JP2017161003A - Slide mechanism and manufacturing method of slide member - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a slide mechanism excellent in a frictional wear characteristic by defining the surface roughness of a slide face by an evaluation index highly affecting the frictional wear characteristic.SOLUTION: One of a first member and a second member is slid with respect to the other with their slide faces facing each other. A height Rpk of a protruding peak of the slide face of the second member is 0.09 μm or less.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a sliding mechanism and a method for manufacturing a sliding member used in the sliding mechanism.

  When machining or surface treatment of the sliding surface is performed, the final finishing requirement is usually specified by the arithmetic average roughness Ra (for example, Patent Document 1). However, since the arithmetic average roughness Ra is an average of the amplitudes of the roughness curves, it cannot be said that the shape of the convex portion that particularly affects the frictional wear characteristics is appropriately expressed. Therefore, when only the arithmetic average roughness Ra is specified as a requirement, the surface shape that particularly affects the friction and wear characteristics varies depending on the processor.

  By blasting, it is possible to provide moderate convex portions necessary for conforming the sliding surface and concave portions that improve lubricity.

JP 2013-204807 A

  When blasting is applied to the surface treatment of the sliding surface, the surface roughness immediately after the processing of the sliding surface tends to vary. This variation affects the reproducibility of familiarity. In order to prevent deterioration in reproducibility of familiarity, a method for quantitatively evaluating the surface shape of the sliding surface formed by blasting is desired. However, the evaluation based on the arithmetic average roughness Ra cannot be said to appropriately express the shape of the convex part that particularly affects the frictional wear characteristics as described above.

  An object of the present invention is to provide a sliding mechanism having excellent frictional wear characteristics by defining the surface roughness of the sliding surface by an evaluation index that greatly affects the frictional wear characteristics. Another object of the present invention is to provide a method for manufacturing a sliding member used in this sliding mechanism.

According to one aspect of the invention,
The sliding member has a first member and a second member that face each other with the sliding surfaces facing each other, and the protruding mountain height Rpk of the sliding surface of the second member is 0. A sliding mechanism is provided that is less than 09 μm.

According to another aspect of the invention,
Preparing a sliding member having a sliding surface;
There is provided a method for manufacturing a sliding member, which includes a step of performing a blasting process on the sliding surface under a processing condition such that the protruding peak height Rpk is less than 0.09 μm.

By setting the protruding peak height Rpk of the sliding surface of the second member to be less than 0.09 μm, good frictional wear characteristics can be obtained.

1A is a cross-sectional view of a sliding mechanism according to an embodiment, and FIG. 1B is a cross-sectional view taken along one-dot chain line 1B-1B in FIG. 1A. FIG. 2A is a graph showing the relationship between the protrusion height Rpk of the sliding surface of the sliding bearing pin and the friction coefficient when the Vickers hardness Hv of the bush is 730, and FIG. 2B shows the Vickers hardness Hv of the bush. Is a graph showing the relationship between the protruding peak height Rpk of the sliding surface of the sliding bearing pin and the specific wear amount of the mating member (bush) in the case of 730. FIG. 3A is a graph showing the relationship between the protruding peak height Rpk when the Vickers hardness Hv of the bush is 730 and the rate of change Δσ with respect to the initial value of the composite root mean square roughness, and FIG. It is a graph which shows the relationship between part height Rpk and the composite root mean square roughness (sigma) after evaluation experiment. FIG. 4A is a graph showing the relationship between the protruding peak height Rpk of the sliding surface of the sliding bearing pin and the friction coefficient when the Vickers hardness Hv of the bush is 330, and FIG. 4B shows the Vickers hardness Hv of the bush. Is a graph showing the relationship between the protruding peak height Rpk of the sliding surface of the sliding bearing pin and the specific wear amount of the mating member (bush) in the case of 330. FIG. 5 is a side view of an excavator according to another embodiment. FIG. 6 is a schematic view of a mold clamping device of a molding machine according to still another embodiment. FIG. 7 is a schematic view of an injection molding machine according to still another embodiment. FIG. 8 is a schematic view of a forging press according to still another embodiment.

The sliding mechanism according to the embodiment will be described with reference to FIGS. 1A to 4B.
FIG. 1A shows a sectional view of a sliding mechanism according to the embodiment. The sliding mechanism according to this embodiment is applied to a sliding bearing including a bush (first member) 11 and a sliding bearing pin (second member) 12. FIG. 1B is a cross-sectional view taken along one-dot chain line 1B-1B in FIG. 1A. A cross-sectional view taken along one-dot chain line 1A-1A in FIG. 1B corresponds to FIG. 1A. The cross-sectional view shown in FIG. 1A includes the center of rotation, and the cross-sectional view shown in FIG. 1B is perpendicular to the center of rotation.

