the total sliding speed 20 can be obtained with a low friction coefficient. wear; * ·· It is distributed on most sliding surfaces and it does not matter because of the low friction and sliding speed. Wear on Squeegee Lubricant surfaces is also low, since there is no need to fear mixed adhesion due to adhesion, which allows for stronger lubricant • · 25 materials and lower viscosity with lubricating fluid than with dynamic lubrication in general. An attempt is made to maintain the sliding velocity between the two sliding surfaces in the range of about 0.6-20 m / s, depending on the lubricant and the desired friction coefficient.

FV 30 The invention will now be described in more detail with reference to the enclosed silicon: *** cartridges in which: •; Figures 1, 2 and 3 are partial sectional views of bearings; Figures 4 and 5 are full-sectioned bearings, Fig. 4 is an enlarged view of S 3 of Fig. 3; Fig. 6 is a Figures 9 to 9 show prior art lubrication methods, and 5 Figures 10 and 11 illustrate lubrication methods according to the invention.

In the following description, reference will be made at various points to the curves of Figure 6, of which curve 1 represents a rolling bearing, curve 2 a sliding surface of an elastic fluorine rubber 10 coating, a curve 3 of a lead bronze sliding surface and a curve 4 of polytetrafluoroethylene (PTFE, Teflon®). The curve is made of a 76.4 mm diameter 60 mm wide plain bearing with a load pressure of 12,600 N (approx. 1280 kg), i.e. an effective pressure surface of 29.2 cm 2, and a pressure of 15 slides of 432 N per square centimeter. The rolling bearing of curve 1 uses a rolling bearing for a corresponding load. For coatings, the coating thickness has been about 0.5-1 mm. Synthetic lubricant 5 W - 50, heat 323 K (+ 50 ° C) between sliding surfaces.

Fig. 7 shows, by way of example, one special case of lubrication of rotating parts: If the piston is loaded in both directions, a frictional squeezing effect due to the reciprocal loading pressure will be generated ...: ***. A portion 35 is mounted around the crank shaft palm 8 of the connecting rod. Due to the movement of the connecting rod, its bearing surface 25 does not rotate much, but the crank shaft pin 8, on its sliding surfaces, rotates once each revolution, i.e. rotates (arrow 36). A and B display continuously. · .. rotation of repetitive stages. Bearing clearance is denoted by reference numeral 37. Fig. 8 shows a hydrodynamic lubrication, where ·; · * as shaft 8 rotates with respect to fixed part 35, a lubricant | * V 30 engulfing area V is pumped to pump lubricant to shaft 8 and wedge-shaped outer periphery 35; or a gap. This requires a certain minimum sliding speed of 0.6 m / s in order for hydrodynamic lubrication to work with low friction. In practice, the bearing is not dared to operate anywhere near the minimum speed due to the fear that the 35 bearings will close and, as a result, a low friction value will not be achieved. Fig. 9 shows a known hydrostatic lubrication in which the pressure of the lubricating fluid is introduced into the bearing gap through a channel 41.

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Since an ordinary sliding bearing has an oil lubricated only in the middle range of 0.5 to 5 m / s, an oil lubricated area with a lower friction coefficient of 0.001-0.0045 (Figure 6 range 32-31 curve 3), it is sought to arrange the sliding intervals . One surface of the highly rotatable bearing gap is secured to a non-rotatable body and the other surface is the outer surface of a gently rotating sleeve or the like (in the case where the rotating part is the center axis of the bearing or the like).

10

Figures 10 and 11 show a simplified principle of a bearing according to the invention. The advantages of stationary thrust rolling (Fig. 10) and the resulting thrust lubrication (Fig. 11) are that the thrust lubrication method results in an almost identical hydrostatic lubrication (Fig. 9). The squeeze roll causes the distance difference between the surfaces π x the sliding clearance per revolution, which is a short distance, but the sliding surfaces remain functional and in motion even at very low rotational speeds. The squeeze roll begins immediately after the more sensitive outward bearing spacing (with the movable surface 20 being the outer surface of the sleeve 42) has started due to its smaller * · l * ·· frictional moment.

··· * ···

There are two moving surfaces simultaneously in the same direction ···: * · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · · When the opposing surfaces move in the same direction at the same speed, the shaft surface rises over the lubricant film when the surfaces reach, i.e., a certain velocity that is significantly lower than the '.'. 7 hydrodynamic lubrication with only one surface moving. .

