WO2011040267A1 - Roulement à billes - Google Patents

Roulement à billes Download PDF

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Publication number
WO2011040267A1
WO2011040267A1 PCT/JP2010/066179 JP2010066179W WO2011040267A1 WO 2011040267 A1 WO2011040267 A1 WO 2011040267A1 JP 2010066179 W JP2010066179 W JP 2010066179W WO 2011040267 A1 WO2011040267 A1 WO 2011040267A1
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WO
WIPO (PCT)
Prior art keywords
bearing
rolling
rolling bearing
pulley
hydrogen embrittlement
Prior art date
Application number
PCT/JP2010/066179
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English (en)
Japanese (ja)
Inventor
幸生 松原
則暁 坂中
淳 諸岡
森　正継
哲人 石井
藤原　宏樹
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.)
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Publication date
Priority claimed from JP2009297773A external-priority patent/JP5538877B2/ja
Priority claimed from JP2009297772A external-priority patent/JP5529526B2/ja
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2011040267A1 publication Critical patent/WO2011040267A1/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
    • F16C33/58—Raceways; Race rings
    • F16C33/62—Selection of substances
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
    • F16C19/26—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with a single row of rollers
    • 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
    • F16C2202/00—Solid materials defined by their properties
    • F16C2202/02—Mechanical properties
    • F16C2202/04—Hardness
    • 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
    • F16C2202/00—Solid materials defined by their properties
    • F16C2202/30—Electric properties; Magnetic properties
    • F16C2202/32—Conductivity
    • 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
    • F16C2206/00—Materials with ceramics, cermets, hard carbon or similar non-metallic hard materials as main constituents
    • F16C2206/40—Ceramics, e.g. carbides, nitrides, oxides, borides of a metal

Definitions

  • the present invention relates to a rolling bearing, and more particularly to a rolling bearing in which at least one bearing member of a race member and a rolling element is made of JIS standard SUJ2.
  • Patent Document 1 discloses a passive film having a predetermined Cr (chromium) content in a steel material. It is disclosed that the entry of hydrogen into a steel material is suppressed by forming a chromium oxide film with a predetermined thickness.
  • carbide is coarsened by adding a large amount of Cr in order to make the Cr content rate a predetermined value, which may become a stress concentration source and cause early peeling.
  • the passive film has an effect of slowing the diffusion of hydrogen, but also has an effect of promoting the adsorption of the generated hydrogen on the steel surface. Therefore, in the case of a rolling bearing that is used intermittently, hydrogen is dissipated at the time of stoppage. Therefore, it is considered effective to suppress early separation by delaying the penetration of hydrogen into the steel by the passive film.
  • the special steel material having a predetermined Cr content has a problem of high cost. Moreover, there is a problem that it is difficult to procure a special steel material having a predetermined Cr content.
  • ⁇ Heat generation from the bearing causes thermal expansion of the shaft, which is one of the causes of deterioration of machining accuracy.
  • a rolling bearing for a main spindle of a machine tool used at a high speed in a machine tool such as a machining center it is important to reduce the torque in order to avoid heat generation during the high speed rotation.
  • the rolling bearings for machine tool main spindles reduce the amount of lubricating oil as much as possible in order to reduce the friction torque of the bearings that causes heat generation.
  • the oil film thickness is reduced as compared with the case where sufficient lubricating oil is supplied, and the shear stress of the lubricating oil due to slip increases, so that hydrogen is likely to be generated.
  • angular ball bearings are frequently used as rolling bearings for machine tool spindles.
  • slip always occurs between the rolling elements (balls) and the race members (race rings).
  • coolant enters the raceway member and the rolling element.
  • water-soluble coolant the entry of the coolant is nothing but water mixing. Therefore, in a rolling bearing for a machine tool main shaft, early peeling is likely to occur due to hydrogen penetrating into steel.
  • the present invention has been made in view of the above problems, and an object thereof is to provide a rolling bearing capable of suppressing early separation due to hydrogen embrittlement.
  • the present inventor has reduced the vacancy density in an unfatigue state and made plastic deformation difficult by optimizing the tempering temperature of at least one bearing member of the raceway member and the rolling element. It has been found that the hydrogen embrittlement resistance of a rolling bearing is improved by making it difficult to generate atomic vacancies.
  • the present inventor has selected high-carbon chromium bearing steel SUJ2 (JIS standard) most frequently used for rolling bearings as the bearing member and at least one of the rolling elements in view of the cost and availability of the material.
  • the present inventor has optimized the tempering temperature to improve hydrogen embrittlement resistance after performing standard soaking.
  • the basis for optimizing the tempering temperature is based on the theory of hydrogen-assisted strain-induced vacancies, which is a powerful hydrogen embrittlement mechanism.