  A slide bearing pin 12 is inserted into the pair of bushes 11 and is rotatably supported by the bushes 11. The sliding bearing pin 12 includes a sliding surface (side surface) that slides on the inner surface (sliding surface, mating surface) of the bush 11. The bush 11 is fixed to the movable member 10. Although FIG. 1A shows an example in which two bushes 11 having the same shape are attached to the movable member 10, the number of the bushes 11 may be one or three or more. The slide bearing pin 12 is supported by support members 13 at both ends thereof. Further, the sliding bearing pin 12 is fixed to the support member 13 so as not to rotate at one end portion 14 thereof. When the movable member 10 rotates with respect to the support member 13, the sliding surface of the bush 11 slides with respect to the sliding surface of the sliding bearing pin 12.

  In addition, it is good also as a mechanism in which the pin 12 for sliding bearings rotates with respect to the bush 11. FIG. In the sliding mechanism according to the present embodiment, the sliding bearing pin 12 and the bush 11 face the sliding surfaces, and one slides with respect to the other.

  A plurality of slide bearing pins 12 having different sliding surface roughness were produced, and the friction and wear characteristics were evaluated. Hereinafter, the results of this evaluation experiment will be described.

  In the evaluation experiment, chromium molybdenum steel (SCM) was used as a material for the sliding bearing pin 12 and the bush 11. More specifically, SCM415 was used as the sliding bearing pin 12, and SCM415 and SCM440 were used as the bush 11. The SCM415 has a Vickers hardness of 730, and the SCM440 has a Vickers hardness of 330.

  Next, a method for manufacturing the sliding bearing pin 12 used in the evaluation experiment will be described. First, the sliding surface (side surface) was ground until the arithmetic average roughness Ra was about 0.01 μm to 0.1 μm. Thereafter, by performing an air blast treatment, a plurality of sliding bearing pins 12 having a protruding peak portion height Rpk of the sliding surface in the range of about 0.03 μm to 0.33 μm were produced. When blasting is used as the surface treatment, there is a correlation between the protruding peak height Rpk and the frequency of the surface roughness curve. For this reason, the frequency of the surface roughness curve of the sliding surface of the sliding bearing pin 12 used in the evaluation experiment is not particularly specified. A Gaussian filter having a short wavelength threshold value of 2.5 μm and a long wavelength threshold value of 0.8 mm was applied in calculating the index defining the surface roughness.

  The bush 11 used in the evaluation experiment is ground so that the arithmetic average roughness Ra of the sliding surface is 0.1 μm.

  In the evaluation experiment, the load is 5 kN, the speed is 0.9 cm / s, the maximum contact stress of Hertz is 187 MPa, the bearing width is 10 mm, the pin / bush diameter is 60 mm / 64 mm, and the extreme pressure agent is used as a lubricant. Filled grease was used.

  FIG. 2A shows the relationship between the protrusion ridge height Rpk of the sliding surface of the sliding bearing pin 12 and the friction coefficient when an SCM415 having a Vickers hardness Hv of 730 is used as the bush 11. The horizontal axis represents the protruding peak height Rpk of the sliding surface of the slide bearing pin 12 in the unit of “μm”, and the vertical axis represents the friction coefficient.

  It can be seen that there is a large difference in the coefficient of friction at the top and bottom of the protruding peak height Rpk value of 0.09 μm. The friction coefficient is larger than 0.07 when the protruding peak height Rpk is larger than 0.09 μm, and the friction coefficient is smaller than 0.03 when the protruding peak height Rpk is less than 0.09. In the very vicinity of the protruding peak height Rpk of 0.09 μm, the friction coefficient is distributed in the range of 0.04 to 0.06.

  When the hardness of the slide bearing pin 12 and the bush 11 is the same, in order to reduce the coefficient of friction, the protruding peak height Rpk of the sliding surface of the slide bearing pin 12 is set to less than 0.09 μm. It is preferable. The lower limit value of the preferable range of the protruding peak height Rpk is, for example, 0.02 μm.

FIG. 2B shows the relationship between the protruding peak height Rpk of the sliding surface of the sliding bearing pin 12 when the Vickers hardness Hv of the bush 11 is 730 and the specific wear amount of the mating member (bush 11). The horizontal axis represents the protruding peak height Rpk of the sliding surface of the sliding bearing pin 12 in the unit “μm”, and the vertical axis represents the specific wear amount of the mating member in the unit “mm ² / N”.