···: * · *: 30 Figure 11 illustrates such a press lubrication when the shaft 8 and the bushing 42, which is arranged to be rotatable, rotate at the same speed (arrows 43). \ e on both sides of the corresponding bearing clearance, ie surface speeds: are the same. This is typically created at a velocity of 0.2-0.4 m / s, whereby the intermediate lubricant does not escape between the surfaces, but forms a lubricating film on the contact side of the surfaces. Due to the constant load direction P, the squeezing lubricating groove 38 between the outer surface of the shaft 8 and the inner surface of the sleeve 42, as well as the rolling point and the impact area V of the squeezing 118740 6 in front thereof, remain in place. The surface velocity at which the lubricating film is formed is less than half (about 0.3 m / s) of the hydrodynamic limit velocity represented in Fig. 6 by point 32 of curve 3, whereby the minimum velocity is 0.6 m / s.

5

The sliding surface rises on the supporting fluid film (Fig. 11) due to a squeezing lubrication interval V formed by moving surfaces in the same direction, thereby achieving an almost frictionless state like hydrostatic lubrication. As the velocity increases, a velocity difference is created on the surfaces. If the relative sliding velocity of the surfaces 10 is still low, 0.05-0.1 m / s, the coefficient of friction is also low, of the order of 0.001, but the sliding velocity increases with the same torque than the gently rotating circumference. As the velocity increases, the situation resembles more hydrodynamic as the thrust roller effect continues (both surfaces move further, now at different speeds). If the bearing has more than two radially spaced slots, the slider roller roller speed increases toward the rotating shaft.

Bearing spacing of the opposed surfaces of the left, moving to each other :: · · * 20 relative to the direction of arrow 44 (Figure 11) is positive (the same direction). '·· lubrication is enhanced, if the speed of the shaft 8 increases, the lubricant deteriorates or if the slow speed of the shaft 8 (Figure 11 arrow 45 (negative lubrication). In this case, the lubricating film is dropped off and the surfaces continue to blend with each other. Only when .···! With 25 squeeze lubrication, the speed of rotation of the shaft 8 is greater than 0.6 m / s, it is possible to remain on the lubricating film even if the speed of the shaft 8 relative to the sleeve 42 is slightly negative (arrow 45). There is not much difference in the velocity of Acse-8 in hydrostatic and fast positive ramming lubrication, but the faster the surfaces move relative to each other: the closer the hydrodynamic lubrication method is.

«« · • ·. \ Note that the squeeze roll is a continuous operation and starts with • i ·; load pressure and bearing play as soon as the two *! ”! a bumpy surface of radially equal size rotates nested 35 in the same direction. In the situation of Fig. 11, the load-bearing capacity of the film is proportional to the load pressure and not merely to the sliding speed. However, sliding speed or pushing roll speed has the most impact on load capacity.

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In the following, the differences in bearing diameters that affect the friction torque are ignored and the comparison is made solely by the friction coefficients. For example, if Fig. 6 is a slip velocity of 3.2 m / s, its friction coefficient is 0.0039 for lead bronze (curve 3) and 158 W for frictional and load losses. If the bearing has similar sliding surfaces facing each other which form three slits, where the relative velocities between each of the surfaces are the same as 10 above, the total slip rate is 3.2x3 = 9.6 m / s and the losses are 3x 158 = 474 W. Calculate the gently rotating sliding distance (bearing gap) to provide a thrust roll and thus also squeegee lubrication (Fig. 6, curve 2) to balance it with squeegee lubricated surfaces. The friction coefficient 0.0039 of curve 2 gives a sliding speed of 4.1 m / s and a loss of 202 W. Thus, the bearing assembly can have 9.6 + 4.1 = 13.7 m / s and the total loss 474 + 202 = 676 W. /B. For example, a standard plain bearing with only one bearing interval would have a friction coefficient of about 0.006 and a loss of 1027 W (35 W / square centimeter) at the same total sliding speed of 13.7 m / s (as determined from the outside of curve 3 in Figure 6).

The heat loss values of the multi-slip bearing are thus reduced by 52%, and. . ·. also (as in Example 676 W), is distributed over each slope, ie, · · · .I, ”the heat loss is only 5.8 W / h per square centimeter, and the lubricant: 7 circulates and cools. The revolutions are at a total speed of 13.7 m / s ** · · ;;; 25 (axis surface speed) then 60 x (13.7 / (0.0764 m χ π)) = 3427 rpm.