  • the number of vacancies increases due to plastic deformation, but this theory is based on the fact that it has been found by systematic experiments that when hydrogen is involved, it increases the vacancy density.
  • one rolling bearing according to the present invention includes a race member and a plurality of rolling elements that are in contact with the race member and are arranged to roll on an annular raceway.
  • the at least one bearing member is made of JIS standard SUJ2, and the electrical resistivity of the bearing member in the room temperature atmosphere is 28 ⁇ cm or less.
  • the electrical resistivity also decreases. Therefore, when the relationship between the tempering temperature and the electrical resistivity was investigated in detail, if the bearing member made of JIS standard SUJ2 was tempered at 230 ° C. or higher, the electrical resistivity of the bearing member in the ambient temperature was 28 ⁇ cm. It became clear that it became almost the same value. On the other hand, it was found that when the tempering temperature was less than 230 ° C., the electrical resistivity of the bearing member was larger than 28 ⁇ cm and the fluctuation was large. Therefore, by setting the tempering temperature to 230 ° C.
  • a SUJ2 standard rolling bearing steel ball having a diameter of 19.05 mm is pressed against the bearing member with a load of 1.97 kN, held for 10 seconds, and then unloaded, thereby forming the bearing member.
  • the depth of the indentation is 0.2 ⁇ m or less.
  • the atomic vacancy density increases due to plastic deformation.
  • the indentation depth indicates the difficulty of plastic deformation. In other words, if the indentation depth is small, it can be said that plastic deformation is difficult. If the indentation depth is 0.2 ⁇ m or less as a guide, it can be said that plastic deformation is difficult. Therefore, when the relationship between the tempering temperature and the indentation depth was investigated in detail, if a tempering treatment was performed at 230 ° C. or higher and 280 ° C. or lower, a SUJ2 standard rolling bearing steel ball having a diameter of 19.05 mm was loaded on the bearing member.
  • the vacancy density in the unfatigue state can be reduced by setting the tempering temperature to 230 ° C. or higher, by setting the tempering temperature to 230 ° C. or higher and 280 ° C. or lower, It is possible to reduce the atomic vacancy density and make it difficult for plastic deformation to generate atomic vacancies.
  • the Rockwell C scale hardness of the entire bearing member is preferably HRC57.0 or more and HRC59.3 or less.
  • the Rockwell C scale hardness of the entire bearing member in the tempering temperature range of 230 ° C. to 280 ° C. is HRC 57.0 to HRC 59.3.
  • the yield stress of the bearing member obtained from the relationship between the indentation depth and the indentation load obtained by indenting the triangular pyramid diamond indenter with the opposite edge angles of 115 ° and 100 ° into the bearing member is 1977 MPa or more
  • the work hardening index of the bearing member is 0.23 to 0.32
  • the plastic constant of the bearing member is 5828 MPa to 8588 MPa.
  • the yield stress of the bearing member determined from the relationship between the indentation depth and the indentation load obtained by indenting the triangular pyramid diamond indenter with a ridge angle of 115 ° and 100 ° into the bearing member in the tempering temperature range of 230 ° C. to 280 ° C. is 1977 MPa.
  • the work hardening index of the bearing member is 0.23 to 0.32
  • the plastic constant of the bearing member is 5828 MPa to 8588 MPa.
  • At least one bearing member of the raceway member and the rolling element may be made of JIS standard SUJ3.
  • the present inventor has reduced the vacancy density in an unfatigue state and made plastic deformation difficult by optimizing the tempering temperature of at least one bearing member of the raceway member and the rolling element. It has been found that the hydrogen embrittlement resistance of a rolling bearing is improved by making it difficult to generate atomic vacancies.
  • the present inventor has selected high-carbon chromium bearing steel SUJ3 (JIS standard), which is often used for rolling bearings, as the at least one bearing member of the raceway member and the rolling element in view of the cost of the material.
  • the present inventor has optimized the tempering temperature to improve hydrogen embrittlement resistance after performing standard soaking.
  • the basis for optimizing the tempering temperature is based on the theory of hydrogen-assisted strain-induced vacancies, which is a powerful hydrogen embrittlement mechanism.
  • the number of vacancies increases due to plastic deformation, but this theory is based on the fact that it has been found by systematic experiments that when hydrogen is involved, it increases the vacancy density.
  • Another rolling bearing according to the present invention includes a race member, and a plurality of rolling elements that are in contact with the race member and are arranged to freely roll on an annular raceway.
  • At least one bearing member is made of JIS standard SUJ3, and the electrical resistivity of the bearing member in the room temperature atmosphere is 36 ⁇ cm or less.
