WO2017126323A1 - Palier à éléments de roulement, dispositif de roulement, et procédé de fabrication de dispositif de roulement - Google Patents

Palier à éléments de roulement, dispositif de roulement, et procédé de fabrication de dispositif de roulement Download PDF

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Publication number
WO2017126323A1
WO2017126323A1 PCT/JP2017/000128 JP2017000128W WO2017126323A1 WO 2017126323 A1 WO2017126323 A1 WO 2017126323A1 JP 2017000128 W JP2017000128 W JP 2017000128W WO 2017126323 A1 WO2017126323 A1 WO 2017126323A1
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WO
WIPO (PCT)
Prior art keywords
rolling
outer ring
component
inner ring
elements
Prior art date
Application number
PCT/JP2017/000128
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English (en)
Japanese (ja)
Inventor
直哉 長谷川
Original Assignee
Ntn株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2016034480A external-priority patent/JP2017150597A/ja
Priority claimed from JP2016170758A external-priority patent/JP6964400B2/ja
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Priority to US16/071,851 priority Critical patent/US11028880B2/en
Priority to EP17741203.8A priority patent/EP3406923A4/fr
Priority to CN201780007576.2A priority patent/CN108603530A/zh
Publication of WO2017126323A1 publication Critical patent/WO2017126323A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/32—Balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—Rollers; Needles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/64—Special methods of manufacture

Definitions

  • the present invention relates to a rolling bearing, a rolling device and a method of manufacturing the rolling device, and more particularly to a rolling bearing provided with first and second rolling parts, a rolling device and a method of manufacturing the rolling device.
  • a rolling device such as a rolling bearing is used in an environment where the oil film formation is insufficient due to poor lubrication of the rolling parts, surface damage such as peeling or seizure and peeling starting from this surface damage Occurs on the surface of the rolling portion. This reduces the life of the rolling device.
  • Non-Patent Document 1 the value of the oil film parameter ⁇ ⁇ , which indicates the severity of the lubrication condition, between the inner and outer rings and rolling elements in the rolling bearing is about
  • the rolling bearing has a long life of 1.2 or more, but under the condition that the value of the oil film parameter ⁇ ⁇ is less than about 1.2, surface rolling of the rolling bearing occurs, and surface rolling starts. It is stated that the life is reduced.
  • Patent Document 1 JP-A-2006-161887
  • Patent Document 2 JP-A-2006-161887
  • Patent Document 3 JP-A-2006-161887
  • Patent Document 2 JP-A-2006-161887
  • Methods of forming and coating solid lubricant in the recesses are described.
  • Patent Document 2 Japanese Patent Laid-Open No. 4-265480
  • Patent Document 2 describes a method in which minute recesses are randomly formed in the rolling portion to enhance the oil film forming ability.
  • there is a method of reducing the surface roughness of the rolling portion of the rolling bearing to the extent that surface damage does not occur for example, by superfinishing, barrel polishing or burnishing.
  • the present invention has been made in view of the above problems, and an object thereof is a rolling bearing capable of easily achieving a long life by suppressing surface damage even when used in a state in which the oil film forming property of the rolling portion is poor. To provide a method of manufacturing a moving device and a rolling device.
  • the rolling device comprises a first rolling part made of high carbon chromium bearing steel and a second rolling part in contact with the first rolling part and made of high carbon chromium bearing steel There is.
  • the arithmetic mean roughness (Ra) of the surface of the rolling portion of the first rolling component is larger than the arithmetic mean roughness of the surface of the rolling portion of the second rolling component.
  • the arithmetic mean roughness of the surface of the rolling portion of the second rolling component is not less than 0.07 ⁇ m and not more than 0.20 ⁇ m.
  • the fine projections present on the surface of the rolling portion of the first rolling component come into contact with the surface of the rolling portion of the second rolling component, whereby the first rolling component is
  • the fine projections are smoothed by friction and plastic deformation so that the inclination of the projections is reduced.
  • Such a phenomenon is referred to herein as the familiarity of the protrusion.
  • the local surface pressure of the part which protrusion in the surface of the rolling part of the 1st and 2nd rolling parts contacts is reduced. Therefore, damage to the surface of the rolling portion of the second rolling component due to the contact between the protrusions of the rolling portions of the first and second rolling components can be suppressed. Thereby, the life reduction of the rolling device due to the damage of the surface of the rolling portion of the second rolling component can be suppressed, and the long life of the rolling device can be realized.
  • the arithmetic mean roughness of the surface of the rolling portion of the first rolling component is preferably 0.70 ⁇ m or less. In this way, the inclination of the projections can be reduced by the familiarity of the projections on the surface of the rolling portion of the first rolling component, and damage to the surface of the second rolling portion can be suppressed. .
  • the surface of the rolling portion of the first rolling part can be made by combining the arithmetic mean roughness of the surfaces of the rolling portions of the first and second rolling parts with the above.
  • the slope of the minute roughness projections can be made sufficiently small.
  • the root mean square inclination of the surface of the rolling portion of the second rolling component is preferably 0.074 or more and 0.100 or less. In this way, the inclination of the projections can be reduced by the familiarity of the projections on the surface of the rolling portion of the first rolling component as described above, and damage to the surface of the second rolling component can be reduced. It can be suppressed.
  • the Rockwell hardness of the rolling portion of the first rolling component is lower than the Rockwell hardness of the rolling portion of the second rolling component, and the second rolling component
  • the Rockwell hardness of the rolling portion is preferably 61.5 HRC or more.
  • the first rolling component is compared to the case where the above-mentioned relationship does not hold between the hardness of the rolling portion of the first rolling component and the rolling portion of the second rolling component.
  • the minute roughness projections on the surface of the rolling portion of the second embodiment inhibit the progress of fatigue on the surface of the rolling portion of the second rolling component due to contact with the surface of the rolling portion of the second rolling component be able to.
  • the Rockwell hardness of the rolling portion of the first rolling component is lower by 0.5 HRC or more than the Rockwell hardness of the rolling portion of the second rolling component.
  • the rolling part of the first rolling part and the rolling part of the second rolling part are respectively the surface of the rolling part of the first rolling part and the rolling of the second rolling part Includes the surface of the part.
  • the rolling device it is preferable to have a film containing at least one of an iron oxide or a compound on the surface of the rolling portion of the first rolling component.
  • the film in the above-mentioned rolling device contains iron trioxide.
  • the material of the microroughness projections on the surface of the rolling portion of the first rolling component can be made brittle. Therefore, the minute projections on the surface of the rolling portion of the first rolling part come in contact with the surface of the rolling portion of the second rolling part, whereby fine projections of the first rolling part The slope can easily be made sufficiently small.
  • the rolling bearing of the present invention is a rolling bearing as the above-described rolling device.
  • the rolling bearing is disposed so as to contact a plurality of rolling elements, a plurality of rolling elements outside the plurality of rolling elements, and an outer ring having an outer ring raceway surface on an inner circumferential surface, and a plurality inside the plurality of rolling elements And an inner ring having an inner ring raceway surface on an outer peripheral surface thereof.
  • the outer ring and the inner ring are first rolling parts, and the plurality of rolling elements are second rolling parts.
  • the rolling bearing of the present invention is a rolling bearing as the above-described rolling device.
  • the rolling bearing is disposed so as to contact a plurality of rolling elements, a plurality of rolling elements outside the plurality of rolling elements, and an outer ring having an outer ring raceway surface on an inner circumferential surface, and a plurality inside the plurality of rolling elements And an inner ring having an inner ring raceway surface on an outer peripheral surface thereof.
  • the outer ring and the inner ring are second rolling parts, and the plurality of rolling elements are first rolling parts.
  • the value of the oil film parameter in the region between the outer ring and each of the plurality of rolling elements and in the region between the inner ring and each of the plurality of rolling elements is 1.2 or less .
  • the phenomenon that the above-mentioned projections conform to each other proceeds under the condition that the oil film parameter ⁇ of 1.2 or less is not good for the oil film forming property of the rolling parts. Further, under the condition that the oil film parameter ⁇ is 1.2 or less, the life reduction due to the surface damage of the second rolling component by the projection of the first rolling component is likely to occur. For this reason, when the oil film parameter ⁇ is 1.2 or less, under the condition that the life reduction is originally likely to occur, the rolling of the outer ring raceway surface and the inner ring raceway surface is caused by the contact between the minute projections The effect of suppressing damage to the surface of the rolling portion of the moving body can be exhibited. Therefore, the long life of the rolling bearing can be realized by the fitting of the projections.
  • a first rolling component made of high carbon chromium bearing steel is prepared.
  • a second rolling part made of high carbon chromium bearing steel is prepared.