• · * * »*» · • · 44 «

In theory, for example, nine concentric sliding sleeves achieve an axial velocity of 50 m / s at the inner surface of the innermost bearing clearance 30 (shaft) 50 m / s: ***: relative bearing sliding bearing gap · 10 bearing intervals · · ·. sliding simultaneously, resulting in a total bearing velocity of 50 m / s for the bearing 77, but the coefficient of friction remains below 0.0045. It should also be noted that * ·; ·: the sliding surface of the inner sleeve opposite the shaft has a velocity n.

: * · *: 35 45 m / s. With such a bearing, for example, at a low sliding speed of 0.3 m / s, ***: no benefit in the number of sleeves, but only the outer circumference ··· rotates due to its delicate motion.

118740 8

The highly sliding circumference may also be provided with a hydrostatic sliding bearing ring which would then operate on the same principle as in Fig. 9 but would not be between the shaft and the sleeve, but between the outer sleeve 5 and the body. However, the hydrostatic lubrication pressure energy is high, but on the other hand the load pressure may also be high. A bearing with a fluorine rubber or similar sliding surface on an elastic base and possibly a partial hydrostatic lubrication (Fig. 6, curve 34) saves the pressurized oil and, at the same time, the pumping energy. At the same time, the coefficient of friction can be 0.001-0.0042 at 0-5 m / s. Water can also be used as a lubricant in the rubber-coated slider, but then all operating values change.

The following describes some of the bearing structure-15 solutions of the invention in more detail.

In Fig. 1, the sleeve or ring denoted by the numeral 16 or the outer periphery or in Figs. 2, 3 and 5 the sleeve or ring or the outer circumference denoted by the numerals 6 are responsively rotated with respect to the fixed part (Fig. cause a ram roll to the inner bearing clearance (outermost in Fig. 5) if the shaft 8 rotates and • · «is the load pressure (arrow P).

· · ·

The highly rotatable outer periphery (sleeve 16) in Fig. 1 assists in rotation of concentric rings 7 and 48 with shaft 8 therein. The outer bearing spacing here is made with a gently moving * ··· '' roller bearing. The gently rotating outer periphery 6, i.e. the sleeve, of Figs. 2 and 3 helps to rotate within it with the axis 8 of the ring 7. The outer bearing spacing here is realized by the material choices of the opposing sliding surfaces 30. This creates a situation where the bearing shaft 8: ·! ·. due to the load applied to the tires, the tires • · get quite a friction on the sunken surfaces, and on the opposite side of the load effect **: * '(in the direction of load «· · in Fig. 5) the surfaces open up to the bearing clearance *: · * : 35 gives a gap to allow the lubricant to penetrate (clearance 13 in Figures 1, 2, 3 and 5). The bearing play 13 remains in place because the direction of load action (arrow P) is the same.

118740 9

2 is a sectional view taken along line 25 of the upper image. The support member 12 also functions as a fastening member which also centers the shoulder sleeve 6 and acts as a sliding surface, and passes the lubricating fluid.

5 The bearing also has a support member 10 which acts as a sliding surface against the sleeve 6 and allows the lubricant to pass. The support member 11, which acts as a sliding surface against the sleeve 7, is attached to the end 8 of the rotating shaft. The low pressure lubrication hole for introducing the lubricant is indicated by reference numeral 5 in the figures. Figures 1, 2 and 3 show radially penetrating holes 9 in the rings or bushings 10 distributed along the periphery of the rolling pulley rings 7 and 48 and in the highly rotatable rim 16 and 6 to provide sufficient lubricant to continue to penetrate well into the pulley slots 13, 22 and 23. The edges of the holes 9 are rounded. If the holes are missing, the lubricant penetrates the lubrication 15 into the slots 13 and 23 at the end of the rings (Fig. 5). The lubricant exits the slot 15 in Figure 2.

