JP2007146889A - Rolling support device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling support device which causes less surface damage and offers an excellent rolling fatigue life even though employed under an undesirable environment in a lubricating state. <P>SOLUTION: A thrust needle roller bearing is equipped with an inner ring 1, an outer ring 2 and a plurality of needle rollers 3 rollably arranged between the raceway surface 1a of the inner ring 1 and a raceway surface 2a of the outer ring 2. In at least one of the raceway surface 1a of the inner ring 1, the raceway surface 2a of the outer ring 2 and the raceway surface 3a of the needle roller 3, a part having an area ratio of 75% or more is covered with lubricating film formed of a solid lubricant. It is preferable that the solid lubricant is graphite fluoride. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a rolling support device such as a rolling bearing, a linear guide device, a ball screw, and a linear motion bearing.

  The rolling support device as described above is used while being repeatedly subjected to shear stress. Therefore, the rolling parts (first member, second member, rolling element) constituting the rolling support device have high hardness, high load resistance, and so that the rolling fatigue life is prolonged even when subjected to repeated shear stress. Generally, it is formed of a material having excellent wear resistance. As such a material, usually, bearing steel such as SUJ2, stainless steel such as SUS440 and 13Cr, and case-hardened steel such as SCR420 are subjected to quenching treatment and tempering treatment, carburizing treatment or A material having a hardness of HRC58 to 64 is used by performing a quenching process and a tempering process after the carbonitriding process.

In addition, the rolling fatigue life of a rolling bearing is closely related to the lubrication state of the rolling surface (the raceway surface of the first member and the second member and the rolling surface of the rolling element) as well as the material forming the rolling part. It is known that The quality of the lubrication state of the rolling surface is represented by an oil film parameter Λ (see the following formula) which is a ratio between the surface roughness of the rolling surface and the oil film thickness formed on the rolling surface.
Λ = h / σ
h: EHL oil film thickness
σ: synthetic surface roughness (σ ₁ ² + σ ₂ ² ) ^1/2
σ ₁ and σ ₂ are the roughness of the two surfaces in contact (root mean square roughness)

  As the oil film parameter Λ is larger, surface-origin separation due to contact between minute projections on the surface is less likely to occur and the lubrication state is better. In this case, the rolling fatigue life is determined by the cleanliness, hardness, material, heat treatment, etc. of the material. Conversely, the smaller the oil film parameter Λ, the easier it is for surface-initiated peeling due to contact between the microprojections on the surface, resulting in poor lubrication. As a result, peeling or seizure tends to occur on the rolling surface, and the rolling fatigue life is shortened.

Examples of rolling support devices used in such poorly lubricated environments include planetary gear bearings used in transmissions, and ball screws used in electric injection molding machines, electric press machines, and the like. It is done. In planetary gear bearings, helical gears are used so that force is smoothly transmitted from the planetary gear (first member) to the planetary shaft (second member). The running trace of the shaft becomes a twisted shape. The planetary gear bearing is used under high-speed rotation exceeding 10,000 min ⁻¹ .

Therefore, a non-uniform force is applied to the needle rollers arranged between the planetary gear and the planetary shaft, and edge loading, skew, and the like may occur in the rollers. As a result, the rolling surface is poorly lubricated and surface damage such as smearing or seizure occurs, which may shorten the rolling fatigue life. In addition, from the viewpoint of improving fuel efficiency associated with CO ₂ emission regulations in recent years, the seizure resistance at planetary gear bearings at high speed rotation is also increasing as the viscosity of the lubricating oil progresses to increase the rotation efficiency at high speed rotation. And durability has been demanded.

  For this reason, a shaft hole lubrication system has been proposed in which needle rollers of a planetary gear bearing are double-rowed, a shaft hole communicating from the shaft end to the inside of the bearing is provided, and oil is supplied through the shaft hole. However, even if such a shaft hole lubrication method is adopted, if the amount of lubricating oil is insufficient, the rolling surface is poorly lubricated and surface damage such as peeling and seizure occurs, resulting in rolling fatigue. Life may be shortened.

  On the other hand, the ball screw is used in a short stroke in which a high load is instantaneously applied, and is used under a reciprocating motion condition in which the ball screw is rotated in the reverse direction after stopping once in a state where the maximum load is applied. Therefore, the lubricating coating formed on the rolling surface is scraped off, and the rolling surface is poorly lubricated. Therefore, surface damage such as peeling and wear may occur on the rolling surface, and the rolling fatigue life may be shortened.