  • Arithmetic mean roughness of the surface of the rolling part of the first rolling part is greater than the arithmetic mean roughness of the surface of the rolling part of the second rolling part Is processed.
  • the second rolling component is processed such that the arithmetic mean roughness of the surface of the rolling portion of the second rolling component is not less than 0.07 ⁇ m and not more than 0.20 ⁇ m. If this is done, it is possible to realize the long life of the rolling device due to the fitting of the projections as described above.
  • the first and second rolling parts be tempered and then tempered.
  • the first rolling component is subjected to chemical conversion treatment after tempering treatment, and an oxide or compound of iron on the surface of the rolling portion of the first rolling component by chemical conversion treatment It is preferable that a film containing at least one of the above is formed. Compared with the case where it does not have a film on the surface of the rolling portion of the first rolling part and this is formed of ordinary steel, the conformity of the projections due to rolling is promoted.
  • the first rolling component is tempered by the heating condition of high temperature and / or long time than the second rolling component. That is, the first rolling component may be tempered at a higher temperature than the second rolling component and under a long-time heating condition.
  • the conditions of the tempering treatment performed after the quenching treatment of the first and second rolling parts are adjusted.
  • the Rockwell hardness of the rolling portion of the first rolling component is lower than the Rockwell hardness of the rolling portion of the second rolling component, and the second rolling is performed.
  • the first and second rolling parts are processed such that the Rockwell hardness of the rolling parts of the parts is 61.5 HRC or more.
  • the first rolling component is compared to the case where the above-mentioned relationship does not hold between the hardness of the rolling portion of the first rolling component and the rolling portion of the second rolling component.
  • the minute roughness projections on the surface of the rolling portion of the second embodiment inhibit the progress of fatigue on the surface of the rolling portion of the second rolling component due to contact with the surface of the rolling portion of the second rolling component be able to.
  • the long life of the rolling device can be realized by the two effects of fitting of projections and suppression of fatigue progress. Can.
  • the Rockwell hardness of the rolling portion of the first rolling component is lower by 0.5 HRC or more than the Rockwell hardness of the rolling portion of the second rolling component.
  • the rolling part of the first rolling part and the rolling part of the second rolling part are respectively the surface of the rolling part of the first rolling part and the rolling of the second rolling part Includes the surface of the part.
  • the surface of the rolling portion of the first rolling part may not be subjected to any of superfinishing, barrel polishing and burnishing. That is, even without these processes, the surface roughness of the rolling portion can be made sufficiently small to the extent that surface damage does not occur.
  • the first rolling component is processed such that the arithmetic mean roughness of the surface of the rolling portion of the first rolling component is 0.70 ⁇ m or less.
  • the second rolling component is processed so that the root mean square inclination of the surface of the rolling portion of the second rolling component is 0.074 or more and 0.100 or less.
  • the rolling device comprises a first rolling part made of high carbon chromium bearing steel and a second rolling part in contact with the first rolling part and made of high carbon chromium bearing steel There is.
  • the Rockwell hardness of the surface of the rolling portion of the first rolling component is lower than the Rockwell hardness of the surface of the rolling portion of the second rolling component.
  • the arithmetic mean roughness (Ra) of the surface of the rolling portion of the first rolling component is larger than the arithmetic mean roughness of the surface of the rolling portion of the second rolling component.
  • the arithmetic mean roughness of the surface of the rolling portion of the second rolling component is 0.07 ⁇ m or more and 0.10 ⁇ m or less, and the root mean square slope (R ⁇ q) of the surface of the rolling portion of the second rolling component is It is 0.07 or more and 0.10 or less.
  • the fine projections present on the surface of the rolling portion of the first rolling component come into contact with the surface of the rolling portion of the second rolling component, whereby the first rolling component is
  • the fine projections are smoothed by friction or plastic deformation so that the inclination angle of the projections (or the curvature of the tip of the projections) is reduced.
  • Such a phenomenon is referred to herein as the familiarity of the protrusion.
  • the local surface pressure of the part which protrusion in the surface of the rolling part of the 1st and 2nd rolling parts contacts is reduced. Therefore, damage to the surface of the rolling portion of the second rolling component due to the contact between the protrusions of the rolling portions of the first and second rolling components can be suppressed. Thereby, the life reduction of the rolling device due to the damage of the surface of the rolling portion of the second rolling component can be suppressed, and the long life of the rolling device can be realized.
  • the Rockwell hardness of the surface of the rolling portion of the first rolling component is 0.5 HRC or more lower than the Rockwell hardness of the surface of the rolling portion of the second rolling component Is preferred. In this way, the inclination angle of the projection can be reduced by the familiarity of the projection on the surface of the rolling portion of the first rolling component, and the damage to the surface of the second rolling portion can be suppressed. it can.
  • the rolling bearing of the present invention is a rolling bearing as the above-described rolling device.
  • the rolling bearing is disposed so as to contact a plurality of rolling elements, a plurality of rolling elements outside the plurality of rolling elements, and an outer ring having an outer ring raceway surface on an inner circumferential surface, and a plurality inside the plurality of rolling elements And an inner ring having an inner ring raceway surface on an outer peripheral surface thereof.
  • the outer ring and the inner ring are first rolling parts, and the plurality of rolling elements are second rolling parts.
  • the rolling bearing of the present invention is a rolling bearing as the above-described rolling device.
  • the rolling bearing is disposed so as to contact a plurality of rolling elements, a plurality of rolling elements outside the plurality of rolling elements, and an outer ring having an outer ring raceway surface on an inner circumferential surface, and a plurality inside the plurality of rolling elements And an inner ring having an inner ring raceway surface on an outer peripheral surface thereof.
  • the outer ring and the inner ring are second rolling parts, and the plurality of rolling elements are first rolling parts.
  • the value of the oil film parameter in the region between the outer ring and each of the plurality of rolling elements and in the region between the inner ring and each of the plurality of rolling elements is 1.2 or less .
  • the phenomenon that the above-mentioned projections conform to each other proceeds under the condition that the oil film parameter ⁇ of 1.2 or less is not good for the oil film forming property of the rolling parts. Further, under the condition that the oil film parameter ⁇ is 1.2 or less, the life reduction due to the surface damage of the second rolling component by the projection of the first rolling component is likely to occur. For this reason, when the oil film parameter ⁇ is 1.2 or less, under the condition that the life reduction is originally likely to occur, the rolling of the outer ring raceway surface and the inner ring raceway surface is caused by the contact between the minute projections The effect of suppressing damage to the surface of the rolling portion of the moving body can be exhibited. Therefore, the long life of the rolling bearing can be realized by the fitting of the projections.
  • a first rolling component made of high carbon chromium bearing steel is prepared.
  • a second rolling part made of high carbon chromium bearing steel is prepared.
  • the first and second rolling parts are configured such that the Rockwell hardness of the surface of the rolling portion of the first rolling part is lower than the Rockwell hardness of the surface of the rolling portion of the second rolling part It is processed.
  • Arithmetic mean roughness of the surface of the rolling part of the first rolling part is greater than the arithmetic mean roughness of the surface of the rolling part of the second rolling part Is processed.
  • the arithmetic mean roughness of the surface of the rolling portion of the second rolling component is 0.07 ⁇ m or more and 0.10 ⁇ m or less, and the root mean square inclination of the surface of the rolling portion of the second rolling component is 0.07 or more
  • the second rolling component is processed to be 0.10 or less. In this way, the long life of the rolling device can be realized as described above.
  • the first and second rolling parts be tempered and then tempered. This is a process necessary to fulfill the function of the rolling bearing.
  • the surface of the rolling portion of the first rolling component is finished by grinding or polishing using a rotary grindstone.
  • the surface of the rolling portion of the first rolling component may not be subjected to any of superfinishing, barrel polishing and burnishing. That is, even without these processes, the surface roughness of the rolling portion can be made sufficiently small to the extent that surface damage does not occur.
  • the minute projections on the surface of the rolling portion of the rolling part conform to each other, and the local surface pressure of the portion where the projections contact with each other is reduced, whereby the surface of the rolling portion of the rolling part It is possible to suppress the damage and the decrease in life associated therewith.
  • Three-dimensional shape (A) of the surface of the rolling portion of the test piece under the conditions of the comparative example of the present embodiment in Example 1 after the peeling resistance evaluation test and the rotation of the test piece under the conditions of the present embodiment It is with the three-dimensional shape (B) after the peeling performance evaluation test of the surface of a moving part.
  • FIG. It is a microscope enlarged photograph after the peeling performance evaluation test of the surface of the rolling part of the test piece by the conditions of each test example in Example 2.
