KR100244584B1 - Sliding bearing - Google Patents

Abstract

An object of the present invention is to provide a sliding bearing for low speed and high surface pressure that can slide without supplying grease for a long period of more than several years.

In addition, it has a bush (9) for supporting the shaft, the bush (9) is a sliding bearing made of a porous iron-based sintered material, the bush (9) is impregnated with a lubricant having a viscosity in the range of 260cSt ~ 950cSt Sliding bearing characterized in that. This sliding bearing is preferably used in an environment of a working surface pressure of 6.0 Kgf / mm 2 or more and a sliding speed within a range of 2 to 5 cm / sec.

Description

Sliding bearing

1 is a schematic cross-sectional view of an example of a sliding bearing assembly with an example of a sliding bearing of the present invention.

2 is a partially enlarged cross-sectional view of the sliding interface between the shaft and the bush in the sliding bearing assembly shown in FIG.

3 is a characteristic diagram showing the relationship between the surface pressure and the friction coefficient according to the type of viscosity of the lubricating oil impregnated in the bush in the sliding bearing of the present invention.

4 is a characteristic diagram comparing tribogie characteristics of a conventional grease supply type sliding bearing and a high viscosity lubricant impregnated sliding bearing of the present invention.

5 is a characteristic diagram showing the amount of wear of the bush when the sliding bearing of the present invention is continuously rocked over 800 hours.

6 is a characteristic diagram showing the amount of abrasion of the shaft when the sliding bearing of the present invention is continuously rocked over 800 hours.

7 is a chart showing the results of infrared spectroscopy analysis of a black high viscosity lubricating material, (a) is a chart of new and unused lubricant, and (b) is 100 hours of bush and shaft impregnated with lubricant. Chart of black high viscosity lubricant produced by sliding.

8 is a chart showing the oil components and solids separated from the black high viscosity lubricating substance, and dried and powdered and identified by X-ray analysis.

FIG. 9 is a waveform diagram of a result obtained by disassembling a sliding bearing in which black high-viscosity lubrication material is confirmed, and measuring a change in the sliding surface of the shaft 10 and the bush 9 with a stylus type coarse gauge, (a) Is a waveform diagram showing the surface roughness of the axis 10, (b) is a waveform diagram showing the surface roughness of the bush (9).

10 is a partial schematic cross-sectional view of another example of the sliding bearing of the present invention.

11 is a partial schematic cross-sectional view of still another example of the sliding bearing of the present invention.

12 is a partial schematic cross-sectional view of another example of the sliding bearing of the present invention.

13 is a schematic cross-sectional view of an example of a sliding bearing assembly with a conventional grease supplied sliding bearing.

14 is a partial schematic cross-sectional perspective view of an example of a conventional solid lubricant embedded bush.

<Explanation of symbols for main parts of drawing>

1: boss 2: conventional bush

3: dust seal 4: O-ring

5: shim 6: bracket

8: Rotating Stop Bolt 9: Bush

10: axis 12: member to block the oil

14: pore 16: high viscosity lubricant

18: oil film 20: grouting part

22: wear-resistant plate 24: high strength bush

30 grease supply hole 32 sealing plug

34 Grease 36 Graphite

The present invention relates to a sliding bearing. More specifically, the present invention relates to a low-speed, high surface pressure sliding bearing capable of sliding without supplying grease over a long period of time.

In an excavation device such as a construction machine, in order to operate the drive mechanism, the respective members constituting the drive mechanism are connected to each other in a rotatable or swingable manner and driven by a cylinder or other actuator. For example, in a hydraulic excavator, a basket is connected to the tip of the arm, but the excavation operation by the bucket causes the basket to pivot or swing about the connection with the arm by operating the bucket cylinder. For this reason, the bucket and the arm are connected by the bush for a sliding bearing provided in either of these, and the shaft inserted in this bush.