  There is no clear correlation between the specific wear amount of the mating member and the protruding peak height Rpk of the sliding surface of the sliding bearing pin 12.

  FIG. 3A shows the relationship between the protruding peak height Rpk when the Vickers hardness Hv of the bush 11 is 730 and the rate of change Δσ with respect to the initial value of the composite root mean square roughness. The horizontal axis represents the protruding peak height Rpk in the unit “μm”, and the vertical axis represents the change rate Δσ in the unit “%”. The composite root mean square roughness σ is obtained by taking the root mean square of the root mean square roughness of the sliding surface of the sliding bearing pin 12 and the root mean square roughness of the sliding surface of the bush.

  In the sample having the protruding peak height Rpk of less than 0.09 μm, the composite root mean square roughness σ is greatly reduced by the evaluation experiment as compared with the sample having the protruding peak height Rpk of 0.09 μm or more. I understand that. This indicates that the sliding surfaces of the bush 11 and the sliding bearing pin 12 are well adapted to each other. A low friction coefficient can be obtained by improving the conformability of the sliding surface.

  FIG. 3B shows a relationship between the protruding peak height Rpk and the composite root mean square roughness σ after the evaluation experiment. The horizontal axis represents the protruding peak height Rpk in the unit “μm”, and the vertical axis represents the composite root mean square roughness σ in the unit “μm”.

  It can be seen that in the sample having the protruding peak height Rpk of less than 0.09 μm, the composite root mean square roughness σ after the evaluation experiment is smaller than that of the sample having the protruding peak height Rpk of 0.09 μm or more. Since the oil film thickness is determined by experimental conditions, it is the same for all samples. Therefore, a small composite root mean square roughness σ means that the ratio of the oil film thickness to the composite root mean square roughness σ is large. Since this film thickness ratio is large, a low friction coefficient can be obtained.

  From the experimental results shown in FIGS. 2A, 2B, 3A and 3B, when the hardness of the sliding bearing pin 12 and the bush 11 is the same, the height of the protruding ridge portion of the sliding surface of the sliding bearing pin 12 is It can be seen that by setting the thickness Rpk to less than 0.09 μm, a sliding mechanism having a small friction coefficient and high conformability of the sliding surface can be obtained. In other words, in order to realize a sliding mechanism having a small coefficient of friction and high conformability of the sliding surface, the protruding peak height Rpk of the sliding surface of the sliding bearing pin 12 may be less than 0.09 μm. preferable.

  In FIGS. 2A and 2B, the hardness of the sliding bearing pin 12 and the bush 11 is the same, but it is not necessary that the hardness of both is exactly the same. For example, if the Vickers hardness of the bush 11 is 0.9 to 1.1 times the Vickers hardness of the sliding bearing pin 12, it can be said that the hardness of both is substantially the same.

  FIG. 4A shows the relationship between the protruding peak height Rpk of the sliding surface of the sliding bearing pin 12 and the friction coefficient when the Vickers hardness Hv of the bush 11 is 330. That is, the bush 11 is softer than the sliding bearing pin 12. The horizontal axis represents the protruding peak height Rpk of the sliding surface of the slide bearing pin 12 in the unit of “μm”, and the vertical axis represents the friction coefficient.

  As the protruding peak height Rpk increases in a range from 0.03 μm to 0.33 μm, the friction coefficient tends to increase. However, as in the case shown in FIG. 2A, a clear boundary where the friction coefficient changes sharply cannot be specified.

FIG. 4B shows the relationship between the protruding peak height Rpk of the sliding surface of the sliding bearing pin 12 when the Vickers hardness Hv of the bush 11 is 330 and the specific wear amount of the mating member (bush 11). The horizontal axis represents the protruding peak height Rpk of the sliding surface of the sliding bearing pin 12 in the unit “μm”, and the vertical axis represents the specific wear amount of the mating member in the unit “mm ² / N”.

It can be seen that there is a large difference in the specific wear amount of the mating material on the upper and lower sides of the protruding ridge height Rpk at the boundary of 0.08 μm. In the range where the protruding peak height Rpk is larger than 0.08 μm, the specific wear amount of the counterpart material is larger than 6 × 10 ⁻¹⁰ mm ² / N, and in the range where the protruding peak height Rpk is less than 0.08 μm, the counterpart The specific wear amount of the material is smaller than 1 × 10 ⁻¹⁰ mm ² / N. Height of the projecting peak portions Rpk is in close proximity to the 0.08 .mu.m, the specific wear rate of the counterpart material is distributed in the range of ^{2 × 10 -10 mm 2 / N~5} × 10 -10 mm 2 / N.