  • FIG. It is a schematic sectional drawing which shows the structure of the tapered roller bearing in this Embodiment. It is a schematic sectional drawing which shows the structure of the cylindrical roller bearing in this Embodiment. It is a flowchart which shows the processing process of the 1st rolling part in Embodiment 3, 4.
  • a microscopic enlarged photograph after the peeling resistance evaluation test and the surface of the rolling portion of the test piece according to the conditions of the example of the present embodiment It is with the microscope enlarged photograph after the peeling performance evaluation test.
  • Embodiment 1 First, the configuration of a rolling bearing as an example of the rolling device according to the present embodiment will be described with reference to FIGS. 1 and 2. Although a deep groove ball bearing is described here as an example of a rolling bearing, the present embodiment can also be applied to rolling bearings of types other than deep groove ball bearings in the same manner as described below.
  • deep groove ball bearing 1 of the present embodiment includes an annular outer ring 11, an annular inner ring 12 disposed on the inner side of outer ring 11 with respect to center line C, an outer ring 11 and an inner ring 12. , And an annular cage 14 for holding the outer ring 11, the inner ring 12 and the plurality of balls 13. As shown in FIG.
  • the outer ring 11 is disposed to be in contact with the plurality of balls 13 outside the plurality of balls 13.
  • the outer ring 11 has an outer ring raceway surface 11A on the inner circumferential surface formed on the inner side with respect to the center line C.
  • the inner ring 12 is disposed to contact the plurality of balls 13 inside the plurality of balls 13.
  • the inner race 12 has an inner raceway surface 12A on the outer peripheral surface formed on the outer side with respect to the center line C.
  • the outer ring 11 and the inner ring 12 are disposed such that the outer ring raceway surface 11A and the inner ring raceway surface 12A face each other.
  • the plurality of balls 13 have a spherical shape, and have a ball rolling surface 13A on the surface thereof. In other words, the entire surface of each of the plurality of balls 13 is the ball rolling surface 13A.
  • the plurality of balls 13 are configured to roll between the outer ring raceway surface 11A and the inner ring raceway surface 12A.
  • a plurality of balls 13 are arranged side by side so as to be in contact with the outer ring raceway surface 11A and the inner ring raceway surface 12A in the ball rolling surface 13A and to have a pitch of an interval in the circumferential direction by the cage 14.
  • each of the plurality of balls 13 is rollably held on the annular path.
  • a grease composition (not shown) is enclosed in a space sandwiched by the outer ring 11 and the inner ring 12, more specifically, a space defined by the outer ring raceway surface 11A and the inner ring raceway surface 12A.
  • An oil film is formed between each of the outer ring 11 and the inner ring 12 and the ball 13 by this grease composition, and the lubricating state between each of the outer ring 11 and the inner ring 12 and the ball 13 is well maintained. Further, the value of the oil film parameter ⁇ in the region between the outer ring 11 and each of the plurality of balls 13 and in the region between each of the inner ring 12 and each of the plurality of balls 13 is 1.2 or less.
  • an outer ring 11, an inner ring 12 and a ball 13 as rolling parts constituting the deep groove ball bearing 1 will be described.
  • a ball 13 as a second rolling part is in contact with each of the outer ring 11 and the inner ring 12 as a first rolling part.
  • Each of the outer ring 11, the inner ring 12 and the ball 13 is a high carbon chromium bearing steel, for example, made of JIS standard SUJ2.
  • the rolling portion of the outer ring 11 is a region including the outer ring raceway surface 11A, and the surface of the rolling portion of the outer ring 11 constitutes the outer ring raceway surface 11A.
  • the rolling portion of the inner ring 12 is a region including the inner ring raceway surface 12A, and the surface of the rolling portion of the inner ring 12 constitutes the inner ring raceway surface 12A.
  • the rolling portion of the ball 13 is a region including the ball rolling surface 13A, and the surface of the rolling portion of the ball 13 constitutes the ball rolling surface 13A.
  • the arithmetic mean roughness (Ra) of the outer ring raceway surface 11A and the inner ring raceway surface 12A is larger than the arithmetic mean roughness of the ball rolling surface 13A, and specifically, the outer ring raceway surface 11A and the inner ring
  • the arithmetic mean roughness of the raceway surface 12A is 0.70 ⁇ m or less
  • the arithmetic mean roughness of the ball rolling surface 13A is 0.07 ⁇ m or more and 0.20 ⁇ m or less.
  • the root mean square inclination (R ⁇ q) of the ball rolling surface 13A is not less than 0.074 and not more than 0.100.
  • the Rockwell hardness (HRC) of the surface of the rolling portion of the first rolling component that is, the outer ring raceway surface 11A and the inner ring raceway surface 12A is the same as that of the rolling portion of the second rolling component. It is lower by 0.5 HRC or more than the Rockwell hardness of the surface, that is, the ball rolling surface 13A. Further, the Rockwell hardness of the ball rolling surface 13A is 61.5 HRC or more.
  • a film 11 B is formed on the surface of the rolling portion of the outer ring 11.
  • a film 12 B is formed on the surface of the rolling portion of the inner ring 12.
  • the films 11B and 12B contain at least one of an oxide or a compound of iron, and particularly preferably contain iron trioxide. That is, it is preferable that each of the film 11B formed on the surface of the rolling portion of the outer ring 11 and the film 12B formed on the surface of the rolling portion of the inner ring 12 be formed by black dyeing.
  • an outer ring 11 and an inner ring 12 are prepared as first rolling parts made of JIS standard SUJ2 (S01). Further, a ball 13 as a second rolling part made of JIS standard SUJ2 is prepared (S02).
  • the JIS standard SUJ2 as the material is subjected to hardening treatment (S11) and then to tempering treatment (S12). Thereafter, the arithmetic mean roughness of the outer ring raceway surface 11A of the outer ring 11 and the inner ring raceway surface 12A of the inner ring 12 is processed to be larger than the arithmetic mean roughness of the ball rolling surface 13A of the ball 13. Specifically, the arithmetic mean roughness of the outer ring raceway surface 11A and the inner ring raceway surface 12A is machined to 0.70 ⁇ m or less (S13).
  • the outer ring raceway surface 11A which is the surface of the rolling portion of the outer ring 11 and the inner ring raceway surface 12A which is the surface of the rolling portion of the inner ring 12 by this chemical conversion treatment is a coating 11B of at least one of iron oxide and compound 12B is formed.
  • the material is subjected to a hardening treatment (S21) and then a tempering treatment (S22) as a material JIS standard SUJ2 which is a material,
  • S21 hardening treatment
  • S22 tempering treatment
  • the arithmetic mean roughness of the rolling surface 13A is smaller than the arithmetic mean roughness of the outer ring raceway surface 11A of the outer ring 11 and the inner ring raceway surface 12A of the inner ring 12.
  • the arithmetic average roughness of the ball rolling surface 13A is 0.07 ⁇ m or more and 0.20 ⁇ m or less, and the root mean square inclination (R ⁇ q) of the ball rolling surface 13A is 0.074 or more and 0.100 It processes so that it may become the following (S23). No subsequent conversion treatment is performed.
  • the tempering treatment (S12) is higher in temperature and / or longer than the tempering treatment (S22). It is tempered according to the heating condition of time. That is, the tempering treatment (S12) may be a higher temperature than the tempering treatment (S22) and may be tempered under a long heating condition, and the tempering treatment (S12) may be a high temperature than the tempering treatment (S22) However, tempering may be performed under conditions that are not for a long time, or conditions that are not high temperature but for a long time.
  • the Rockwell hardness of the outer ring raceway surface 11A and the inner ring raceway surface 12A is lower than the Rockwell hardness of the ball rolling surface 13A, and the Rockwell hardness of the ball rolling surface 13A is 61.
  • the outer ring 11, the inner ring 12 and the ball 13 are processed so as to be 5 HRC or more.
  • the arithmetic average roughness of the outer ring raceway surface 11A as the surface of the rolling portion of the outer ring 11 and the inner ring raceway surface 12A as the surface of the rolling portion of the inner ring 12 It is larger than the arithmetic mean roughness of the ball rolling surface 13A as the surface of the rolling portion.
  • the arithmetic average roughness of the outer ring raceway surface 11A and the inner ring raceway surface 12A is 0.70 ⁇ m or less
  • the arithmetic average roughness of the ball rolling surface 13A is 0.07 ⁇ m or more and 0.20 ⁇ m or less.
  • the root mean square inclination of the ball rolling surface 13A is not less than 0.074 and not more than 0.100.
  • the value of the arithmetic average roughness is smaller than, for example, the value of the arithmetic average roughness of the ball rolling surface 13A is less than 0.07 ⁇ m.