  • the electrical resistivity also decreases. Therefore, when the relationship between the tempering temperature and the electrical resistivity was investigated in detail, if the bearing member made of JIS standard SUJ3 was tempered at 260 ° C. or higher, the electrical resistivity of the bearing member in the normal temperature atmosphere was 36 ⁇ cm. It became clear that it became almost the same value. On the other hand, it was found that when the tempering temperature was less than 260 ° C., the electrical resistivity of the bearing member was larger than 36 ⁇ cm and the fluctuation was large. Therefore, by setting the tempering temperature to 260 ° C.
  • a SUJ2 standard rolling bearing steel ball having a diameter of 19.05 mm is pressed against the bearing member with a load of 2.30 kN, held for 10 seconds, and then unloaded, and then formed into the bearing member.
  • the depth of the indentation is 0.2 ⁇ m or less.
  • the atomic vacancy density increases due to plastic deformation.
  • the indentation depth indicates the difficulty of plastic deformation. In other words, if the indentation depth is small, it can be said that plastic deformation is difficult. If the indentation depth is 0.2 ⁇ m or less as a guide, it can be said that plastic deformation is difficult. Therefore, when the relationship between the tempering temperature and the indentation depth was investigated in detail, if a tempering treatment was performed at 270 ° C. or higher and 320 ° C. or lower, a SUJ2 standard rolling bearing steel ball having a diameter of 19.05 mm was loaded on the bearing member.
  • the depth of the indentation formed on the bearing member was 0.2 ⁇ m or less by pressing at 2.30 kN and holding for 10 seconds before unloading. Therefore, by setting the tempering temperature to 270 ° C. or more and 320 ° C. or less, it is difficult to plastically deform and it is possible to make it difficult to generate atomic vacancies. Thereby, since hydrogen embrittlement resistance can be improved, early peeling due to hydrogen embrittlement can be suppressed.
  • the vacancy density in the unfatigue state can be reduced by setting the tempering temperature to 260 ° C. or higher, by setting the tempering temperature to 270 ° C. or higher and 320 ° C. or lower, It is possible to reduce the atomic vacancy density and make it difficult for plastic deformation to generate atomic vacancies.
  • the Rockwell C scale hardness of the entire bearing member is preferably HRC56.8 or more and HRC58.7 or less.
  • the Rockwell C scale hardness of the entire bearing member in the tempering temperature range of 270 ° C. to 320 ° C. is HRC 56.8 to HRC 58.7.
  • the bearing member preferably has a yield stress of 2196 MPa or more obtained from the relationship between the indentation depth and the indentation load obtained by indenting the triangular pyramid diamond indenter with the opposite ridge angles of 115 ° and 100 ° into the bearing member.
  • the work hardening index is 0.22 or more and 0.33 or less
  • the plastic constant of the bearing member is 6469 MPa or more and 9825 MPa or less.
  • the yield stress of the bearing member determined from the relationship between the indentation depth obtained by indenting the triangular pyramid diamond indenter with a ridge angle of 115 ° and 100 ° into the bearing member in the range of 270 ° C. to 320 ° C. and the indentation load is 2196 MPa.
  • the work hardening index of the bearing member is 0.22 to 0.33
  • the plastic constant of the bearing member is 6469 MPa to 9825 MPa.
  • the rolling element is made of JIS standard SUJ2, and the electric resistivity of the rolling element in the room temperature atmosphere is 28 ⁇ cm or less.
  • the present inventor has selected high carbon chromium bearing steel SUJ2 (JIS standard) as the rolling element in view of the cost and procurement of the material.
  • JIS standard high carbon chromium bearing steel
  • the rolling element is preferably formed by pressing a steel ball for SUJ2 standard rolling bearing having a diameter of 19.05 mm to the rolling element with a load of 1.97 kN, holding it for 10 seconds, and then unloading it.
  • the depth of the indentation is 0.2 ⁇ m or less.
  • the indentation depth is 0.2 ⁇ m or less as a guide, it can be said that plastic deformation is difficult. Therefore, when the relationship between the tempering temperature and the indentation depth was investigated in detail, if a tempering treatment was performed at 230 ° C. or higher and 280 ° C. or lower, SUJ2 standard rolling bearing steel balls with a diameter of 19.05 mm were loaded on the rolling elements. It was found that by pressing at 1.97 kN and holding for 10 seconds before unloading, the depth of the indentation formed on the rolling element was 0.2 ⁇ m or less. Therefore, by setting the tempering temperature to 230 ° C. or higher and 280 ° C. or lower, it is difficult to plastically deform and it is difficult to generate atomic vacancies. Thereby, since hydrogen embrittlement resistance can be improved, early peeling due to hydrogen embrittlement can be suppressed.