  In particular, the contact surface between the balls causes relative slip at twice the rolling speed, and due to the deformation of the machine base due to high load and misalignment during installation, surface damage is significant. The rolling fatigue life may be further shortened due to the surface damage of the balls. As techniques for preventing such surface damage, techniques described in Patent Documents 1 to 4 have been proposed.

In Patent Document 1, an infinite number of independent minute depressions are randomly formed on the surface of a rolling element or raceway, and an axial surface roughness RMS (L) and a circumferential surface roughness RMS (C) It has been proposed that the ratio RMS (L) / RMS (C) is 1.0 or less, the surface roughness parameter (SK value) is negative, and the area ratio occupied by the minute recesses is 10 to 40%. Further, in Patent Document 2, in a mechanical component having a sliding surface that is in sliding contact with being subjected to a thrust load, an infinite number of independent small depressions are provided on the sliding surface, and the average area of the minute depressions is 35 to 150 μm ² . It has been proposed that the area ratio occupied by the minute recesses is 10 to 40%.

Further, in Patent Document 3, a solid lubricating film made of a molybdenum disulfide projecting material containing about 95% by mass or more of molybdenum disulfide having an average particle diameter of about 1 to 20 μm is selected from metal, resin, glass, and ceramics. It has been proposed to form on the surface of materials consisting of Further, in Patent Document 4, it is proposed to form a solid lubricant film having a thickness of 0.5 μm or less by fixing fine particles of molybdenum disulfide on at least one sliding contact surface of a screw shaft, a nut, and a ball. ing.
Japanese Patent No. 2634495 Japanese Patent No. 2554881 JP 2002-339083 A JP 2004-60742 A

  By the way, in recent years, with the downsizing of transmissions and CVT, etc., the above-mentioned planetary gear bearings have been required to have higher speeds. As the operating temperature rises, the rolling surface is in a lubricated state. Further, it is assumed that it becomes defective. Further, in the ball screw, it is demanded that the load is further increased and the stroke of the reciprocating motion is shortened, and the lubrication state of the rolling surface is assumed to be further deteriorated.

  However, in the techniques described in Patent Documents 1 and 2 described above, when a low-viscosity lubricating oil is used or the amount of lubricating oil is insufficient, the lubricating oil cannot be sufficiently retained in the minute recess, It is difficult to effectively prevent surface damage. Further, in Patent Document 3 described above, there is room for further improvement in that it is difficult to cause surface damage because only the material of the solid lubricant film is specified.

Furthermore, in the technique described in Patent Document 4 described above, since the material and thickness of the solid lubricant film are only specified, there is room for further improvement in that it is difficult to cause surface damage. Furthermore, in the techniques described in Patent Documents 3 and 4 described above, the solid lubricant film is merely fixed by collision, and therefore when applied to rolling parts for a rolling support device that is used under repeated shear stress. It is assumed that the solid lubricant film easily falls off, and it is difficult to effectively prevent surface damage.
Therefore, the present invention solves the problems of the prior art as described above, and provides a rolling support device that has an excellent rolling fatigue life and hardly causes surface damage even when used in an environment where the lubrication state is poor. The issue is to provide.

  In order to solve the above problems, the present invention has the following configuration. That is, the rolling support device according to claim 1 of the present invention includes a first member and a second member having raceways arranged to face each other, a raceway surface of the first member, and a raceway surface of the second member. A rolling support device that is arranged so as to be freely rollable between, wherein one of the first member and the second member moves relative to the other through the rolling of the rolling member. At least one of the raceway surface of the first member, the raceway surface of the second member, and the rolling surface of the rolling element has a lubricating coating composed of a solid lubricant in a portion having an area ratio of 75% or more. It is characterized by having.

  The rolling surface of the rolling parts (first member, second member, and rolling element) is formed with a specific area ratio on the rolling surface of the rolling lubricant. The coating is formed in close contact, and good lubricity is imparted to the rolling parts. Therefore, surface damage such as smearing, seizure, wear, and peeling is unlikely to occur on the rolling surface of the rolling component, and acoustic failure and vibration failure due to peeling of the lubricating coating are unlikely to occur.

According to a second aspect of the present invention, there is provided the rolling support device according to the first aspect, wherein the solid lubricant is graphite fluoride.
Lubricant coatings made of graphite fluoride have better adhesion to the surface of metal rolling parts than lubricant coatings made of other solid lubricants (for example, polytetrafluoroethylene or molybdenum disulfide). It is good and has excellent lubricity and strength.