  • the minute projections included in a large number on the outer ring raceway surface 11A and the inner ring raceway surface 12A, which are larger than the ball rolling surface 13A, are easily fitted.
  • the outer ring raceway surface 11A and the inner ring raceway surface 12A come into contact with the ball rolling surface 13A after a short time from the start of the operation of the deep groove ball bearing 1 by the above two actions, thereby the outer ring raceway surface 11A and the inner ring raceway surface 12A.
  • the inclination of the minute projections can be reduced.
  • the local contact surface pressure between the minute projections of the outer ring raceway surface 11A and the inner ring raceway surface 12A and the flat surface or the minute projections of the ball rolling surface 13A in contact with the projections decreases.
  • the Rockwell hardness of the outer ring raceway surface 11A and the inner ring raceway surface 12A is adjusted to be relatively lower than the Rockwell hardness of the ball rolling surface 13A. Furthermore, the Rockwell hardness of the ball rolling surface 13A is adjusted to 61.5 HRC or more. In this way, the deep groove ball bearing 1 is used under conditions where the oil film formability is not good because the lubricating state between the outer ring 11 and the inner ring 12 and the ball 13 is not good, and the outer ring raceway surface 11A and the inner ring raceway surface Even if the minute projections 12A come in contact with the ball rolling surface 13A, damage or fatigue of the ball rolling surface 13A can be suppressed.
  • the outer ring raceway surface 11A and the inner ring raceway surface 12A are tempered by heating conditions higher than the ball rolling surface 13A and / or for a long time, whereby the outer ring raceway surface 11A, the inner ring raceway surface 12A and the ball rolling surface 13A are It can process so that hardness may become said conditions.
  • the values of the oil film parameter ⁇ ⁇ ⁇ ⁇ in the region between the outer ring 11 and each of the plurality of balls 13 and in the region between each of the inner ring 12 and each of the plurality of balls 13 are 1.2 or less. If the value of the hydraulic pressure parameter ⁇ is 1.2 or less, the frequency of contact between the minute roughness projections of the outer ring 11 and the ball 13 and the minute roughness projections of the inner ring 12 and the ball 13 increases. Therefore, the fitting of the minute roughness projections of the rolling portions of the outer ring 11 and the inner ring 12 occurs.
  • the deep groove ball bearing 1 of the present embodiment can be basically described similarly using the same drawing as the deep groove ball bearing 1 of the first embodiment, and therefore detailed description will be omitted.
  • the ball 13 is disposed as a first rolling component
  • the outer ring 11 and the inner ring 12 are disposed as a second rolling component.
  • the deep groove ball bearing 1 of the present embodiment is different from the deep groove ball bearing 1 of the first embodiment in this point.
  • the arithmetic mean roughness of ball rolling surface 13A is larger than the arithmetic mean roughness of outer raceway surface 11A and inner raceway surface 12A, and the arithmetic mean roughness of ball rolling surface 13A is 0.70 ⁇ m.
  • the arithmetic mean roughness of the outer ring raceway surface 11A and the inner ring raceway surface 12A is not less than 0.07 ⁇ m and not more than 0.20 ⁇ m.
  • the balls 13 are subjected to chemical conversion treatment after tempering treatment.
  • the Rockwell hardness (HRC) of the ball rolling surface 13A is lower than the Rockwell hardness of the outer ring raceway surface 11A and the inner ring raceway surface 12A, and the lock of the outer ring raceway surface 11A and the inner ring raceway surface 12A Well hardness is 61.5 HRC or more.
  • the Rockwell hardness (HRC) of the ball rolling surface 13A is preferably 0.5 HRC or more lower than the Rockwell hardness of the outer ring raceway surface 11A and the inner ring raceway surface 12A.
  • the effect of suppressing damage to the outer raceway surface 11A and the inner raceway surface 12A, which are the second rolling parts, can be enhanced in the same manner as in the first embodiment. .
  • the tapered roller bearing 102 of the present embodiment includes an annular outer ring 120, an annular inner ring 121 disposed on the inner side of the outer ring 120 with respect to the center line C, an outer ring 120 and an inner ring 121. And an annular retainer 123 for holding the outer ring 120, the inner ring 121, and the plurality of rollers 122. As shown in FIG.
  • the outer ring 120 is disposed to be in contact with the plurality of rollers 122 outside the plurality of rollers 122.
  • the outer ring 120 has an outer ring raceway surface 120 ⁇ / b> A on the inner circumferential surface formed on the inner side with respect to the center line C.
  • the inner ring 121 is disposed to contact the plurality of rollers 122 inside the plurality of rollers 122.
  • the inner race 121 has an inner raceway surface 121 ⁇ / b> A on the outer peripheral surface formed on the outer side with respect to the center line C.
  • the outer ring 120 and the inner ring 121 are disposed such that the outer ring raceway surface 120A and the inner ring raceway surface 121A face each other.
  • the plurality of rollers 122 have roller rolling surfaces 122A on their surfaces. In other words, the entire surface of each of the plurality of rollers 122 is a roller rolling surface 122A.
  • the plurality of rollers 122 are configured to roll between the outer ring raceway surface 120A and the inner ring raceway surface 121A.
  • a plurality of rollers 122 are arranged side by side so as to be in contact with the outer ring raceway surface 120A and the inner ring raceway surface 121A at the roller rolling surface 122A and to have a pitch of a certain interval in the circumferential direction by the cage 123. Thereby, each of the plurality of rollers 122 is rotatably held on the annular raceway of the outer ring 120 and the inner ring 121.
  • the holder 123 is made of synthetic resin.
  • a cone including the outer ring raceway surface 120A, a cone including the inner ring raceway surface 121A, and a cone including the locus of the rotation axis when the roller 122 rolls are on the center line of the bearing. It is configured to meet at one point. With the above configuration, the outer ring 120 and the inner ring 121 of the tapered roller bearing 102 can rotate relative to each other.
  • cylindrical roller bearing 103 of the present embodiment includes an annular outer ring 130, an annular inner ring 131 disposed on the inner side of outer ring 130 with respect to center line C, an outer ring 130 and an inner ring 131. And an annular cage 133 for holding the outer ring 130, the inner ring 131 and the plurality of rollers 132.
  • the outer ring 130 is disposed to be in contact with the plurality of rollers 132 outside the plurality of rollers 132.
  • the outer ring 130 has an outer ring raceway surface 130 ⁇ / b> A on the inner circumferential surface formed on the inner side with respect to the center line C.
  • the inner ring 131 is arranged to contact the plurality of rollers 132 inside the plurality of rollers 132.
  • the inner race 131 has an inner raceway surface 131A on the outer peripheral surface formed on the outer side with respect to the center line C.
  • the outer ring 130 and the inner ring 131 are disposed such that the outer ring raceway surface 130A and the inner ring raceway surface 131A face each other.
  • the plurality of rollers 132 have a cylindrical shape, and have roller rolling surfaces 132A on their surfaces. In other words, the entire surface of each of the plurality of rollers 132 is a roller rolling surface 132A.
  • the plurality of rollers 132 are configured to roll between the outer ring raceway surface 130A and the inner ring raceway surface 131A.
  • a plurality of rollers 132 are arranged side by side so as to be in contact with the outer ring raceway surface 130A and the inner ring raceway surface 131A at the roller rolling surface 132A and to have a circumferential pitch by the cage 133.
  • each of the plurality of rollers 132 is rotatably held on the annular raceway of the outer ring 130 and the inner ring 131.
  • the cage 133 is made of synthetic resin. With the above configuration, the outer ring 130 and the inner ring 131 of the cylindrical roller bearing 103 can rotate relative to each other.
  • a grease composition is enclosed in a space between the outer ring 120 and the inner ring 121 in FIG. 9, more specifically, a space between the outer ring raceway surface 120A and the inner ring raceway surface 121A.
  • An oil film is formed between each of the outer ring 120 and the inner ring 121 by this grease composition.
  • the value of the oil film parameter ⁇ in the region between the outer ring 120 and each of the plurality of rollers 122 and in the region between each of the inner ring 121 and each of the plurality of rollers 122 is 1.2 or less.
  • the grease composition is enclosed in a raceway space which is a space sandwiched between the outer ring raceway surface 130A and the inner ring raceway surface 131A as in FIG. 9 also in FIG.
  • outer ring 120, the inner ring 121 and the rollers 122 as rolling parts constituting the tapered roller bearing 102 will be described.
  • a roller 122 as a second rolling part is in contact with each of the outer ring 120 and the inner ring 121 as a first rolling part.
  • Each of the outer ring 120, the inner ring 121 and the roller 122 is a high carbon chromium bearing steel, for example, made of JIS standard SUJ2. The same applies to the outer ring 130, the inner ring 131, and the rollers 132 that constitute the cylindrical roller bearing 103.