  • the vacancy density in the unfatigue state can be reduced by setting the tempering temperature to 230 ° C. or higher, by setting the tempering temperature to 230 ° C. or higher and 280 ° C. or lower, It is possible to reduce the atomic vacancy density and make it difficult for plastic deformation to generate atomic vacancies.
  • the Rockwell C scale hardness of the entire rolling element is preferably HRC57.0 or more and HRC59.3 or less.
  • the Rockwell C scale hardness of the entire rolling element in the range of tempering temperature 230 ° C. or higher and 280 ° C. or lower is HRC 57.0 or higher and HRC 59.3 or lower.
  • the yield stress of the rolling element obtained from the relationship between the indentation depth obtained by indentation of the triangular pyramid diamond indenter of 115 ° to 100 ° and the indentation load into the rolling element is 1977 MPa or more
  • the work hardening index of the rolling element is 0.23 or more and 0.32 or less
  • the plastic constant of the rolling element is 5828 MPa or more and 8588 MPa or less.
  • the yield stress of the rolling element obtained from the relationship between the indentation depth obtained by indenting the triangular pyramid diamond indenter with a ridge angle of 115 ° and 100 ° into the rolling element in the range of tempering temperature 230 ° C. or more and 280 ° C. or less is 1977 MPa.
  • the work hardening index of the rolling element is 0.23 to 0.32
  • the plastic constant of the rolling element is 5828 MPa to 8588 MPa.
  • the rolling element is preferably made of a material containing ceramics. According to the rolling bearing of the present invention, since the rolling element is made of a material containing ceramics that does not exhibit hydrogen embrittlement, the hydrogen embrittlement resistance can be improved, so that early separation due to hydrogen embrittlement can be suppressed.
  • the above-mentioned one and other rolling bearings preferably further include a cage for holding the rolling elements, and the cage is made of a material containing metal.
  • the metal cage under the condition where energization occurs, the metal cage is less likely to cause early peeling due to hydrogen embrittlement than the resin cage, and therefore, early peeling due to hydrogen embrittlement can be suppressed.
  • the one and other rolling bearings described above further include a main shaft of the motor and a housing arranged to face the outer peripheral surface of the main shaft, and the main shaft is rotatably supported with respect to the housing.
  • the rolling bearing of the present invention since early peeling due to hydrogen embrittlement can be suppressed, a long service life can be obtained even under severe use conditions such as conditions where water is mixed in the bearing, conditions involving slippage, and conditions where energization occurs. It is possible to provide a rolling bearing for a simple motor.
  • the above-mentioned one and other rolling bearings preferably further include a main shaft of the machine tool and a housing disposed so as to face the outer peripheral surface of the main shaft, and the main shaft is rotatably supported with respect to the housing.
  • the rolling bearing of the present invention since early peeling due to hydrogen embrittlement can be suppressed, a long service life can be obtained even under severe use conditions such as conditions where water is mixed in the bearing, conditions involving slippage, and conditions where energization occurs.
  • a rolling bearing for a main spindle of a machine tool can be provided. Further, it is possible to provide a rolling bearing for a machine tool spindle that has a long life even under use conditions in which the oil film thickness of the lubricating oil is reduced in order to reduce the friction torque of the bearing that causes heat generation during high-speed rotation.
  • the one and other rolling bearings further include a rotation side member of the wheel and a fixed side member disposed so as to oppose the outer peripheral surface of the rotation side member, and the rotation side member is disposed on the fixed side member. And support it rotatably.
  • the rolling bearing of the present invention since early peeling due to hydrogen embrittlement can be suppressed, a long service life can be obtained even under severe use conditions such as conditions where water is mixed in the bearing, conditions involving slippage, and conditions where energization occurs.
  • a rolling bearing for a wheel can be provided. Further, since the early peeling due to hydrogen embrittlement can be suppressed even under conditions where the bearing vibrates, a long-life wheel rolling bearing can be provided.
  • the above-mentioned one and other rolling bearings preferably further include a main shaft of the alternator and a housing disposed so as to face the outer peripheral surface of the main shaft, and the main shaft is rotatably supported with respect to the housing.
  • a rolling bearing for an alternator can be provided. Providing rolling bearings for alternators that have a long life by suppressing early delamination due to hydrogen embrittlement, especially under operating conditions where sliding due to hydrogen embrittlement is likely to occur due to the effect of slippage between contact elements under rapid acceleration / deceleration conditions can do.
  • the one and other rolling bearings described above further include a main shaft and a pulley main body disposed so as to face the outer peripheral surface of the main shaft, and the main shaft is rotatably supported with respect to the pulley main body.