Furthermore, the rolling support device according to claim 3 of the present invention is the rolling support device according to claim 1 or 2, wherein the thickness of the lubricating coating is 0.1 μm or more and 8 μm or less. .
With such a configuration, the lubricity is good and the strength required for the lubricating coating coated on the rolling parts can be obtained. If the thickness of the lubricating coating is less than 0.1 μm, the lubricity may be insufficient. On the other hand, if the thickness exceeds 8 μm, the strength of the lubricating coating may be insufficient.

Furthermore, the rolling support apparatus of Claim 4 which concerns on this invention is a rolling support apparatus as described in any one of Claims 1-3, The track surface of said 1st member, The track surface of said 2nd member, and A minute recess having a depth of 0.1 μm or more and 5 μm or less is formed in at least a portion of the rolling surface of the rolling element provided with the lubricating coating.
Since the lubricant film is filled in the minute recesses formed on the surface, the lubricant film can be formed in close contact with the surface of the rolling part. If the depth of the minute recess is less than 0.1 μm, good adhesion of the lubricating coating may not be obtained. However, even if it exceeds 5 μm, no further effect can be expected. Therefore, the depth of the minute recess is preferably 5 μm or less.

Furthermore, the rolling support apparatus of Claim 5 which concerns on this invention is a rolling support apparatus as described in any one of Claims 1-4, The track surface of said 1st member, The track surface of said 2nd member, and At least a portion of the rolling surface of the rolling element provided with the lubricating coating has a center line average roughness Ra of 0.1 μm or more and 0.5 μm or less.
With such a configuration, the acoustic characteristics and vibration characteristics of the rolling support device are good. If the center line average roughness Ra of the surface is more than 0.5 μm, the acoustic characteristics and vibration characteristics may be insufficient. On the other hand, if the center line average roughness Ra is less than 0.1 μm, the rolling support device may be expensive.

Furthermore, the rolling support apparatus of Claim 6 which concerns on this invention is the rolling support apparatus as described in any one of Claims 1-5. WHEREIN: The said lubricating coating is the shot-peening method which projects the powder of the said solid lubricant. It is formed by these.
Examples of the method for forming the lubricating film include coating, baking, thermal spraying, sputtering, ion plating, and shot peening. In order to improve the surface hardness of the rolling parts after the lubricating film is formed, Peening is preferred.

  The present invention can be applied to various rolling support devices. For example, rolling bearings, ball screws, linear guide devices, and linear motion bearings. The first member and the second member in the present invention are an inner ring and an outer ring when the rolling support device is a rolling bearing, a screw shaft and a nut when the ball screw is also used, and a guide when the linear guide device is used. In the case of a rail and a slider, and also a linear motion bearing, it means a shaft and an outer cylinder, respectively.

  The rolling support device of the present invention has an excellent rolling fatigue life because it hardly causes surface damage even when used in an environment where the lubrication state is poor.

Embodiments of a rolling support device according to the present invention will be described in detail with reference to the drawings. FIG. 1 is a partial longitudinal sectional view showing a structure of a thrust needle roller bearing which is an embodiment of a rolling support device according to the present invention.
1 includes an inner ring (first member) 1 having a raceway surface 1a, an outer ring (second member) 2 having a raceway surface 2a facing the raceway surface 1a of the inner ring 1, and both raceway surfaces. There are provided a plurality of needle rollers (rolling elements) 3 that are arranged so as to roll freely between 1a and 2a, and a cage 4 that holds the plurality of needle rollers 3 between both raceway surfaces 1a and 2a. . In addition, the holder | retainer 4 does not need to be provided.

At least one of the raceway surface 1 a of the inner ring 1, the raceway surface 2 a of the outer ring 2, and the rolling surface 3 a of the needle roller 3 is made of a solid lubricant in a portion having an area ratio of 75% or more. A lubricating coating (not shown) is coated.
Such a thrust needle roller bearing is provided with excellent lubricity due to the lubricating coating, so even if the lubrication with a lubricant or the like is poor, smearing, seizure, wear, It does not easily cause surface damage such as peeling, and has an excellent rolling fatigue life. Further, since the lubricant film is hardly peeled off, it is difficult for acoustic defects and vibration defects to occur.

  The lubricating coating is preferably formed by a shot peening method in which a solid lubricant powder is projected. In addition, the type of solid lubricant is not particularly limited. For example, graphite fluoride, molybdenum disulfide, polytetrafluoroethylene, polyethylene, fluororesin, nylon, polyacetal, polyolefin, polyester, metal soap, tungsten disulfide, Boron nitride, graphite, calcium fluoride, barium fluoride, tin, and a tin alloy can be used, and among these, graphite fluoride is particularly preferable.