  When the bush 11 is softer than the sliding bearing pin 12, it is preferable that the protruding peak height Rpk of the sliding surface of the sliding bearing pin 12 is less than 0.08 μm in order to reduce the amount of wear of the bush 11. . The lower limit value of the preferable range of the protruding peak height Rpk is, for example, 0.02 μm.

  In the evaluation experiment shown in FIGS. 4A and 4B, the Vickers hardness of the sliding bearing pin 12 was 730, and the Vickers hardness of the bush 11 was 330. In order to obtain the above-described effect, generally, one standard is that the Vickers hardness of the bush 11 is 1/2 times or less than the Vickers hardness of the sliding bearing pin 12.

  In the evaluation experiment, air blasting is used for finishing the sliding surface of the sliding bearing pin 12, but wet blasting may be used. In order to make the protruding peak height Rpk of the sliding surface less than 0.09 μm or less than 0.08 μm, it is preferable to use a projection material having a particle size of 50 μm or less. Furthermore, it is preferable to use particles with rounded corners as the projection material.

  If the projection material is too hard, it is difficult to make the protruding peak height Rpk of the sliding surface less than 0.09 μm or less than 0.08 μm. As the material of the projection material, it is preferable to use a material that is the same as or softer than the sliding surface to be blasted.

  If the projection energy of the projection material is increased too much, the protruding peak height Rpk of the sliding surface becomes larger than 0.09 μm. When the surface treatment is performed with the projection energy used in the general air blast treatment, the protruding peak height Rpk of the sliding surface becomes larger than 0.09 μm. In order to make the protruding peak height Rpk less than 0.09 μm or less than 0.08 μm, it is preferable that the projection energy of the projection material is smaller than the projection energy used in general air blasting.

  In the above embodiment, the sliding bearing is taken up as an example of the sliding mechanism. In the sliding bearing, sliding surfaces facing each other have a cylindrical shape. The sliding surface produced by the blasting process described above can be applied to other sliding mechanisms. For example, the present invention can be applied to a sliding mechanism in which a pair of sliding members having a planar sliding surface slide with the sliding surfaces facing each other.

  Next, a plurality of other embodiments to which the above-described sliding mechanism is applied will be described with reference to FIGS.

  FIG. 5 shows a side view of an excavator according to another embodiment. An upper turning body 21 is mounted on the lower traveling body 20 so as to be turnable. A boom 22, an arm 23, and a bucket 24 are connected to the upper swing body 21. Hydraulic cylinders 25, 26, and 27 drive the boom 22, the arm 23, and the bucket 24, respectively. The hydraulic cylinder 27 and the bucket 24 are connected via a link mechanism 28. The joint portion 31 of the boom 22 and the upper swing body 21, the joint portion 32 of the boom 22 and the arm 23, the joint portion 33 of the arm 23 and the bucket 24, the hydraulic cylinders 25, 26, and 27, and the work elements The slide bearing pin 12 according to the embodiment shown in FIGS. 1A and 1B is used for the joint portion 34 and the joint portion of the link mechanism 28.

  By applying the slide bearing pin 12 according to the above embodiment to the joint portion of the excavator, the effects of reducing the friction coefficient and improving the conformability can be obtained. Alternatively, an effect of reducing the wear amount of the bush 11 (FIGS. 1A and 1B) can be obtained.

  FIG. 6 shows a schematic view of a mold clamping device of a molding machine according to still another embodiment. The stationary platen 40 and the toggle support 41 are fixed to the frame at a distance from each other. A plurality of tie bars 42 are installed between the fixed platen 40 and the toggle support 41.

  The movable platen 43 is supported by the tie bar 42 so as to be able to advance and retreat relative to the fixed platen 40. The mold mounting surface of the fixed platen 40 and the mold mounting surface of the movable platen 43 are opposed to each other. A fixed mold 45 is mounted on the mold mounting surface of the fixed platen 40, and a movable mold 46 is mounted on the mold mounting surface of the movable platen 43.

  A toggle mechanism 50 is disposed between the movable platen 43 and the toggle support 41. A driving device 47 is attached to the back surface of the toggle support 41 (the surface facing the side opposite to the movable platen 43). A connecting rod 51 extends from the driving device 47 through the toggle support 41 toward the movable platen 43. The drive device 47 moves the connecting rod 51 in the axial direction.