13 is a cross-sectional view of an example of a sliding bearing conventionally used. A conventional bush 2 for sliding bearing is fitted inside the boss 1. The dust chamber 3 is press-fitted in the side outer periphery of a bush. Brackets 6 are provided on both sides of the boss 1, and a shim 5 is interposed between the bosses 1 and the bracket 6. And the O-ring 4 was attached to the outside of the upper end of the space | interval between these. The shaft 7 is inserted through the bracket 6 at both ends and the conventional bush 2. The shaft 7 is made impossible to rotate by the rotation stop bolt 8 which penetrates this shaft and the bracket 6. The grease supply hole 30 is provided toward the substantially center portion of the conventional bush 2 at the side end of the shaft opposite to the mounting position of the rotation stop bolt 8. At one end of the grease supply hole 30, a sealing stopper 32 is attached. Grease 34 is filled in the grease supply hole 30.

In the excavation work, the bush and shaft for sliding bearings slide at a low speed, but require extremely large surface pressure. For this reason, in such a sliding bearing for high surface pressure, if the lubricating oil, such as grease, is not fully interposed in the sliding surface, it will burn early, eaten up, and wears out unevenly. Therefore, it is necessary to supply frequently, but this supply work is not so easy.

In addition, to supply new grease, the liquefied old grease in the bearing must be discharged out of the bearing. This supply and discharge generally takes place at sites where excavation work is being carried out. In this case, the discharged liquefied grease is scattered around the site's soil surface and discarded, causing problems of soil pollution. In recent years, the disposal of liquefied grease on the soil surface or discarded in various places in the construction of land and gardening in urban areas becomes a problem from the viewpoint of environmental protection.

As a means for maintaining lubricity on the sliding surface even without supplying lubricant such as grease over a long period of time, a solid lubricant such as graphite 36 is embedded in the sliding surface of the conventional bush 2 as shown in FIG. The bush itself is formed from a plastic material having self-lubricating properties, or as a special one, magnetic bearings or air bearings have been developed. However, magnetic bearings and air bearings are not suitable for high load bearings. On the other hand, bearings using solid lubricants (eg graphite) or self-lubricating members (eg plastics) also have various drawbacks. For example, in the case of bearings using a solid lubricant, there is a contact between the base metals and a visual "eat-eat" occurs. In addition, self-lubricating members such as plastics may cause sudden abnormal wear or deformation (creeping) due to lack of strength and hardness.

It is therefore an object of the present invention to provide a sliding bearing assembly for low speed, high surface pressure that can slide without supplying grease over a long period of time over several years.

In order to solve the above problems, in the present invention, the bush has a bush supporting the shaft, and the bush is impregnated with a lubricant having a viscosity within the range of 260 to 950 cSt in the sliding bearing made of a porous iron-based sintered material. Provided is a sliding bearing characterized in that.

The sliding bearing of the present invention is preferably used in an environment of a sliding surface speed of 6.0 Kgf / mm 2 or more and a sliding speed within a range of 2 to 5 cm / sec.

As described above, the sliding bearing of the present invention can be continuously used without supplying grease for a long time (for example, 5 years or more) even under low speed and high surface pressure by impregnating the porous bush with high viscosity lubricant. have.

Japanese Unexamined Patent Publication No. 63-60247 discloses a plurality of inclined grooves formed in a shaft hole of a bearing metal (corresponding to a porous bush in the present invention) for interleaving the shaft freely and including the shaft and the groove. A dynamic pressure bearing with lubricating oil interposed between a shaft hole is disclosed. The bearing metal is made of porous small alloy alloy, and impregnates the oil having a kinematic viscosity of 1000 C / S equivalent to the porous portion of the small alloy, and at the same time as the lubricating oil between the shaft and the shaft hole, The same kind and fluid film are formed through the grease of the same dynamic viscosity. In this dynamic bearing, the lubrication function is achieved by the oil of the bearing metal at the time of rotation start of the shaft which does not cause the dynamic pressure action, and after starting, the fluid film by grease is formed and the shaft is supported in the non-contact state by this dynamic pressure action. . As described above, in the dynamic bearing described in Japanese Patent Application Laid-Open No. 63-60247, the dynamic pressure action by the fluid film of grease exhibits a major lubrication action, and the lubricating oil impregnated in the bearing metal can achieve only such a lubrication function. On the other hand, it is not necessary to use grease in the bearing of this invention, and all the lubrication actions are performed only with the lubricating oil which has a viscosity within the range of 260-950 cSt impregnated to a porous bush. Since the grease does not need to be used in the bearing of the present invention, it is not necessary to form a groove or the like for forming a grease fluid film in the shaft hole of the porous bush.