  Furthermore, the thickness of the lubricating coating is preferably 0.1 μm or more and 8 μm or less. Further, at least a portion of the raceway surface 1 a of the inner ring 1, the raceway surface 2 a of the outer ring 2, and the rolling surface 3 a of the needle roller 3 covered with the lubricating coating has a depth of 0.1 μm to 5 μm. It is preferable to form a recess. Further, at least a portion of the raceway surface 1 a of the inner ring 1, the raceway surface 2 a of the outer ring 2, and the rolling surface 3 a of the needle roller 3 coated with the lubricating coating has a center line average roughness Ra of 0.1 μm or more. It is preferable that it is 0.5 μm or less.

  In the present embodiment, the thrust needle roller bearing has been described as an example of the rolling support device. However, the type of the rolling bearing is not limited to the thrust needle roller bearing, and the present invention includes various types. It can be applied to rolling bearings. For example, radial rolling bearings such as deep groove ball bearings, angular contact ball bearings, self-aligning ball bearings, needle roller bearings, cylindrical roller bearings, tapered roller bearings, self-aligning roller bearings, thrust ball bearings, thrust roller bearings This is a thrust type rolling bearing. The present invention is not limited to rolling bearings, and can be applied to various other types of rolling support devices. For example, a ball screw, a linear guide device, a linear motion bearing, or the like.

〔Example〕
The present invention will be described more specifically with reference to the following examples. Various thrust needle roller bearings (inner diameter 40 mm, outer diameter 70 mm, width 5.5 mm) were prepared as test bearings and subjected to a rotation test to evaluate the life. The thrust needle roller bearing, which is a test bearing, is composed of a solid lubricant only on the rolling surface of the needle roller among the raceway surface of the inner ring, the raceway surface of the outer ring, and the rolling surface of the needle roller. The thrust needle roller bearing shown in FIG. 1 is the same as that described above except that the lubricating coating is applied.
The type of lubricant film coated on the rolling surface of the needle roller (type of solid lubricant), the area ratio of the lubricant film, the thickness of the lubricant film, the type of pretreatment described below, and the rolling surface of the needle roller Tables 1 to 3 show the depth of the formed minute recess and the centerline average roughness Ra of the rolling surface of the needle roller.

  Here, the manufacturing method of the thrust needle roller bearing which is a test bearing is demonstrated. First, the inner ring, the outer ring, and the needle rollers are made of SUJ2, and after carbonitriding at 840 ° C. for 3 hours in an atmosphere containing RX gas, enriched gas, and ammonia gas, oil quenching and tempering are performed. Is. By such treatment, the amount of retained austenite of the surface layer is adjusted to 15 to 40% by volume, and the surface hardness is adjusted to HRC 62 to 67 (Hv 746 to 900). In addition, carbonitriding treatment may not be performed, and it may be subjected to sublimation quenching. Further, steel such as SCM420 and SCr420 may be used as a raw material, and the surface may be hardened by performing carbonitriding or carburizing.

When forming a minute depression on the rolling surface of the needle roller, a pretreatment for forming the minute depression is performed after the heat treatment. Although the method for forming the minute recess is not particularly limited, shot peening treatment and barrel treatment are adopted. The shot peening process was performed using a shot peening apparatus. As the shot material, a steel ball, SiC, SiO ₂ , Al ₂ O ₃ , glass beads, etc. having an average particle diameter of 45 μm specified in JIS R6001 are used, and shot under the conditions of an injection pressure of 196 to 882 kPa and an injection time of 10 to 20 min. The material was sprayed onto the rolling surface of the needle roller. The amount of needle rollers processed at a time was 1 to 6 kg.

The barrel treatment was performed using a blend of various media and additives to perform rough processing for forming large irregularities on the rolling surface of the needle rollers and finishing processing for adjusting the roughness of the plateau portion. In addition, you may give both a shot peening process and a barrel process to the rolling surface of a needle roller.
The method for measuring the depth of the minute recess is as follows. Using a three-dimensional non-contact surface shape measurement system, 30 views of the rolling surface of the needle roller were observed at a magnification of 100 times, and the obtained image was converted into a cross-sectional profile. Then, in each of the five cross sections in the X direction and the Y direction, the depth of the minute depression was measured, and the results were averaged.