In Figure 2, the solid outer periphery 2 of the outer bearing gap, and in Figure 3, body 1 or Figure 5, part 27 may be steel, cast iron or aluminum or the like with an elastic fluorine rubber layer or fluorine elastomer (FPM, FKM) attached thereto. acrylate rubber (IF 4) by gluing or vulcanization (layer 3 and:. This material has a sliding frictional property such that it provides a lower resting frictional torque at the start, can be placed at the appropriate position; The surface may be of the aforementioned fluorine rubber alone or provided with an elastic (more elastic) rubber base material. Alternatively, as shown in Figure 4, a thin fluoropolymer film is glued or vulcanized on the elastic base layer 3 \ '\ · 30: ·! ·. 24, thickness 0.01-0.5 mm, if the elastic rubber material of the base layer 3 has lower friction, heat resistance and wear properties, but better elasticity than the surface material. For bonding or vulcanization, a bonding layer 26 *: ··: 35 may also be used, which may be a thin steel film or other strong fibrous bandage, 0.01-0.5 mm thick. This support layer is attached to the binder or the like fluorikumikerrokseen layer 24, and the elastic base layer 10 118 740 3 to the other side of the base binder layer. The thickness of the layers 3, 26 and 24 may be 0.05-6 mm. More precisely, the thickness is from 1: 1000 to 1:50 of the diameter or length of the sliding surface thereof, if the length is greater than the diameter.

5

Hole 14 of Figure 2 illustrates a hydrostatic pressure inlet. There may be two or more holes. At high load pressures while the shaft is still stationary (Fig. 6, curve 34), lubrication can then be performed partially hydrostatically using an external monitoring unit that accurately controls that the gently rotating ring 6 rotates during start-up and regulates hydrostatic pressure in the outer bearing gap .

In Figure 1, the inner circumference 16 of the rolling bearing acts as a highly rotatable outer circumference 15 which, with the rolling elements, forms a bearing gap having a lower resting friction moment than the other inner bearing intervals (slides) and causes a thrust roll to the inner sliding surfaces. The roller bearing here is a spherical roller bearing with a roller frame 47 between the rings 19, 16 having 20 fastened roller rollers 29 between the rings 46. and 20 into a single assembly to form conical thrust rolling surfaces on both sides that are resistant to partial axial '; · *! 25 loads. Alternatively, the innermost, with the outer surface of the shaft 8, can be locked non-rotatable by squeezing the ring 48 onto the shaft 8 without sliding clearance, thereby losing one slip (squeegee lubrication gap) but causing the bearing to be axially guided (axial surfaces 49).

The invention also encompasses a bearing according to Fig. 1 which does not have sliding rings 7 and 48, leaving only a rolling bearing and one * ·: · * slider between its inner periphery 16 and the shaft 8. The shaft 8 is not locked on the inner circumference of the rolling bearing, but is slidable. Here, too: ·: ··: 35 is a gently moving bearing spacing (roller bearing) and a slider inside where the aforementioned thrust lubrication effects occur.

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Figure 5 shows the bearing of the shaft end. The structure differs from the other in that it has a fixed part in the center (a spherical surface 27 attached to the frame 1) and an outwardly rotating shaft 8. The inner surface of the intermediate sleeve or ring 6 is shaped according to the spherical shape of the part 27.

5 The ball-joint design allows the shaft 8 to be angled. The shaft end may also be more cup-shaped, as shown by the line 50 representing the cut-off point.

The rings 6, 7, 48 and shaft 8 of Figures 1, 2, 3 and 5 are of ductile graphite, 10 of alloy steel or of hardened steel. Bronze and alloyed aluminum are also possible. These rings or the like may be coated with various coatings such as white metal, zinc, molybdenum, bronze, chromium, oxidation, nitrified surface, carbides, and nitrides (CVD). The ring 16 of Fig. 1 may also be coated on its inner periphery. It can be noted that in opposed lubrication, opposing and simultaneously moving surfaces do not require good mixed lubricating properties and therefore their surfaces may be of hard material, e.g. even hardened steel.

In Figure 2, the continuation of the lubrication groove 28 in the circumferential direction is shown as a dotted line. In Fig. 3, the groove 21 is connected circumferentially: · to the hole forming the low pressure inlet 5 of the lubricant. In position 22 • Il * the rings are located at an angle to the shaft 8, i.e. the bearing also withstands a small \\ * axial load and also acts at this point with a squeeze roll, '; ·] 25 but the bearing is mainly dependent on radial load pressure' • 'i (arrow P). Figure 3 shows the free flow holes 18 of the lubricant fluid inside the shaft. In Figure 1, the low pressure inlet 5 of the lubricant is drilled into the outer periphery 19 and is intended to circulate oil 13 in intervals. · * ·: The end flanges 46 prevent oil from being wasted.