The following describes the sliding bearing of the present invention in detail with reference to the drawings.

1 is a cross-sectional view of one example of a bearing assembly with a sliding bearing of the present invention. The basic configuration of the sliding bearing of the present invention is the same as that of the sliding bearing shown in FIG. Therefore, the same members as those in FIG. 14 will be described with the same reference numerals. Also in the sliding bearing of the present invention shown in FIG. 1, the bush 9 is fitted inside the boss 1. Brackets 6 are provided on both sides of the boss 1, and a shim 5 is interposed between the bosses 1 and the bracket 6. The O-ring 4 is attached to the outside of the upper end of the gap therebetween. The shaft 10 is inserted through the bracket 6 and the bush 9 at both ends. The shaft 10 is not rotatable by the rotation stop bolt 8 penetrating the shaft and the bracket 6.

The bush 9 constituting the sliding bearing of the present invention is a porous composite sintered alloy formed of, for example, copper powder and iron powder. Porous bushes made of other materials can also be used. It is preferable that the processing rate of this bush is about 5 to 30%. If the porosity is less than 5%, the impregnation amount of high viscosity lubricating oil becomes insufficient, and there is a fear that it cannot be used as a bearing which does not supply grease. On the other hand, if the porosity is higher than 30%, the mechanical strength of the bush itself becomes weak and there is a risk of destruction during use. Processing in the bush is preferably in communication with each other.

The porous bush is impregnated with a high viscosity lubricant having a viscosity in the range of 260 to 950 cSt. If the viscosity is less than 260 cSt, the fluidity of the lubricating oil is so high that it is difficult to fix it into the pores of the bush. On the other hand, in the case of lubricating oil having a viscosity of more than 950 cSt, it is very difficult to impregnate into the porous part of the bush, and even if it can be impregnated arbitrarily, the lubricant lubricated into the sliding part by the frictional heat becomes difficult to return to the porous part in the long term. There is a fear that the sliding characteristics cannot be maintained.

The lubricating oil impregnated into the porous bush is not particularly limited as long as its composition is within the above range. Any commercially available lubricating oil, such as mineral oil or synthetic oil, can be used. However, since grease contains fibers, it cannot be impregnated into the bush. The lubricating oil may be blended with solid lubricating fine particles having a particle diameter of 500 µm or less such as MoS ₂ , WS ₂ , hexagonal BN, graphite, or the like. These solid lubricating fine particles exhibit an effect when the sliding bearing of the present invention is used in a cold region.

When the porous bush of the present invention is impregnated with a high viscosity lubricating oil, the lubricating oil is heated to liquefy to a lower viscosity, and the bush is deposited in the liquefied lubricating oil and placed in a vacuum atmosphere. As a result, air in the pores of the bush is sucked out, and the liquefied lubricant is drawn into the pores of the bush instead. When the bush is removed from the air and left to room temperature, the liquefied lubricating oil is returned to the original high viscosity lubricating oil in the pores of the bush and loses fluidity. This allows high viscosity lubricants to gather into the processing of the bush. The heating temperature of the high viscosity lubricating oil is not particularly limited. The heating temperature changes with each viscosity. Therefore, what is necessary is just to heat until lubricating oil will liquefy. This is easy for a person skilled in the art. In addition, the deposition time and vacuum degree of the bush with the liquefied lubricating oil are not particularly stable. The deposition time and the degree of vacuum also depend on the viscosity of the lubricant used. The important thing is to deposit the bush into the liquefaction lubricant until the pores of the bush are saturated with the lubricant. As an example, when a 460cSt lubricating oil is heated to 60 to 80 ° C. and the bush is immersed in this lubricating oil under a vacuum of 2 × 10 ⁻² mmHg, the pores of the bush saturate with the lubricating oil in about 1 hour.