  • the rolling bearing of the present invention since early peeling due to hydrogen embrittlement can be suppressed, a long service life can be obtained even under severe use conditions such as conditions where water is mixed in the bearing, conditions involving slippage, and conditions where energization occurs.
  • a pulley rolling bearing can be provided. Also, since it is possible to suppress early peeling due to hydrogen embrittlement even under conditions in which slippage is induced more than before due to increased load load and increased load fluctuation associated with serpentine conversion, a long-life pulley rolling bearing is provided. Can do.
  • the one and other rolling bearings further include a car air conditioner electromagnetic clutch pulley, and a pulley bearing support member disposed so as to face the inner peripheral surface of the car air conditioner electromagnetic clutch pulley, The pulley is rotatably supported with respect to the pulley bearing support member.
  • rolling bearing of the present invention since early peeling due to hydrogen embrittlement can be suppressed, a long service life can be obtained even under severe use conditions such as conditions where water is mixed in the bearing, conditions involving slippage, and conditions where energization occurs.
  • a rolling bearing for a car air conditioner electromagnetic clutch pulley can be provided.
  • rolling bearings for car air conditioner electromagnetic clutch pulleys that have a long service life can be prevented because early peeling due to hydrogen embrittlement can be suppressed even under conditions in which slippage is induced more than before due to increased load load and increased load fluctuation associated with serpentine conversion. Can be provided.
  • the one and other rolling bearings further include a pulley shaft of a continuously variable transmission and a housing disposed so as to face the outer peripheral surface of the pulley shaft, and the pulley shaft is rotatable with respect to the housing.
  • a pulley shaft of a continuously variable transmission and a housing disposed so as to face the outer peripheral surface of the pulley shaft, and the pulley shaft is rotatable with respect to the housing.
  • the rolling bearing of the present invention since early peeling due to hydrogen embrittlement can be suppressed, a long service life can be obtained even under severe use conditions such as conditions where water is mixed in the bearing, conditions involving slippage, and conditions where energization occurs. It is possible to provide a rolling bearing for a continuously variable transmission.
  • the groove curvature of the inner and outer rings of the bearing is set to be small in order to suppress the axial clearance of the bearing, it is possible to suppress early peeling due to hydrogen embrittlement even under conditions where differential sliding during bearing operation is large.
  • a rolling bearing for a continuously variable transmission can be provided.
  • the rolling bearing is preferably a shell needle roller bearing.
  • Shell-shaped needle roller bearings have a fast acceleration at the time of start-up (antilock) when they are used to support air compressors in automobiles that are rapidly accelerated or decelerated by switching electromagnetic clutches, especially under conditions involving sliding such as sudden acceleration / deceleration.
  • start-up antilock
  • the rolling element is likely to slip, and early peeling due to hydrogen embrittlement may occur.
  • the rolling bearing of the present invention it is possible to provide a long-life shell needle roller bearing because it is possible to suppress early separation due to hydrogen embrittlement even under such conditions.
  • the rolling bearing is preferably a solid needle roller bearing.
  • Solid needle roller bearings support transmissions that accelerate quickly during start-up, especially when used to support air compressors in automobiles that accelerate and decelerate suddenly by switching electromagnetic clutches under conditions involving sudden acceleration and deceleration. In the case of being used for a large-sized connecting rod of a general-purpose engine, slippage between contact elements is likely to occur, and early peeling due to hydrogen embrittlement may occur.
  • the rolling bearing of the present invention it is possible to provide a long-life solid needle roller bearing because early peeling due to hydrogen embrittlement can be suppressed even under such conditions.
  • the rolling bearing is a thrust needle roller bearing.
  • the thrust needle roller bearing is constantly slipped from the rolling wheel during operation due to the difference in peripheral speed between the inside and outside of the rolling element, and may cause early separation due to hydrogen embrittlement.
  • Thrust needle roller bearings may experience early peeling due to hydrogen embrittlement even under conditions involving slippage such as rapid acceleration and deceleration. According to the rolling bearing of the present invention, since it is possible to suppress early separation due to hydrogen embrittlement even under such conditions, a long-life thrust needle roller bearing can be provided.
  • the rolling bearing preferably includes a cage.
  • Needle roller bearings with cages are planetary pinion support bearings of CVT (Continuously Variable Transmission), especially when used as idler bearings for automobile transmissions that accelerate quickly during acceleration, such as sudden acceleration and deceleration.
  • CVT Continuous Variable Transmission
  • the rolling element When used as a bearing for a large end of a connecting rod of a two-wheeled engine or a general-purpose engine, the rolling element easily slips and may cause early peeling due to hydrogen embrittlement.