  • the rolling portion of outer ring 120 in FIG. 9 is a region including outer ring raceway surface 120A, and the surface of the rolling portion of outer ring 120 constitutes outer ring raceway surface 120A.
  • the rolling portion of the inner ring 121 is a region including the inner ring raceway surface 121A, and the surface of the rolling portion of the inner ring 121 constitutes the inner ring raceway surface 121A.
  • the rolling portion of the roller 122 is a region including the rolling surface 122A, and the surface of the rolling portion of the roller 122 constitutes the rolling surface 122A.
  • the Rockwell hardness of the outer ring raceway surface 120A and the inner ring raceway surface 121A is lower than the Rockwell hardness of the roller rolling surface 122A. Specifically, it is preferable that the Rockwell hardness of the outer ring raceway surface 120A and the inner ring raceway surface 121A be 0.5 HRC or more lower than the Rockwell hardness of the roller rolling surface 122A.
  • the arithmetic average roughness (Ra) standardized by JIS B 0601-2001 of the outer ring raceway surface 120A and the inner ring raceway surface 121A is larger than the arithmetic average roughness of the roller rolling surface 122A.
  • the root mean square inclination (R ⁇ q) standardized by JIS B 0601-2001 of the outer ring raceway surface 120A and the inner ring raceway surface 121A is larger than the root mean square inclination of the roller rolling surface 122A.
  • the arithmetic average roughness of the outer ring raceway surface 120A and the inner ring raceway surface 121A is 0.70 ⁇ m or less, and the root mean square inclination is 0.30 or less. Further, the arithmetic average roughness of the roller rolling surface 122A is 0.07 ⁇ m or more and 0.10 ⁇ m or less, and the root mean square inclination is 0.07 or more and 0.10 or less.
  • an outer ring 120 and an inner ring 121 as first rolling parts made of JIS standard SUJ2 are prepared (S01).
  • a roller 122 is prepared as a second rolling component made of JIS standard SUJ2 (S02).
  • the material is subjected to a hardening treatment (S11) and then to a tempering treatment (S12).
  • the outer raceway surface 120A and the inner raceway surface 121A are processed (S13).
  • the Rockwell hardness of the outer ring raceway surface 120A and the inner ring raceway surface 121A is processed so as to be lower than the Rockwell hardness of the roller rolling surface 122A.
  • the arithmetic mean roughness of the outer ring raceway surface 120A of the outer ring 120 and the inner ring raceway surface 121A of the inner ring 121 is processed to be larger than the arithmetic mean roughness of the roller rolling surface 122A of the roller 122.
  • the root mean square inclination of the outer ring raceway surface 120A and the inner ring raceway surface 121A is processed to be larger than the root mean square inclination of the roller rolling surface 122A.
  • the Rockwell hardness of the outer ring raceway surface 120A and the inner ring raceway surface 121A be 0.5 HRC or more lower than the Rockwell hardness of the roller rolling surface 122A.
  • the arithmetic average roughness of the outer ring raceway surface 120A and the inner ring raceway surface 121A is processed so as to be 0.70 ⁇ m or less, and the root mean square inclination is 0.30 or less.
  • tempering treatment (S22) is carried out after the JIS standard SUJ2 which is a material is subjected to quenching treatment (S21). Thereafter, the arithmetic average roughness of the roller rolling surface 122A of the roller 122 is processed so as to be smaller than the arithmetic average roughness of the outer ring raceway surface 120A of the outer ring 120 and the inner ring raceway surface 121A of the inner ring 121.
  • the roller rolling surface 122A is processed so as to have an arithmetic average roughness of 0.07 ⁇ m or more and 0.10 ⁇ m or less and a root mean square inclination of 0.07 or more and 0.10 or less (S23).
  • each raceway surface in the above steps (S13) and (S23) is finished by grinding or polishing using a rotary grindstone. That is, even if the outer surface raceway surface 120A and the inner ring surface 121A as the first rolling parts are not processed to improve surface roughness such as superfinishing, barrel polishing and burnishing, Good. For example, even if it is difficult to perform superfinishing or the like in which the outer ring raceway surface 120A and the inner ring raceway surface 121A are reduced in arithmetic mean roughness, root mean square inclination, etc.
  • the combination of the values of the arithmetic mean roughness and the root mean square slope with the raceway surfaces 20A and 21A and the rolling surface 122A may be set as the above-mentioned numerical range.
  • the tip shapes of the projections of the outer ring raceway surface 120A and the inner ring raceway surface 121A can be smoothed by conforming without superfinishing the outer ring raceway surface 120A and the inner ring raceway surface 121A. Therefore, the possibility of occurrence of damage due to rolling fatigue such as peeling on the roller rolling surface 122A can be reduced, and a reduction in the life of the rolling device due to the damage can be suppressed.
  • the Rockwell hardness of the roller rolling surface 122A as the surface of the moving part is 0.5 HRC or more lower.
  • the arithmetic mean roughness of the outer ring raceway surface 120A and the inner ring raceway surface 121A is larger than the arithmetic mean roughness of the roller rolling surface 122A.
  • the arithmetic average roughness of the roller rolling surface 122A is 0.07 ⁇ m or more and 0.10 ⁇ m or less, and the roller rolling surface 122A is processed so that the root mean square inclination is 0.07 or more and 0.10 or less .
  • the arithmetic mean roughness can be reduced compared to, for example, the case where the value of the arithmetic mean roughness of roller rolling surface 122A is less than 0.07 ⁇ m.
  • the minute projections included in a large number in the outer ring raceway surface 120A and the inner ring raceway surface 121A whose values are larger than the roller rolling surface 122A are easily fitted.
  • the Rockwell hardness of the surface of each rolling portion of the outer ring 120 and the inner ring 121 lower than the hardness of the roller rolling surface 122A, the roughness of the outer ring raceway surface 120A and the inner ring raceway surface 121A is further reduced.
  • the projections can be made more familiar.
  • the outer ring raceway surface 120A and the inner ring raceway surface 121A come into contact with the roller rolling surface 122A after a short period of time from the start of operation of the tapered roller bearing 102, so that the rough surface present on the roller rolling surface 122A.
  • the projections of the stem wear or plastically deform large projections present on the outer ring raceway surface 120A and the inner ring raceway surface 121A. Thereby, the fit-in of large protrusions and the like present on the outer ring raceway surface 120A and the inner ring raceway surface 121A is promoted, and the tip shape of the projections is smoothed.
  • the local contact surface pressure between the minute projections of the outer ring raceway surface 120A and the inner ring raceway surface 121A and the flat surface or the minute projections of the roller rolling surface 122A in contact with the projections decreases. Therefore, it is possible to suppress the occurrence of damage to roller rolling surface 122A caused by, for example, minute projections on outer ring raceway surface 120A and inner ring raceway surface 121A. Therefore, for example, even if a method such as forming minute recesses on the surface such as outer ring raceway surface 120A at random and coating a solid lubricant there is not used, the tapered roller bearing 102 is damaged by damage to the roller rolling surface 122A. It is possible to suppress the reduction of the life. Therefore, the long life of the tapered roller bearing 102 can be realized.
  • the value of the arithmetic average roughness of the outer ring raceway surface 120A, the inner ring raceway surface 121A and the rolling surface 122A is adjusted. For this reason, even if the tapered roller bearing 102 is used under conditions where the oil film formability is not good because the lubricating state between the outer ring 120 and the inner ring 121 and 122 is not good, the outer ring raceway surface 120A and the inner ring raceway surface 121A. It is possible to suppress damage to the roller rolling surface 122A due to the contact with the minute projections of the Thereby, the long life of the tapered roller bearing 102 can be realized.
  • the values of the oil film parameter ⁇ in the region between the outer ring 120 and each of the plurality of rollers 122 and in the region between each of the inner ring 121 and each of the plurality of rollers 122 are 1.2 or less. Therefore, under the condition that the life of the tapered roller bearing 102 is likely to decrease because the surface rolling type separation occurs on the roller rolling surface 122A, the roller rolling due to the contact with the minute projections of the outer ring raceway 120A and the inner ring raceway 121A. Damage to the surface 122A can be suppressed. Thereby, the long life of the tapered roller bearing 102 can be realized effectively.
  • roller rolling surface 122A Since damage to roller rolling surface 122A is suppressed by the above method, in the present embodiment, superfinishing, barrel polishing, and burnishing on outer ring raceway surface 120A, inner ring raceway surface 121A and roller rolling surface 122A. There is no need to do any of the processing. Therefore, the process of machining the tapered roller bearing 102 can be simplified, and the cost can be reduced.