Next, a lubricating film composed of a solid lubricant was coated on the rolling surfaces of the needle rollers. The method for coating the lubricating coating is not particularly limited, but shot peening treatment is adopted. A shot peening apparatus is used for forming the lubricating coating, and as the solid lubricant as the shot material, graphite fluoride powder having an average particle size of 60 μm or less (according to JIS R6001) or an average particle size of 5 μm or less (JIS R6001). ) Molybdenum disulfide (MoS ₂ ) powder. The injection pressure is 196 to 882 kPa, and the injection time is 10 to 20 minutes. The mass of the needle rollers used for one treatment was 1 to 6 kg.

  The method for measuring the area ratio of the lubricating coating is as follows. Using an electron beam microanalyzer (EPMA), the rolling surface of the needle roller coated with the lubricating coating was observed at 30 fields of view at a magnification of 2000 times, and a square portion of 200 μm on one side of the portion where the lubricating coating was formed was 1000 The characteristic X-ray intensity of carbon or molybdenum was measured by magnifying. Then, assuming that the lubricating film is coated in a region where an intensity of 10 times or more of the characteristic X-ray intensity before coating the lubricating film is observed, a portion where the lubricating film is coated by image analysis of the result Were obtained, and the average value of 30 fields of view was calculated.

  The method for measuring the thickness of the lubricating coating is as follows. First, a pyrrolidone solution of polyamide-imide, which is a thermosetting resin, was applied to the rolling surface of a needle roller provided with a lubricant film, and cured by heating at 175 ° C. for 2 hours to form a protective film for the lubricant film. . The needle rollers were cut and embedded in an epoxy resin, and the cut surface was mirror finished by buffing. Furthermore, a nano-order chromium layer was coated on the surface by sputtering to provide electrical conductivity.

The cut surface of the sample obtained in this manner was mirror-finished and observed with 30 fields of view at a magnification of 5000 with an electron microscope (SEM). In this electron microscope observation, the film thickness can be clearly observed by using a secondary electron beam image when graphite fluoride is used as a solid lubricant, and using a reflected electron beam image when molybdenum disulfide is used. I did it.
In each field of view, the thickness of the lubricating coating was measured at five points, the average value of these five points was determined, and this average value was taken as the thickness of the lubricating coating in the field of view. And the average value of 30 visual fields of the thickness of a lubricating film was calculated | required.

  Further, when the surface hardness was measured using a microhardness meter after coating the lubricating coating, the rolling surface coated with the lubricating coating was the hardness of the portion from the outermost surface to a depth of 2 to 15 μm. Had a gradient. And the hardness of the hardest part improved 5 to 20% compared with the hardness before the shot peening process of a solid lubricant.

  Next, a life evaluation method by a rotation test will be described. Thrust-type bearing steel life test described on pages 10 to 21 of “Special Steel Handbook 1st Edition” (Electric Steel Research Institute, Science and Engineering, published on May 25, 1969) A machine was used (see FIG. 2). This testing machine will be described. An upper fixing portion 22 having a recess formed on the lower surface and a lower fixing portion 23 having a recess formed on the upper surface are fitted via an O-ring 24 to thereby form the test chamber 21. The test chamber 21 is formed and can be sealed. The spindle 25 is rotatably supported by the upper fixed portion 22, and is configured such that the test bearing 26 can be disposed between the lower surface of the rotating disk portion 25 a attached to the spindle 25 and the upper surface of the lower fixed portion 23. Has been.

  Reference numeral 31 is a thrust bearing, reference numeral 32 is a radial bearing, reference numeral 33 is a seal, and reference numeral 34 is a spacer. In FIG. 2, reference numeral 26 a is an upper race of the test bearing 26, reference numeral 26 b is a roller and a cage of the test bearing 26, and reference numeral 26 c is a lower race of the test bearing 26. Further, reference numeral 27 denotes a lubricating oil, and this lubricating oil 27 is supplied into the test chamber 21 from a lubricating oil supply port (discharge port) 28. Reference numerals 29 and 30 denote an introduction port and a discharge port for the substitute chlorofluorocarbon, respectively. After the alternative chlorofluorocarbon 134a is introduced from the inlet 29 and sucked by the vacuum pump from the outlet 30 and the test chamber 21 is filled with the alternative chlorofluorocarbon 134a, the inlet 29 and outlet 30 are closed by valves.