  A cross head 52 is attached to the tip of the connecting rod 51. One end of each of the pair of small toggle levers 53 is attached to the cross head 52 via a slide bearing pin 61. One end of the pair of large toggle levers 54 is attached to the toggle support 41 via a slide bearing pin 62. The other end of the small toggle lever 53 is attached to an intermediate position of the large toggle lever 54 via a slide bearing pin 63. The other end of the large toggle lever 54 is attached to one end of the toggle arm 55 via a slide bearing pin 64. The other end of the toggle arm 55 is attached to the movable platen 43 via a sliding bearing pin 65.

  The toggle mechanism 50 can be operated by the drive device 47 moving the connecting rod 51 in the axial direction. For processing the sliding surfaces (side surfaces) of the sliding bearing pins 61, 62, 63, 64, 65, the blasting process for the sliding surface of the sliding bearing pin 12 shown in FIGS. 1A and 1B can be applied. . As a result, the effects of reducing the friction coefficient and improving the conformability can be obtained. Alternatively, the effect of reducing the wear amount of the mating surfaces of the sliding bearing pins 61, 62, 63, 64, 65 can be obtained.

  FIG. 7 shows a schematic view of an injection molding machine according to still another embodiment. A toggle mechanism 72 is disposed between the fixed platen 70 and the toggle support 71. The toggle support 71 moves up and down with respect to the fixed platen 70 by the toggle mechanism 72. Three tie bars 73 extending upward from the toggle support 71 extend through the fixed platen 70 and further upward. In FIG. 7, two tie bars 73 are shown. A movable platen 75 is fixed to the upper end of the tie bar 73 using a fixing nut 76. When the toggle mechanism 72 is operated to move the toggle support 71 downward, the movable platen 75 approaches the fixed platen 70.

  Two sliding plates 80 a and 80 b are fixed on the fixed platen 70. A rotary table 77 is rotatably supported with respect to one tie bar 73 via a rotary bearing 78, and is supported from below by sliding plates 80a and 80b. The two sliding plates 80 a and 80 b are arranged at point-symmetrical positions with respect to the rotation center of the rotary table 77. A rotation drive mechanism 79 rotates the rotary table 77.

  Two lower molds 82 a and 82 b are supported on the rotary table 77. When one lower mold 82a is positioned right above one sliding plate 80a, the other lower mold 82b is positioned right above the other sliding plate 80b. FIG. 7 shows a state in which the lower mold 82a is positioned directly above the sliding plate 80a.

  An upper mold 83 is attached to the surface facing the lower side of the movable platen 75. The upper mold 83 is disposed immediately above one sliding plate 80a. By rotating the rotary table 77, one of the lower molds 82a and 82b can be arranged under the upper mold 83 to produce a molded product, and the produced molded product can be taken out from the other.

  When injection molding is performed, the distance between the fixed platen 70 and the movable platen 75 is narrowed, and a downward load is applied to a part of the rotary table 77, specifically, a position directly above the sliding plate 80a. The sliding plate 80 a supports a load applied to the rotary table 77.

  The upper surfaces of the sliding plates 80a and 80b and the lower surface of the rotary table 77 constitute a pair of sliding surfaces. When the rotary table 77 rotates, the lower surface (sliding surface) of the rotary table 77 and the upper surfaces (sliding surfaces) of the sliding plates 80a and 80b slide. The blasting process for the sliding surface of the sliding bearing pin 12 shown in FIGS. 1A and 1B can be applied to processing the upper surfaces of the sliding plates 80a and 80b.

  By applying the blasting of the sliding surface of the sliding bearing pin 12 shown in FIGS. 1A and 1B to the processing of the upper surfaces of the sliding plates 80a and 80b, the effects of reducing the friction coefficient and improving the conformability can be obtained. . Alternatively, an effect of reducing the wear amount of the mating surfaces of the sliding plates 80a and 80b, that is, the lower surface of the rotary table 77 can be obtained.

  FIG. 8 shows a schematic view of a forging press according to still another embodiment. A column 92 extends upward from the four corners of the bed 90, and a crown 91 is fixed to the upper end of the column 92. An eccentric shaft 95 spanned in the horizontal direction is rotatably supported on the crown 91. A drive source 96 rotates the eccentric shaft 95. A slide 98 is connected below the eccentric shaft 95 via a connecting rod 97.