  • Embodiment 4 The tapered roller bearing 102 of the present embodiment can be basically described similarly using the same drawing as the tapered roller bearing 102 of the third embodiment, and therefore detailed description will be omitted. However, in the tapered roller bearing 102 of the present embodiment, the roller 122 is disposed as a first rolling component, and the outer ring 120 and the inner ring 121 are disposed as a second rolling component. The tapered roller bearing 102 of the present embodiment is different from the tapered roller bearing 102 of the third embodiment in this point.
  • the Rockwell hardness of the roller rolling surface 122A is, for example, 0.5 HRC or more lower than the Rockwell hardness of the outer ring raceway surface 120A and the inner ring raceway surface 121A.
  • the arithmetic mean roughness of the roller rolling surfaces 122A is larger than the arithmetic mean roughness of the outer ring raceway surface 120A and the inner ring raceway surface 121A.
  • the arithmetic mean roughness of the outer ring raceway surface 120A and the inner ring raceway surface 121A is 0.07 ⁇ m or more and 0.10 ⁇ m or less, and the root mean square inclination is 0.07 or more and 0.10 or less.
  • the root mean square inclination of the roller rolling surface 122A is larger than the root mean square inclination of the outer ring raceway surface 120A and the inner ring raceway surface 121A.
  • the arithmetic mean roughness of the roller rolling surface 122A is 0.70 ⁇ m or less, and the root mean square inclination is 0.30 or less.
  • the roller 132 can be applied as a first rolling part, and the outer ring 130 and the inner ring 131 can be applied as a second rolling part.
  • the method of manufacturing these tapered roller bearings 102 and cylindrical roller bearings 103 is basically the same as in Embodiment 3, although the first and second rolling parts are opposite to those in Embodiment 3. Therefore, the detailed description is omitted.
  • the effect of suppressing damage to the outer raceway surface 120A and the inner raceway surface 121A, which are the second rolling parts, can be enhanced similarly to the third embodiment. .
  • this shows a two-cylinder tester 2 used for the peeling resistance evaluation test.
  • the two-cylinder testing machine 2 has a drive side rotation axis D1 and a driven side rotation axis F1.
  • the driving side rotation shaft D1 is a member extending in the left and right direction in FIG. 5, and the motor M is connected to the left end in FIG.
  • the drive-side rotation axis D1 is rotatable with respect to a central axis C1 extending in the left-right direction in FIG. 5 by the motor M.
  • a drive-side test piece D2 is attached to the tip on the right side of the drive-side rotary shaft D1 in FIG.
  • the drive-side test strip D2 is a member corresponding to the first rolling component in each of the above-described embodiments, and is driven so as to be rotatable around the central axis C1 with the rotation of the drive-side rotary shaft D1. It was fixed to the tip on the right side of the side rotation axis D1.
  • the driven side rotation shaft F1 is a member extending in the left and right direction of FIG. 5, and is rotatable with respect to a central axis C2 extending in the left and right direction of FIG.
  • the left side is the tip end and the right side is the end.
  • the driven side test strip F2 is attached to the left end of the driven side rotation shaft F1 in FIG.
  • the driven-side test strip F2 is a member corresponding to the second rolling component in each of the above-described embodiments, and is driven so as to be rotatable around the central axis C2 with the rotation of the driven-side rotation shaft F1. It was fixed to the tip on the left side of the side rotation axis F1.
  • the end of the drive side rotation shaft D1 is directed to the right in FIG. 5, and the end of the driven rotation axis F1 is directed to the left in FIG.
  • the central axis C1 of the drive side rotational shaft D1 and the central axis C2 of the driven side rotational shaft F1 do not coincide, and both have an interval in the vertical direction in FIG. Therefore, the drive side test strip D2 fixed to the tip end of the drive side rotation shaft D1 and the driven side test strip F2 fixed to the tip end of the driven side rotation shaft F1 are the drive side rotation shaft D1 and the driven side rotation.
  • the respective outer diameter surfaces of the axis F1 are arranged to be in contact with each other at the outer diameter surface contact portion DF in their non-rotated state.
  • the drive-side test strip D2 and the driven-side test strip F2 arranged to be in contact with each other are in contact with the fueling felt pad 3 laid under them.
  • an additive-free poly- ⁇ -olefin oil (corresponding to VG5) was used as a lubricating oil in the two-cylinder tester 2.
  • This lubricating oil was impregnated in the felt pad 3 for oil supply, and was supplied from there to the outer diameter surface of the driving side test piece D2 and the driven side test piece F2.
  • the number of revolutions around the central axis C1 of the drive side rotation axis D1 was 2000 rpm
  • the value of the load W (see FIG. 5) applied to the driven side test piece F2 was 230 kgf.
  • the load W is a load applied to the driven-side test piece F2 in the direction shown by the arrow W in FIG.
  • the test time was 100 minutes, and the test was ended when the total number of loads applied to the driven test piece F2 reached 200,000 times.
  • the above conditions are conditions under which minute peeling called peeling is likely to occur on the surface of the rolling portion of the driven-side test piece F2.
  • the shapes, dimensions, and the like of the drive-side test piece D2 and the driven-side test piece F2 used for each of the three types of tests will be described using Tables 2 and 3.
  • the three types of tests are a comparative example which is a nonstandard test of the present embodiment, a test example 1 which is a test based on the present embodiment, and a test example 1 of a test based on the present embodiment.
  • conditions such as dimensions of the driving side test piece D2 used in each of the three types of tests will be described using Table 2.
  • the drive-side test strip D2 has a cylindrical shape having a circular shape in plan view from the tip side of the drive-side rotation axis D1 to which the drive-side test strip D2 is set.
  • the diameter of the outer diameter is the same 40 mm in any of the three types of tests, that is, Comparative Example, Test Example 1 and Test Example 2, and the diameter of the inner diameter is 20 mm in any of the above three types.
  • the width corresponding to the dimension in the axial direction is 12 mm
  • the radial sub-curvature radius is 60 mm.
  • the material of the drive-side test piece D2 is JIS standard SUJ2 in all of the above three types.
  • the Rockwell hardness of the width surface (the outer diameter surface and corresponding to the surface of the rolling portion) of the driving side test piece D2 of the comparative example and the test example 1 is 62.2 HRC.
  • the following process was done to First, the steel material of SUJ 2 was held at 840 ° C. for 40 minutes, then quenched by being introduced into oil at 80 ° C. and cooled, and then heated to 180 ° C. and tempered for 3 hours. Further, as shown in Table 2, the Rockwell hardness of the width surface of the driving-side test piece D2 of Test Example 2 is 60.5 HRC, and the following processing was carried out to achieve this.
  • the steel material of SUJ 2 was held at 850 ° C. for 80 minutes, then quenched by being put into oil at 80 ° C. and cooled, and then heated to 220 ° C. and subjected to tempering treatment for 100 hours.
  • the value of the arithmetic mean roughness Ra in the axial direction of the circular outer diameter surface in plan view of the drive-side test piece D2 is 0.650 ⁇ m for all of the test pieces D2 of Comparative Example and Test Example 1 and Test Example 2.
  • the value of the root mean square inclination R ⁇ q in the axial direction of the circular outer diameter surface of the driving side test piece D2 was finished to be 0.270.
  • the outer diameter surface of the drive side test piece D2 corresponds to the surface of the rolling portion of the drive side test piece D2.
  • the coating treatment of iron trioxide was not performed after the quenching treatment and the tempering treatment of the outer diameter surface of the driving side test piece D2.
  • the drive-side test pieces D2 of Test Example 1 and Test Example 2 were subjected to the coating treatment of triiron trioxide after the quenching treatment and tempering treatment of the outer diameter surface thereof. Specifically, after the quenching process and the tempering process, polishing was performed so that the arithmetic mean roughness of the outer diameter surface of the driving-side test piece D2 had the same value as that of the comparative example. Thereafter, triiron tetraoxide film treatment was performed on the driving side test piece D2.
  • the driving-side test piece D2 was immersed for 30 minutes in an alkaline solution containing sodium hydroxide as a main component and heated to 140 ⁇ 5 ° C. There was almost no change in the arithmetic mean roughness or the like of the outer diameter surface of the driving-side test piece D2 before and after this film treatment.
  • the driven-side test strip F2 has a cylindrical shape having a circular shape in plan view from the tip side of the driven-side rotation shaft F1 to which the driven-side test piece F2 is set.
  • the diameter of the outer diameter of each of the above three types is 40 mm
  • the diameter of the inner diameter is 20 mm
  • the width corresponding to the dimension in the axial direction is 12 mm, but does not have an axial minor radius of curvature.