  • the rolling bearing of the present invention since it is possible to suppress early separation due to hydrogen embrittlement even under such conditions, a long-life needle roller bearing with a cage can be provided.
  • FIG. 1 is a schematic cross-sectional view showing a configuration around a spindle of a machine tool provided with a rolling bearing for a machine tool spindle in an embodiment of the present invention.
  • FIG. 1 is a schematic partial cross-sectional view of a lubricating device provided with a rolling bearing that lubricates with a small amount of lubricating oil as a rolling bearing for a machine tool spindle in an embodiment of the present invention.
  • FIG. 1 is a schematic partial cross-sectional view of a lubricating device provided with a rolling bearing that lubricates with a small amount of lubricating oil as a rolling bearing for a machine tool spindle in an embodiment of the present invention.
  • FIG. 3 is a schematic partial cross-sectional view of a lubrication apparatus including a rolling bearing that is lubricated with another small amount of lubricating oil as a rolling bearing for a machine tool main spindle according to an embodiment of the present invention. It is a figure which shows the relationship between the tempering temperature and electrical resistivity in the electrical resistivity measurement test of Example 1 of this invention. It is a figure which shows the relationship between the tempering temperature and the indentation depth in the indentation test of Example 1 of this invention. It is a figure which shows the relationship between the tempering temperature and HRC hardness in the HRC hardness test of Example 1 of this invention. It is a schematic diagram of a true stress-true strain diagram of a metal material.
  • a motor 90 has a disk-like shape, and includes a rotor 91 provided with a coil, and a frame (housing) 93 disposed so as to surround the rotor 91. And a main shaft 92 that is connected to a portion including the center (rotating shaft) of the rotor 91 and penetrates the frame 93 so as to be rotatable about the shaft integrally with the rotor 91.
  • a grease-enclosed deep groove ball bearing 1 as a rolling bearing for a motor is fitted between the outer peripheral surface 92A of the main shaft 92 and a portion of the frame 93 that faces the outer peripheral surface 92A of the main shaft 92.
  • the grease-filled deep groove ball bearing 1 is a rolling bearing for a motor that rotatably supports a main shaft 92 of a motor 90 with respect to a frame 93 disposed so as to face the outer peripheral surface 92A of the main shaft 92.
  • the motor 90 includes a stator 96 including a magnet fixedly arranged with respect to the frame 93 so as to face the outer peripheral surface of the rotor 91 inside the frame 93, and the main shaft as viewed from the rotor 91.
  • 92 is connected to a portion opposite to the side protruding from the frame 93 and is commutator 94 configured to be rotatable integrally with the rotor 91 and fixed to the frame 93 so as to be in contact with the commutator 94.
  • a brush 95 arranged in the same manner.
  • a grease-filled deep groove ball bearing 1 includes an outer ring 11 as a first race member, an inner ring 12 as a second race member, balls 13 as a plurality of rolling elements, and a cage. 14 and a seal member 15.
  • An outer ring rolling surface 11 ⁇ / b> A as an annular first rolling surface is formed on the inner peripheral surface of the outer ring 11.
  • an inner ring rolling surface 12A as an annular second rolling surface facing the outer ring rolling surface 11A is formed.
  • a plurality of balls 13 is formed with a ball rolling surface 13A (the surface of the ball 13) as a rolling element rolling surface.
  • the balls 13 are in contact with each of the outer ring rolling surface 11A and the inner ring rolling surface 12A at the ball rolling surface 13A, and are arranged at a predetermined pitch in the circumferential direction by the annular retainer 14, It is rotatably held on an annular track.
  • the pair of seal members 15 are arranged so as to close the outer ring 11 and the inner ring 12 so as to close the space between the outer ring 11 and the inner ring 12, more specifically, the raceway space that is the space between the outer ring rolling surface 11A and the inner ring rolling surface 12A.
  • the outer ring 11 and the inner ring 12 are arranged at both ends in the width direction.
  • At least one bearing member out of the outer ring 11 and the inner ring 12 as the race member and the ball 13 as the rolling element is made of JIS standard SUJ2, and the electrical resistivity of the bearing member in the room temperature atmosphere is 28 ⁇ cm or less.
  • a SUJ2 standard rolling bearing steel ball having a diameter of 19.05 mm is pressed with a load of 1.97 kN to at least one bearing member among the outer ring 11 and the inner ring 12 as the race members and the balls 13 as the rolling elements and held for 10 seconds. After the unloading, the depth of the indentation formed in the bearing member is 0.2 ⁇ m or less.
  • the Rockwell C scale hardness of the entire at least one bearing member among the outer ring 11 and the inner ring 12 as the race members and the balls 13 as the rolling elements is HRC 57.0 or more and HRC 59.3 or less.