  A slide give 100 is attached to each column 92. The slide give 100 includes a guide surface extending in the vertical direction. The slide 98 is guided in the vertical direction with the guided surface facing the guide surface of the slide give 100. By rotating the eccentric shaft 95, the slide 98 can be reciprocated in the vertical direction.

  A lower die holder 105 is attached on the bed 90. The lower die 106 is held by the lower die holder 105. An upper die holder 107 is attached to the lower surface of the slide 98. The upper die 108 is held by the upper die holder 107.

  For example, a liner material made of a copper alloy can be used for the guide surface of the slide give 100. The blasting of the sliding surface of the sliding bearing pin 12 shown in FIGS. 1A and 1B can be applied to the processing of the guided surface of the slide 98. On the contrary, for example, a copper alloy liner material is used for the guided surface of the slide 98, and the sliding surface of the sliding bearing pin 12 shown in FIGS. Blasting may be applied.

  By applying the blasting of the sliding surface of the sliding bearing pin 12 shown in FIGS. 1A and 1B to one of the guide surface of the slide give 100 and the guided surface of the slide 98, the friction coefficient is reduced. The effect of improving the compatibility is obtained. Alternatively, an effect of reducing the amount of wear of the other of the guide surface of the slide give 100 and the guided surface of the slide 98 can be obtained.

  Although the present invention has been described with reference to the embodiments, the present invention is not limited thereto. It will be apparent to those skilled in the art that various modifications, improvements, combinations, and the like can be made.

DESCRIPTION OF SYMBOLS 10 Fixed member 11 Bush 12 Sliding bearing pin 13 Movable member 14 End part 20 of sliding bearing pin Lower traveling body 21 Upper turning body 22 Boom 23 Arm 24 Bucket 25, 26, 27 Hydraulic cylinder 28 Link mechanism 31, 32, 33 , 34 Joint 40 Fixed platen 41 Toggle support 42 Tie bar 43 Movable platen 45 Fixed mold 46 Movable mold 47 Drive device 50 Toggle mechanism 51 Connecting rod 52 Cross head 53 Small toggle lever 54 Large toggle lever 55 Toggle arms 61, 62, 63, 64, 65 Slide bearing pin 70 Fixed platen 71 Toggle support 72 Toggle mechanism 73 Tie bar 75 Movable platen 76 Fixing nut 77 Rotary table 78 Rotating bearing 79 Rotating drive mechanism 80a, 80b Sliding plate 82a, 82b Lower mold 83 Upper side Type 90 bed 91 Crown 92 column 95 the eccentric shaft 96 the drive source 97 connecting rod 98 slides 100 slide gib 105 lower die holder 106 lower mold 107 the upper die holder 108 upper mold

Claims (9)

  A sliding member has a first member and a second member that face each other with the sliding surfaces facing each other, and the protruding peak height Rpk of the sliding surface of the second member is 0.09 μm. Sliding mechanism that is less than.   2. The sliding mechanism according to claim 1, wherein a protrusion peak height Rpk of the sliding surface of the second member is less than 0.08 μm.   The sliding mechanism according to claim 1, wherein the first member is softer than the second member.   The sliding mechanism according to claim 3, wherein the second member has a Vickers hardness of ½ times or less of the Vickers hardness of the first member.   The sliding mechanism according to any one of claims 1 to 4, wherein the first member is a bush, and the second member is a sliding bearing pin that is inserted into the bush and rotates. The first member is a rotary table that is rotatably supported with respect to a vertical rotation axis and has a sliding surface facing downward;
The second member is a sliding plate disposed under the rotary table and having a sliding surface facing the sliding surface of the rotary table;
By rotating the rotary table, the sliding surface of the rotary table slides with respect to the sliding surface of the sliding plate,
The sliding mechanism according to claim 1, wherein the sliding plate supports a load applied to the rotary table. One of the first member and the second member is a slide giving including a guide surface extending in the vertical direction,
The other of the first member and the second member is a slide that moves in a vertical direction with a guided surface facing the guide surface of the slide give,
The sliding mechanism according to any one of claims 1 to 4, wherein the guided surface of the slide slides with respect to the guide surface of the slide give as the slide moves up and down. Preparing a sliding member having a sliding surface;
And a step of performing a blasting process on the sliding surface under a processing condition such that the protruding peak height Rpk is less than 0.09 μm.   The manufacturing method of the sliding member according to claim 8, wherein the processing condition in the step of performing the blasting process is a condition in which the protruding ridge height Rpk is less than 0.08 µm.

Images