  • the material of the driven-side test piece F2 is JIS standard SUJ2 in any of the above three types.
  • the Rockwell hardness of the width surface of the driven-side test piece F2 of the comparative example and the test example 1 is 62.2 HRC, but the following processing was performed to do this.
  • the steel material of SUJ 2 was held at 840 ° C. for 40 minutes, then quenched by being introduced into oil at 80 ° C. and cooled, and then heated to 180 ° C. and tempered for 3 hours.
  • the Rockwell hardness of the width surface of the driven-side test piece F2 of Test Example 2 is 63.0 HRC, and the following processing was carried out to do so.
  • the steel material of SUJ 2 was held at 850 ° C. for 80 minutes, then quenched by being put into oil at 80 ° C. and cooled, and then heated to 180 ° C. and tempered for 4 hours.
  • the test piece of the comparative example is polished and tempered after tempering, and finished so that the arithmetic mean roughness Ra of its outer diameter surface is 0.020 ⁇ m and the root mean square slope R ⁇ q is 0.013. It was done.
  • the outer diameter surface of the driven-side test piece F2 is polished after quenching and tempering treatment, and the arithmetic average roughness Ra of the outer diameter surface is 0.200 ⁇ m, the root mean square The square root slope R ⁇ q was finished to be 0.100.
  • grinding and superfinishing are performed on the outer diameter surface of the driven-side test piece F2 after quenching and tempering, and the arithmetic average roughness Ra of the outer diameter surface is 0. It was finished so that 070 ⁇ m and root mean square slope R ⁇ q became 0.074.
  • the outer diameter surface of the driven test piece F2 corresponds to the surface of the rolling portion of the driven test piece F2.
  • Planar shape of the outer diameter surface which is a rolling portion of the driven-side test piece F2 corresponding to the second rolling component after performing the respective tests of the comparative example and the respective test examples using the above-mentioned respective test pieces 6 (A) and 6 (B) show magnified micrographs of FIG. Referring to FIGS. 6 (A) and 6 (B), many peelings occurred on the surface of the rolling portion of the driven side test piece F2 of the comparative example, but the driven side test of Test Example 1 and Test Example 2 Peeling did not occur on the surface of the rolling portion of piece F2.
  • FIG. 7 shows the result of measurement of a three-dimensional shape using a laser microscope. Referring to FIG. 7, it can be confirmed that the minute projections of the rolling portions in Test Example 1 and Test Example 2 are more rounded than in the comparative example.
  • the drive side test piece D2 having a larger value of the surface roughness of the rolling portion is treated with a triiron oxide coating, and the driven side has a smaller value of the surface roughness of the rolling portion than that.
  • a two-cylinder tester 2 shown in FIG. 5 is used as in the first embodiment.
  • Table 5 conditions of the shape and dimensions of the drive-side test piece D2 and the driven-side test piece F2 in the present embodiment, and the drive conditions of the equipment of the two-cylinder test machine 2 will be described.
  • the drive-side test piece D2 has the same dimensions in any of the test examples performed in the present embodiment, and corresponds to the dimension of 40 mm in outer diameter, 20 mm in inner diameter, and the axial direction. It has a cylindrical shape with a width of 12 mm and a width-direction minor radius of curvature of 60 mm. Further, the surface roughness in the axial direction of the circular outer diameter surface in plan view of the drive-side test piece D2 is the same in any of the test examples, and the value of the arithmetic mean roughness Ra is about 0.650 ⁇ m, the root mean square Polishing was performed so that the value of the inclination R ⁇ q was about 0.270.
  • the driven-side test piece F2 has the same dimensions in any of the test examples conducted in the present embodiment, and has an outer diameter of 40 mm, an inner diameter of 20 mm, and an axial dimension. Is 12 mm in width, but has a cylindrical shape having no widthwise minor radius of curvature.
  • the surface roughness in the axial direction of the circular outer diameter surface in plan view of the driven-side test piece F2 is the same in any of the test examples, and the value of the arithmetic mean roughness Ra is about 0.020 ⁇ m, the root mean square Polishing and superfinishing were performed such that the value of the inclination R ⁇ q was about 0.013.
  • the value of this surface roughness is the same as that of the comparative example of Table 3 and FIG. 6 (A), and it was set as the conditions which peeling (minute peeling) tends to generate on the surface of the rolling part of driven side test piece F2.
  • the driving conditions (lubricant, rotation speed, load, test time, load frequency) of the equipment of the two-cylinder test machine 2 are as shown in Table 5. Specifically, the test was completed when the test time was 5 minutes and the total number of loads applied to the driven test piece F2 reached 10,000 times. The other conditions are the same as in the first embodiment. Further, the fixing aspect and the rotation aspect of the drive-side test piece D2 and the driven-side test piece F2 to the two-cylinder testing machine 2 in the present embodiment are the same as in the first embodiment, and can be described using FIG. Detailed description is omitted here.
  • each of the nine types of tests is set to test examples 3 to 11 regardless of whether it is a test based on the present embodiment or a nonstandard test of the present embodiment. It shows by.
  • the steel material constituting the drive-side test piece D2 and the driven-side test piece F2 is JIS standard SUJ2.
  • the driving side test piece D2 and the driven side test piece F2 are hardened by being charged in oil at 80 ° C. and cooled after being held at 850 ° C. for 80 minutes.
  • the conditions for subsequent tempering differ depending on the test example and the test piece.
  • the drive side test pieces D2 of Test Examples 3 to 5 are tempered at 250 ° C. for 7.5 hours, and the drive side test pieces D2 of the test pieces 6 to 8 are tested at 230 ° C. for 7.5 hours
  • the driving side test pieces D2 of the pieces 9 to 11 were tempered at 200 ° C. for 3 hours.
  • the driven side test piece F2 of Test Examples 3, 6 and 9 is tempered at 250 ° C. for 7.5 hours, and the driven side test piece F2 of the test pieces 4, 7 and 10 is tested at 230 ° C. for 7.5 hours
  • the driven side test pieces F2 of the pieces 5, 8 and 11 were tempered at 200 ° C. for 3 hours.
  • the Rockwell hardness of the width surface (corresponding to the surface of the rolling portion) of the drive-side test piece D2 and the driven-side test piece F2 was measured by these tempering conditions.
  • the Rockwell hardness is roughly classified into three types so as to be either about 59.5 HRC, about 60.5 HRC or about 61.5 HRC (including an error of about ⁇ 0.2 HRC).
  • the combinations of the values of the Rockwell hardness (the above classification) of the width surfaces of the drive-side test piece D2 and the driven-side test piece F2 were different.
  • the peeling performance evaluation test was performed in each test example using nine types of test pieces with which the combination of the above hardness differs.
  • the cracked portion in the micrograph of the outer diameter surface which is the rolling portion of the driven-side test piece F2 corresponding to the second rolling component after each test is shown in FIG. %) are shown in Table 7.
  • the area ratio was calculated by converting the photograph of FIG. 8 into a monochrome image using commercially available image processing software in each test example, and performing a binarization process on the image to paint only the cracked portion.
  • the Rockwell hardness (unit: HRC) of the width surface of the drive-side test piece D2 as the first rolling part is greater than that of the driven-side test piece F2 as the second rolling part.
  • HRC Rockwell hardness
  • the Rockwell hardness of the width surface of the driven-side test piece F2 is 61.4 HRC (about 61.5 HRC).
  • the test pieces 5 and 8 each have a Rockwell hardness of 61.5 HRC on the width surface of the driven-side test piece F2.
  • the two-cylinder tester 2 of FIG. 5 was used.
  • the driving conditions of the equipment of the two-cylinder testing machine 2 are shown in Table 1 above, and the two-cylinder testing machine 2 is also driven in the same manner as in Example 1 in this embodiment.
  • the drive-side test strip D2 has a cylindrical shape having a circular shape when viewed in plan from the tip side of the drive-side rotation axis D1 to which it is set.
  • the diameter of the outer diameter is 40 mm which is the same in both of the two types of tests, that is, the comparative example and the test example, and the diameter of the inner diameter is 20 mm in each of the above two types.
  • the width of each of the above two types is 12 mm, which corresponds to the dimension in the axial direction, and the radial radius of curvature in the axial direction is 60 mm.
  • the materials of the test pieces are both JIS standard SUJ2 of the above two types, and all of them are tempered after being subjected to a general quenching treatment, and in the comparative example, the Rockwell hardness of the width surface thereof is It was processed to be 62.2 HRC, and in the test example, it was processed to have a Rockwell hardness of 60.5 HRC on its width surface.