  • the yield stress of the bearing member is 1977 MPa or more
  • the work hardening index of the bearing member is 0.23 or more and 0.32 or less
  • the plastic constant of the bearing member is 5828 MPa or more and 8588 MPa or less.
  • the balls 13 as rolling elements are made of a material containing ceramics.
  • the ceramic silicon nitride, sialon, or the like can be applied.
  • the ceramic is a sintered body mainly composed of ⁇ sialon, which is one of sialon, it is sintered under a pressure of low pressure (for example, 1 MPa or less), so pressure sintering is performed under a pressure of 10 MPa or more. It can be manufactured at a lower cost than a sintered body mainly composed of silicon nitride.
  • a sintered body containing ⁇ sialon as a main component is a sintered body in which ⁇ sialon is a main component and the balance is made of impurities.
  • ⁇ sialon is represented by a composition formula of Si 6-Z AL Z N 8-Z and is configured so that Z satisfies a range of 0.1 ⁇ Z ⁇ 3.5.
  • Impurities include those derived from raw materials or mixed in the manufacturing process, and also include inevitable impurities.
  • the sintering aid at least one of magnesium (Mg), aluminum (Al), silicon (Si), titanium (Ti), rare earth element oxide, nitride, and oxynitride may be employed. it can.
  • the sintering aid is preferably 20% by mass or less in the sintered body.
  • the cage 14 for holding the balls 13 as rolling elements is preferably made of a material containing metal.
  • a current supplied to a brush 95 from a power source (not shown) via a wire flows through a coil of the rotor 91 via a commutator 94.
  • the rotor 91 rotates about the axis of the main shaft 92 with respect to the frame 93 by an electromagnetic force generated by a current flowing through the coil of the rotor 91 and a magnetic field formed by the stator 96 including a magnet.
  • the rotor 91 rotates by a predetermined angle, the direction of the current flowing through the coil of the rotor 91 is reversed by the action of the commutator 94 and the brush 95, and the rotor 91 further rotates. By repeating this, the rotor 91 continuously rotates with respect to the housing, and the rotation is taken out by the main shaft 92.
  • a steel material preparation step of preparing a steel material composed of JIS standard SUJ2 is performed. Specifically, for example, steel bars or steel wires composed of JIS standard SUJ2 are prepared.
  • a forming step for producing a steel member formed into the general shape of the bearing member of the rolling bearing for motor is performed. Specifically, for example, forging, turning, and the like are performed on the above-described steel bars and steel wires, and the outer ring 11, the inner ring 12, the balls 13, and the like shown in FIGS. A steel member is produced.
  • the said process (S100) and (S200) comprise the steel member preparation process in which the steel member shape
  • the steel member is cooled from a temperature of A1 point or higher to a temperature of MS point or lower, whereby a quench hardening step is performed in which the steel member is hardened and hardened. Is done.
  • a tempering step is performed in which the quench-hardened steel member is heated to a temperature range of 230 ° C. or higher and 280 ° C. or lower and tempered.
  • the steps (S300) and (S400) constitute a heat treatment step in which the steel member is heat treated. Details of this heat treatment step will be described later.
  • a finishing step is performed. Specifically, the outer ring 11, the inner ring 12, the ball 13 and the like are finished by performing a finishing process such as a grinding process on the steel member that has been subjected to the heat treatment process. Thereby, the manufacturing method of the bearing member of the rolling bearing for motor in one embodiment of the present invention is completed, and the outer ring 11, the inner ring 12, the ball 13 and the like as the bearing member of the rolling bearing for motor are completed.
  • an assembly process is performed in the process (S600). Specifically, the outer ring 11, the inner ring 12, and the ball 13 produced in steps (S100) to (S500) are combined with a separately prepared cage 14, and the motor according to the embodiment of the present invention.
  • a grease-filled deep groove ball bearing 1 as a rolling bearing for use is assembled. Thereby, the manufacturing method of the rolling bearing for motors in one embodiment of the present invention is completed, and the grease-enclosed deep groove ball bearing 1 as the rolling bearing for motors is completed.
  • the horizontal direction indicates time, and the time elapses toward the right.
  • the vertical direction indicates the temperature, and the higher the temperature, the higher the temperature.
  • the steel member produced in the step (S200) is first heated to a temperature T1 which is a temperature equal to or higher than the A1 point, and is held for a time t1. At this time, the steel member is heated, for example, in an RX gas atmosphere. Thereafter, the steel member is immersed, for example, in oil (oil cooling), so that the steel member is cooled from the temperature of the A1 point or higher to the temperature of the MS point or lower to complete the quenching. The quench hardening process is completed by the above procedure.