· "*. · 30 * · *:. \ M The low pressure inlet 5 through which the lubricating and cooling fluid enters can have a pressure of 0.5-10 bar. The bearing according to the invention can also function as a complete lubricant. inside: without low pressure lubrication, or: t: *: the lubricant is fed through a rotating shaft to the bearing Figures ·: ··: 35 generally P the direction of the load pressure which presses the shaft The lubricating surface may be cylindrical, conical or spherical 5.

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The invention also encompasses the idea that the bearing has the potential for hydrostatic lubrication. Hydrostatic lubrication can be used to provide a gently rolling bearing clearance, particularly the 5 outermost gap. Particularly on hard sliding surfaces, lower load friction and sensitive motion are otherwise difficult to achieve when higher load pressures are desired. Hydrostatic lubrication can be on when the rotation is started and the end when a certain speed is exceeded. Lubrication can be restarted when the rotation speed drops below a certain value 10, whereupon the lubricant pump connected to the bearing interval is restarted. This operation may be automatic in that the device is equipped with a rotational speed sensor which continuously monitors the rotational speed and causes the pump to start or stop if necessary.

The bearing according to the invention is suitable for devices with a long service life and in which the operating energy of the device is relatively expensive to lose. The bearing is also suitable for a location where a normal sliding bearing or a rolling bearing cannot be used due to its high sliding speed, or it has a very short service life due to wear. Also, the use of a fluorine rubber surface 20 is economical if the position is such that a normal rolling bearing that cannot withstand impact stress or waterproof bearing surfaces is required.

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Claims (9)

118740 A sliding bearing having at least two concentric circular circumferential bearing spacings between two relatively rotatable portions (1, 8) 5 for providing radial bearing, of which at least one bearing spacer is a slider and the second sliding surface of this slider is characterized in that (8) a second bearing interval (2-6; 19-16) radially spaced from said sliding gap (7-8; 48-8) having one surface included in the rotatable member (8) having a lower resting friction torque such that it first moves when both surfaces of the aforementioned slider (7-8), one of which is part of a rotatable member (8), initially moving at substantially the same peripheral speed, and that the sliding bearing has a low pressure lubrication hole 15 (5) for introducing lubricant or bearing. A plain bearing according to claim 1, characterized in that the second surface of said second bearing means having a lower resting friction moment is fixed in the body or in a corresponding non-rotatable position (1; 19). • • « Sliding bearing according to Claim 1 or 2, characterized in that said second bearing having a lower resting friction moment *; ·: * 25 is provided by a rolling surface, by a sliding surface formed by an elastic coating, such as a fluorine rubber coating (24):. ** j , or with hydrostatic lubrication. ··· • · ♦ · Plain bearing according to any one of the preceding claims, characterized in that there is one between the two concentric bearing intervals. ···. or more bores (9) or the like for introducing lubricant ** between bearing intervals, or the bearing has an arrangement for introducing lubricant from the end or ends of the bearing intervals. • · • · ♦ ·· · *. ·; Slide bearing according to claim 3, characterized in that: ···. the elastic coating is a common elastic coating made of at least two different layers (24, 3) of elastic coating material, whereby a non-stretchable support layer (26), such as a metal film or mesh support layer, is optionally disposed between the layers 118740 (24, 3). Sliding bearing according to Claim 5, characterized in that the outermost elastic coating material of the sliding surface is stiffer than the elastic coating material inside. Sliding bearing according to one of the preceding claims 3, 5 or 6, characterized in that the elastic coating has a total thickness of 1: 1000 to 1:50 of the corresponding sliding surface diameter or the axial length of the sliding surface if the length is larger than the diameter, is between 0.05 and 6 mm. Sliding bearing according to one of the preceding claims, characterized in that it has three or more concentric bearing intervals. A method of using a bearing according to any one of the preceding claims, characterized in that a sleeve (6) is provided inside or outside the bearing gap by a gentle movement of a bearing gap having a lower friction torque such as a rolling surface or an elastic sliding surface; the sleeves (6, 7; 16, 7, 48) and the pivoting part (8) to rotate together such that the thrusting roll can be carried out in all ···: 25 other bearing intervals between them, allowed by the sliding clearance of these bearing intervals (13) ··· resulting in a thrust lubrication that continues ΟΙ even if the surfaces slide relative to one another on the lubricant film, and the lubricant is introduced into the bearing gaps by low pressure lubrication or by the bearing acting within the lubricant fluid. 30 • • • • 1 1 t · • • • • • • • • 1 1 t · • • • • • • • ••••••••• 118740