  • the value of the arithmetic average roughness Ra in the axial direction of the outer surface in the plan view of the drive-side test piece D2 is 0.650 ⁇ m
  • the circular outer diameter of the drive-side test piece D2 Polishing was performed so that the value of the root mean square slope R ⁇ q in the axial direction of the surface was 0.270.
  • the driven-side test strip F2 has a cylindrical shape having a circular shape in a plan view from the tip side of the driven-side rotation shaft F1 to which the driven-side test piece F2 is set.
  • the diameter of the outer diameter of the above two types is 40 mm
  • the diameter of the inner diameter is 20 mm
  • the width corresponding to the dimension in the axial direction is 12 mm, but does not have an axial minor radius of curvature.
  • the materials of the test pieces are both JIS standard SUJ2 of the above two types, and both are subjected to tempering treatment after being subjected to quenching treatment, and in the comparative example, the Rockwell hardness of its width surface is 62.2 HRC. It was processed so that it might become and in the test example, it was processed so that the Rockwell hardness of the width side might be 63.0 HRC. With respect to the driven-side test piece F2, both of the above two types were subjected to polishing and superfinishing after tempering. Thereby, in the comparative example, the arithmetic mean roughness Ra of the outer diameter surface is finished to be 0.020 ⁇ m and the root mean square slope R ⁇ q to be 0.013. In the test example, the outer diameter surface was finished to have an arithmetic mean roughness Ra of 0.070 ⁇ m and a root mean square inclination R ⁇ q of 0.074.
  • both of the drive-side test piece D2 and the driven-side test piece F2 of the comparative example have a width surface Rockwell hardness of 62.2 HRC
  • the following steps were carried out for this purpose. First, after holding the steel material at 840 ° C. for 40 minutes, it was quenched by being cooled in oil at 80 ° C., and then tempered for 3 hours at 180 ° C.
  • the width surface Rockwell hardness of the driving-side test piece D2 of the test example is 60.5 HRC
  • the following steps are performed for this purpose. First, the steel material was held at 850 ° C. for 80 minutes, cooled in oil at 80 ° C. for quenching, and then tempered at 220 ° C. for 100 hours.
  • the width surface Rockwell hardness of the driven-side test piece F2 of the test example is 63.0 HRC
  • the following steps are performed for this purpose. First, the steel material was held at 850 ° C. for 80 minutes, cooled in oil at 80 ° C. for quenching, and then tempered at 180 ° C. for 4 hours.
  • FIG. 12 The planar shape of the outer diameter surface which is the rolling portion of the driven-side test piece F2 corresponding to the second rolling part after conducting the respective tests of the comparative example and the test example using the above-described respective test pieces A microscope enlarged photograph is shown in FIG. Referring to FIG. 12, many peelings were generated on the surface of the rolling portion of driven side test piece F2 of the comparative example, but peeling was performed on the surface of the rolling portion of driven side test piece F2 of the test example. Did not occur.
  • the surface roughness of the rolling portion of the driving side test piece D2 is made larger than the surface roughness of the rolling portion of the driven side test piece F2, and the hardness of the rolling portion surface of the driving side test piece D2 is the driven side
  • the hardness of the surface of the rolling portion of the test piece F2 is made softer, and the arithmetic mean roughness of the surface of the rolling portion before the test of the driven side test piece D2 is about 0.070 ⁇ m, and the root mean square inclination is about 0.074 Is preferable.
  • Reference Signs List 1 deep groove ball bearing, 2 two cylindrical testing machine, 3 felt pad for oil supply, 1,120,130 outer ring, 11A, 120A, 130A outer ring raceway surface, 11B, 12B film, 12,121,131 inner ring, 12A, 121A, 131A Inner ring raceway, 13 balls, 13A ball rolling surface, 14, 123, 133 cage, 102 conical roller bearings, 103 cylindrical roller bearings, 122, 132 rollers, 122A, 132A roller rolling surfaces, D1 drive side rotation shaft, D2 Drive side test piece, DF OD surface contact part, F1 driven side rotation shaft, F2 driven side test piece.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention concerne un palier à éléments de roulement, lequel palier est apte à limiter une détérioration de surface et à atteindre facilement une longue durée de vie, même quand il est utilisé dans des conditions dans lesquelles la formation d'un film d'huile sur les surfaces de roulement est médiocre; un dispositif de roulement; et un procédé de fabrication d'un dispositif de roulement. Le dispositif de roulement (1) comporte des premières pièces de roulement (11, 12) qui sont réalisés en SUJ2 et des secondes pièces de roulement (13) qui viennent en contact avec les premières pièces de roulement (11, 12) et qui sont réalisés en SUJ2. La rugosité moyenne arithmétique (Ra) des surfaces (11A, 12A) des zones de roulement des premières pièces de roulement (11, 12) est supérieure à la rugosité moyenne arithmétique des surfaces (13A) des zones de roulement des secondes pièces de roulement (13). La rugosité moyenne arithmétique des surfaces (13A) des zones de roulement des secondes pièces de roulement (13) est de 0,07 µm à 0,20 µm.
PCT/JP2017/000128 2016-01-21 2017-01-05 Palier à éléments de roulement, dispositif de roulement, et procédé de fabrication de dispositif de roulement WO2017126323A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US16/071,851 US11028880B2 (en) 2016-01-21 2017-01-05 Rolling bearing, rolling device, and method of manufacturing rolling device
EP17741203.8A EP3406923A4 (fr) 2016-01-21 2017-01-05 Palier à éléments de roulement, dispositif de roulement, et procédé de fabrication de dispositif de roulement
CN201780007576.2A CN108603530A (zh) 2016-01-21 2017-01-05 滚动轴承、滚动装置以及滚动装置的制造方法

Applications Claiming Priority (6)

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JP2016009964 2016-01-21
JP2016-009964 2016-01-21
JP2016034480A JP2017150597A (ja) 2016-02-25 2016-02-25 転がり軸受、転動装置および転動装置の製造方法
JP2016-034480 2016-02-25
JP2016-170758 2016-09-01
JP2016170758A JP6964400B2 (ja) 2016-01-21 2016-09-01 転がり軸受、転動装置および転動装置の製造方法

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Publication number Priority date Publication date Assignee Title
US11078961B2 (en) * 2018-04-02 2021-08-03 Nsk Ltd. Intermediary race member of rolling bearing, race, rolling bearing and production method therefor
US11542985B2 (en) 2018-09-26 2023-01-03 Ntn Corporation Rolling bearing and wind power generation rotor shaft support device

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JPH04265480A (ja) 1991-02-21 1992-09-21 Ntn Corp エアコンディショナー用コンプレッサの軸受
JP2002070873A (ja) * 2000-08-28 2002-03-08 Nsk Ltd 転がり軸受
JP2002206542A (ja) * 2001-01-10 2002-07-26 Ntn Corp 電食防止型軸受およびその外輪製造方法
JP2005061495A (ja) * 2003-08-11 2005-03-10 Nsk Ltd 円筒ころ軸受
JP2005226683A (ja) * 2004-02-10 2005-08-25 Nsk Ltd スラスト針状ころ軸受
JP2006161887A (ja) 2004-12-03 2006-06-22 Nsk Ltd 針状ころ軸受
JP2006322017A (ja) * 2005-05-17 2006-11-30 Nsk Ltd 転がり軸受
JP2006348342A (ja) * 2005-06-15 2006-12-28 Nsk Ltd 転がり支持装置
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JPH04265480A (ja) 1991-02-21 1992-09-21 Ntn Corp エアコンディショナー用コンプレッサの軸受
JP2002070873A (ja) * 2000-08-28 2002-03-08 Nsk Ltd 転がり軸受
JP2002206542A (ja) * 2001-01-10 2002-07-26 Ntn Corp 電食防止型軸受およびその外輪製造方法
JP2005061495A (ja) * 2003-08-11 2005-03-10 Nsk Ltd 円筒ころ軸受
JP2005226683A (ja) * 2004-02-10 2005-08-25 Nsk Ltd スラスト針状ころ軸受
JP2006161887A (ja) 2004-12-03 2006-06-22 Nsk Ltd 針状ころ軸受
JP2006322017A (ja) * 2005-05-17 2006-11-30 Nsk Ltd 転がり軸受
JP2006348342A (ja) * 2005-06-15 2006-12-28 Nsk Ltd 転がり支持装置
JP2012219995A (ja) * 2011-04-14 2012-11-12 Ntn Corp 転がり軸受およびその製造方法

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11078961B2 (en) * 2018-04-02 2021-08-03 Nsk Ltd. Intermediary race member of rolling bearing, race, rolling bearing and production method therefor
US11542985B2 (en) 2018-09-26 2023-01-03 Ntn Corporation Rolling bearing and wind power generation rotor shaft support device

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