The sliding surface of the bush 9 is preferably subjected to surface modification by carburizing, nitriding or dipping. For example, when a carburized hardened layer having a thickness of 1 to 3 mm, preferably about 2 mm is formed on the sliding surface of the bush 9, the wear resistance of the bush can be improved.

The shaft 10 inserted into the bush 9 is made of steel, for example. After carburizing, nitriding and induction hardening of the steel shaft 10, it is preferable that the outer surface is subjected to surface modification by chemical conversion (for example, zinc phosphate, manganese phosphate, etc.) or by a distillation treatment method. Although the reason is not clear, the surface modification treatment of the shaft 10 improves the "wet" property of the high viscosity lubricant impregnated in the bush 9, thereby improving the lubricating effect and the tribolic property.

The boss 1 and the bush 9 can be fitted to each other by any method known to those skilled in the art. For example, it can be fitted to each other by shrinkage such as combustion or cooling.

2 is a partially enlarged cross-sectional view of an interface between the bush 9 and the shaft 10. As shown, the high viscosity lubricating oil 16 impregnated in the pores 14 of the porous bush 9 is expressed on the inner circumferential surface of the bush 9 to form a thin oil film 18. This oil film 18 becomes a sliding interface between the bush 9 and the shaft 10, and the lubricating effect is exhibited, so that excellent tribolic characteristics can be obtained. High viscosity lubricants impregnated in the pores of the bush are extremely low in fluidity and are not lost from the bush even when the bush and the shaft repeat their relative sliding. As a result, the oil film 18 is continuously supplied stably for an extremely long time. Thereby, the sliding bearing which does not supply the grease of this invention can be obtained reliably. In particular, the "pumping phenomenon" between the shaft 10 and the bushing 9 oscillating at low speed and high load is caused by micro metal contact, but according to the present invention, when the lubricant having a viscosity of 260 cSt to 950 cSt is impregnated, It is possible to eliminate the damage caused by being eaten away by the presence of the oily mass (oil film 18).

See Figure 1 again. The high viscosity lubricant impregnated with the bush 9 sometimes comes out of the sliding interface between the shaft 10 and the bush 9 beyond the sufficient supply necessary to form the oil film 18 (see FIG. 2). . This bleeding is considered to occur mainly because the lubricating oil expands due to frictional heat due to sliding between the shaft 10 and the bush 9 and the viscosity decreases slightly. When the liquefied lubricating oil leaks out of the bearing, it is not preferable because it causes not only the deterioration of tribolic characteristics between the shaft 10 and the bush 9 but also environmental pollution as in the case of the conventional grease. For this reason, in the sliding bearing of this invention, the member 12 which blocks oil is arrange | positioned at the both sides of the bush 9, and the dust chamber 3 is made to contact the member 12 which blocks this oil toward the bush 9. ) Is press-fitted between the shaft 10 and the boss 1. The oil blocking member 12 is preferably made of a material having elasticity as a soft material and sucking oil. Examples of the material suitable for this purpose include nonwoven fabrics, woven fabrics, porous elastic plastics, sponges, asbestos, felts, and the like. Felt is preferred in terms of cost, durability and oil sucking properties. The liquefied lubricating oil oozed from the bush 9 is absorbed into the felt in contact with the member blocking the oil of the felt when moving along the longitudinal direction of the shaft 10. As a result, liquefied lubricating oil is effectively prevented from leaking out of the bearing.