Using such a testing machine, a rotational test of the thrust needle roller bearing was performed under the following conditions. The rotation test was stopped when the vibration value became five times the initial value or when the lower race (outer ring) reached 160 ° C. When the vibration value increased 5 times, the presence or absence of damage was confirmed with a stereomicroscope. If there was damage, the life was determined. If there was no damage, the rotation test was resumed. Further, when the lower race reached 160 ° C., it was judged that seizure had occurred, and the life was determined.
Rotational speed: 2500min ^-1
Load: 40% of dynamic load rating (P / C = 0.4)
Lubricant: Mineral oil whose ISO viscosity grade is ISO VG10 Atmospheric temperature: Room temperature (about 28 ° C)
Bearing temperature: 100 to 110 ° C. at the outer diameter of the lower race
Number of tests: 5 per type of bearing

The test results are shown in Tables 1-3. Moreover, the test result of Examples 1-8 and Comparative Examples 3-8 is shown in the graph of FIG. In addition, the numerical value of the lifetime in Table 1 to 3 and the graph of FIG. 3 is shown by the relative value when the lifetime of the comparative example 1 is set to 1.
The comparative example 1 is a bearing to which the technique described in the above-mentioned Patent Document 1 is applied, and an infinite number of independent minute depressions are randomly provided on the sliding surface, and the surface roughness of the surface on which the minute depressions are provided. Rmax is 1.0 μm, the parameter SK value of the surface roughness is −2.0, the average area of the minute recesses is 80 μm ² , and the ratio of the area of the minute recesses to the surface is 25%. In Comparative Example 1, barrel processing is performed as preprocessing.

Moreover, the comparative example 2 is also a bearing to which the prior art is applied. No shot peening treatment or barrel treatment is performed, and the rolling surface of the needle roller is superfinished.
As can be seen from Tables 1 to 3, Examples 1 to 18 were 5.3 times or more longer in life than Comparative Example 1 which is a conventional technique. Compared to Comparative Example 2, the lifetime was 10.6 times longer. In particular, as can be seen from the graph of FIG. 3, Examples 5 to 8 (which are plotted with black circles in the graph) in which a minute depression was formed on the rolling surface of the needle roller by the pretreatment had no pretreatment and were minute. Compared with Examples 1-4 which do not have a dent (it is plotted by the black triangle mark in the graph), it was longer life.

  Moreover, it turns out that it is preferable that the depth of a micro dent shall be 0.1-5 micrometers from the comparison with Examples 5-8 and Examples 13,14. Further, Examples 9 to 12 show that the thickness of the lubricating coating is preferably 0.1 to 8 μm. Further, Examples 15 to 18 show that the solid lubricant constituting the lubricating coating is preferably graphite fluoride. Comparative Examples 3 to 8 had a short life because the area ratio of the lubricating coating was low.

It is a fragmentary longitudinal cross-section which shows the structure of the thrust needle roller bearing which is one Embodiment of the rolling support apparatus which concerns on this invention. It is sectional drawing of the testing machine used for the life test of a bearing. It is a graph which shows the result of a life test.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Inner ring 1a Raceway surface 2 Outer ring 2a Raceway surface 3 Needle roller 3a Rolling surface

Claims (6)

A first member and a second member having raceway surfaces arranged opposite to each other, and rolling elements arranged to roll between the raceway surface of the first member and the raceway surface of the second member, A rolling support device in which one of the first member and the second member moves relative to the other through the rolling of the rolling element,
At least one of the raceway surface of the first member, the raceway surface of the second member, and the rolling surface of the rolling element has a lubricating coating composed of a solid lubricant in a portion having an area ratio of 75% or more. A rolling support device comprising:   The rolling support device according to claim 1, wherein the solid lubricant is graphite fluoride.   The rolling support device according to claim 1 or 2, wherein a thickness of the lubricating coating is 0.1 µm or more and 8 µm or less.   Of the raceway surface of the first member, the raceway surface of the second member, and the rolling surface of the rolling element, at least a portion of the rolling surface provided with the lubricating coating has a depth of 0.1 μm to 5 μm. Is formed, The rolling support apparatus as described in any one of Claims 1-3 characterized by the above-mentioned.   Of the raceway surface of the first member, the raceway surface of the second member, and the rolling surface of the rolling element, at least a portion provided with the lubricating coating has a center line average roughness Ra of 0.1 μm or more and 0. It is 5 micrometers or less, The rolling support apparatus as described in any one of Claims 1-4 characterized by the above-mentioned.   The rolling support device according to any one of claims 1 to 5, wherein the lubricating coating is formed by a shot peening method in which powder of the solid lubricant is projected.

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