3 is a characteristic diagram showing the relationship between the surface pressure of the lubricant impregnated in the bush and the friction coefficient. The porosity of the porous composite alloy as described above is three bushes quenched and quenched at 15%, respectively, viscosity 230 cSt (Demitsu Dubnis gear 230 commercially available from Demitz Petroleum) and viscosity 360 cSt (available from Demitz Petroleum). The impregnated lubricating oil of Demitz Dubnisch gear 360 and viscosity 460cSt (Demitz Dubnisch gear 460 available from Demitz Petroleum) is impregnated in the same manner as above. The sliding bearing assembly was assembled, and the sliding bearing assembly was subjected to various values of surface pressure and measured at a resistance of 120 degrees while swinging at an angle of 120. As apparent from the results shown in FIG. Lubricant oil having a viscosity of 230 cSt is produced at a surface pressure of about 5 Kgf / mm 2. For 460cSt lubricants, even signs of scouring are not recognized at surface pressures above 10 Kgf / mm2.

4 is a characteristic diagram comparing the tribogie characteristics of the conventional grease supply type sliding bearing and the high viscosity lubricating oil impregnated sliding bearing of the present invention. The conventional grease supplied sliding bearing used a sliding bearing assembly having a configuration as shown in FIG. S45C high frequency quenched steel was used for the shaft 7, and the same S45C high frequency quenched steel was used for the conventional bush 2. In Greece, Douboniconex EPNo.2, which is commercially available from Demitsu Hongsan Corporation, was used. Meanwhile, the high viscosity lubricating oil-impregnated sliding bearing of the present invention used a sliding bearing assembly as shown in FIG. S45C high frequency quenched steel was used for the shaft 10, and bush 9 was used for the carburized quenched bush having a porosity of 15% made of porous composite small alloy (Fe / Cu). The bush was impregnated with a lubricating oil having a viscosity of 460 cSt (using the Demitz Dubnisper Gear 460 commercially available from Demitz Petroleum). As is apparent from the results shown in FIG. 4, in the case of the conventional grease-type sliding bearings, the signs of surface pressure are recognized from above 5 Kgf / mm 2 are recognized. No signs of being eaten at all.

5 and 6 are characteristic diagrams showing the wear amount of the bush and the shaft when the sliding bearing of the present invention is continuously rocked over 800 hours. This sliding bearing basically has a configuration as shown in FIG. The shaft 10 was made of S45C high frequency quenched steel, and the bush 9 was made of a carburized quenched bush having a porosity of 15% made of porous composite small alloy (Fe / Cu). The bush was impregnated with a lubricating oil having a viscosity of 460 cSt (using Demitz Dubneyspur Gear 460, available from Demitz Petroleum). It tested on the conditions of 8 Kgf / mm <2>, rocking angle 120 degree | times, constant load direction, and rotation speed 12rpm. The measurement results are shown in the shaking direction divided into X1 and X2 directions and Y1 and Y2 directions, respectively. As apparent from the results shown in FIG. 5, even after 800 hours, the bush is almost unweared regardless of the swing direction. Similarly, even after 800 hours, the shaft receives almost no abrasion regardless of the swing direction. In addition, the amount of wear is extremely small at 0.4mm at most. In other words, these results show that in the sliding bearing using the high viscosity lubricating oil-impregnated sintering bush of the present invention, no chipping occurs during 800 hours of continuous operation even at a high surface pressure of 8 Kgf / mm 2.

After sliding the sliding bearing of the present invention for a predetermined time (for example, about 50 hours), it was found that a highly viscous lubricating substance was produced in black other than the lubricant impregnated with the bush. This new black, high viscosity lubricant is probably the product of a megachemistry reaction by sliding the shaft and bush. The mixture of lubricating oil impregnated with the bush and this new black high viscosity lubricating material is thought to contribute to the realization of sliding without supplying grease for a long time. "Meganochemistry" refers to changes in structure, mutual transfer, reactivity, adsorption, catalytic activity, etc. caused by applying mechanical energy such as grinding, friction, elongation, compression, etc. to solid materials. , 4th edition, page 1276).

7 and 8 are charts showing the results of compositional analysis of black high viscosity lubricating material. FIG. 7 (a) is a chart showing the results of infrared spectroscopy analysis of lubricating oil impregnated in the bush 9 and Demitz Dubnisper Gear 460 (new and unused), and FIG. This chart shows the results of infrared spectroscopy analysis of black high viscosity lubricants produced by sliding the lubricating oil-impregnated bush and shaft for 100 hours. As is apparent from this, the black high-viscosity lubricating substance has infrared wavelengths of 170cm ^-1 and 1660cm ^-1 , and a remarkable absorption band different from the new lubricant was recognized. The infrared wavelength 1720 cm ^-1 belongs to the carbonyl group (ester), while the wavelength 1660 cm ^-1 belongs to the carbon-to-carbon double bond (olefin). From these results, it was confirmed that chemically deterioration of the impregnated lubricating oil.

FIG. 8 is a chart showing the oil component and the solid matter separated from the black high viscosity lubricating substance, and dried and identified as powder to be analyzed by X-ray. As a result, it was found that the solid was mainly composed of SiO ₂ , Fe ₃ O ₄ , C, graphite, and α-Fe ₂ O ₃ . Accordingly, it can be seen that the mechanochemistry reaction occurs in the sliding portion between the shaft 10 and the bush 9 in accordance with the result of FIG. 7.

9 is a waveform diagram of the result of measuring the change of the sliding surface of the shaft 10 and the bush 9 by disassembling the sliding bearing which the generation of the black high viscosity lubricating material was confirmed with the stylus type roughness meter. (a) is a waveform diagram showing the surface roughness of the shaft 10. As is apparent from the results shown, the sliding surface of the shaft 10 with the bush 9 is improved to a mirror state of 10-12 μm before surface driving to 1 m or less, but the dust seal does not slide with the bush 9. The contact part with (3) and the high frequency quenched part are still in the surface roughness state before driving. On the other hand, (b) is a waveform diagram showing the surface roughness of the bush 9, but it is recognized that the mirror state of 1 µm or less is improved over the entire surface of the bush. There was no "corruption damage" that was recognized again between the shaft 10 and the bush 9.

10 is a partial cross-sectional view showing another embodiment of the sliding bearing of the present invention. Grows on both ends of bush 9 to improve strength reliability against axial contact with shaft 10 and bush 9 (e.g. due to shaft / bush spacing or shaft deformation). The ning part 20 is provided.

11 is a partial cross-sectional view showing another embodiment of the sliding bearing of the present invention. In FIG. 11, abrasion damage of the boss 1 and the bracket 6 is caused by abrasion action caused by the earth and sand (for example, Vickers hardness (Hv) = 1000 SiO ₂ ) invading from the O-ring 4. In order to prevent this, abrasion resistant plates 22 having a hardness such as soil sand or the like are disposed. By this wear-resistant plate 22, it is possible to prevent not only the tribological characteristics of the sliding bearing assembly but also the strength improvement and the rattling of the bearing itself.

12 is a partial sectional view showing yet another embodiment of the sliding bearing of the present invention. 12, a high-strength bush 24 made of steel (for example, S45C quenched steel) is again provided between the bush 9 and the boss 1 to compensate for the lack of strength such as the cross section of the bush 9. It is interposed. The presence of this high strength bush 24 makes it possible to use the sliding bearing of the present invention under a higher surface pressure.

The sliding bearing assembly of the present invention is particularly suitable for use under conditions of high surface pressure of 6 Kgf / mm 2 or more and high PV value of 1.0 Kgf · m / mm 2 · s or more. The sliding bearings of the present invention are, for example, bearings for the front parts of excavators, bearings for crane arms, roller gate bearings for dam gates, vertical slide cam bearings for press molds, hydroelectric aberration guide blade bearings, marine crane unloader pin bearings. Especially suitable for low speed and high surface pressure applications.

As the bearing which does not supply grease, the porous bearing itself is already known. For example, cast copper alloy-containing bearings, powder sintered bearings and the like have been used. However, in the conventional porous bearings, relatively low viscosity lubricants are used, and under high surface pressure, the viscosity of the lubricant is further lowered by frictional heat due to sliding between the shaft and the bush, and due to the sliding motion between the shaft and the bush. Lubricant is discharged to the outside early from the bush and the sliding surface. For this reason, although the loss of lubricating oil is large, the supply interval can be lengthened to some extent, but it cannot drive for a long period of more than several years without supplying grease at all. The PV value of the conventional porous bearings is less than 1 Kgf · m / mm2 · s, but in recent excavators, the PV value of the front buoy is more than 1 Kgf · m / mm2 · s due to the high efficiency and high output. Is less than 0.15 is strongly required. Conventional porous bearings impregnated with low viscosity lubricating oil cannot be obtained with sliding bearing assemblies that do not supply grease that meets these numerical requirements.

As described above, according to the present invention, a sliding bearing capable of sliding without supplying grease over a long period of time (for example, five years) for several years or more in a use environment subjected to high surface pressure of 6 Kgf / mm 2 or more can be obtained.

Claims (18)

In the sliding bearing having a bush 9 for supporting the shaft 10 and the bush 9 made of a porous iron-based sintered material, the bush 9 is impregnated with a lubricant having a viscosity within the range of 260 cSt to 950 cSt. Sliding bearing characterized in that there is. 2. The bush (9) according to claim 1, wherein the bush (9) is made of a composite sintered alloy of copper powder and iron powder having a porosity of 5 to 30%, and the pores are communicating pores, and the bush (9) is carburized, nitrided or infiltrated. A sliding bearing whose surface is modified by nitriding. The sliding bearing according to claim 1, which is used at a surface pressure of 6 Kgf / mm2 or more. The sliding bearing according to claim 3, which is used at a surface pressure of 6 Kgf / mm 2 or more and a sliding speed in a range of 2 to 5 cm / sec. The sliding bearing according to claim 1, wherein the lubricating oil contains at least one solid particle having a particle diameter of 500 µm or less selected from the group consisting of MoS ₂ , WS ₂ , hexagonal BN, and graphite. The sliding bearing according to claim 1, wherein a member (12) for blocking oil is in contact with the outer circumferential side wall surface of the bush (9). 7. The sliding bearing according to claim 6, wherein the oil blocking member (12) is made of a material which is soft, elastic and sucks oil. 8. The sliding bearing according to claim 7, wherein the oil blocking member (12) is formed of nonwoven fabric, woven fabric, porous elastic plastic, sponge, asbestos or felt. The sliding bearing according to claim 1, wherein the bush (9) is grouted. According to claim 1, wherein the boss (9) and the bracket (6) having a bush (9) disposed on the inner circumferential surface and the contact surface of the boss (1) and the bracket (6), respectively, of a high wear resistance plate ( 22) Sliding bearings are excreted. The sliding bearing according to claim 1, wherein the sliding bearing has a boss 1 and an inner circumferential surface of the boss 1 is provided with a high-strength bush 24 radially outward and a porous composite sintered alloy bush 9 radially inward. . The sliding bearing according to claim 1, wherein the bush (9) produces a product of a mechanochemistry reaction on the sliding surface with the shaft (10) by sliding with the shaft (10) to be supported. The sliding bearing according to claim 1, which is used as a bearing for a front part of an excavator. The sliding bearing according to claim 1, which is used as a bearing for an arm of a crane. The sliding bearing according to claim 1, which is used as a roller gate bearing of a dam floodgate. The sliding bearing according to claim 1, which is used as a vertical slide cam bearing of a press die. The sliding bearing according to claim 1, which is used as a hydroelectric aberration guide vane bearing. The sliding bearing according to claim 1, which is used as a marine crane unloading pin bearing.

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