  • the tempering step is performed by, for example, air cooling (cooling) to room temperature.
  • the temperature T1 is, for example, a temperature of 850 ° C.
  • the time t1 is, for example, 50 minutes.
  • the temperature T2 is, for example, a temperature of 230 ° C. or higher and 280 ° C. or lower.
  • the time t2 is 120 minutes, for example.
  • the A1 point indicates a point corresponding to a temperature at which the steel structure starts transformation from ferrite to austenite when the steel is heated.
  • MS point shows the point corresponded to the temperature which the structure
  • At least one bearing member among the outer ring 11, the inner ring 12, and the balls 13 as the rolling members can have an electrical resistivity of 28 ⁇ cm or less in the normal temperature atmosphere.
  • a steel member made of JIS standard SUJ2 is prepared in the steel member preparation step in view of the cost and procurement of the material. Then, after quenching in the quench hardening step, the steel member is heated to 230 ° C. or higher and 280 ° C. or lower in the tempering step, and tempering is performed.
  • the atomic vacancy density in an unfatigue state is reduced. In addition, it is possible to make it difficult to form atomic vacancies by making plastic deformation difficult.
  • the grease deep groove ball bearing has been described as an example of the rolling bearing according to the embodiment of the present invention.
  • the motor was demonstrated as an example of the apparatus with which the rolling bearing of one embodiment of this invention is applied.
  • the rolling bearing according to an embodiment of the present invention is not limited to the above, and may be an angular ball bearing, a cylindrical roller bearing, or the like.
  • the rolling bearing of one embodiment of the present invention may be applied to a rolling bearing for a machine tool main shaft.
  • an angular ball bearing and a cylindrical roller bearing will be described as another example of the rolling bearing according to the embodiment of the present invention, and the configuration of a machine tool including these will be described.
  • machine tool 100 includes a main shaft 101 having a cylindrical shape, a housing 102 surrounding outer peripheral surface 101 ⁇ / b> A of main shaft 101, and an outer peripheral surface of outer ring 11 being housing 102.
  • a rolling bearing for a machine tool main shaft disposed so as to be fitted between the main shaft 101 and the housing 102 so that the inner peripheral surface of the inner ring 12 is in contact with the outer peripheral surface 101A of the main shaft 101.
  • An angular ball bearing 10 (front bearing) and a cylindrical roller bearing 20 (rear bearing) are provided.
  • the main shaft 101 is supported so as to be rotatable about the axis with respect to the housing 102.
  • a motor rotor 103B is installed on the main shaft 101 so as to surround a part of the outer peripheral surface 101A, and a motor stator 103A is installed on the inner wall 102A of the housing 102 at a position facing the motor rotor 103B.
  • the motor stator 103A and the motor rotor 103B constitute a motor 103 (built-in motor).
  • the main shaft 101 can rotate relative to the housing 102 by the power of the motor 103.
  • the angular ball bearing 10 and the cylindrical roller bearing 20 are members that are disposed adjacent to the main shaft 101 in the machine tool 100 that processes a workpiece by rotating the main shaft 101. It is a rolling bearing for a machine tool main shaft that is rotatably supported with respect to a certain housing 102.
  • an angular ball bearing 10 includes an outer ring 11 as a first race member that is a bearing member of a rolling bearing for a machine tool spindle, an inner ring 12 as a second race member, and a plurality of rolling elements.
  • a ball 13 and a cage 14 are provided.
  • the outer ring 11 is formed with an outer ring rolling surface 11A as an annular first rolling surface.
  • the inner ring 12 is formed with an inner ring rolling surface 12A as an annular second rolling surface facing the outer ring rolling surface 11A.
  • a plurality of balls 13 is formed with a ball rolling surface 13A (the surface of the ball 13) as a rolling element rolling surface.
  • the balls 13 are in contact with each of the outer ring rolling surface 11A and the inner ring rolling surface 12A at the ball rolling surface 13A, and are arranged at a predetermined pitch in the circumferential direction by an annular retainer 14. It is rotatably held on an annular track. Thereby, the outer ring
  • the straight line connecting the contact point between the ball 13 and the outer ring 11 and the contact point between the ball 13 and the inner ring 12 is a radial direction (a direction perpendicular to the rotation axis of the angular ball bearing 10). ). Therefore, when a radial load is applied, a component force is generated in the axial direction (the direction of the rotation axis of the angular ball bearing 10).
  • two angular ball bearings 10 in the same direction are arranged on the front side (tip 101B side of main shaft 101), and the rear side (motor rotor 103B). On the side), two angular ball bearings 10 opposite to the front side are arranged to cancel the component force.
  • the cylindrical roller bearing 20 basically has the same configuration as the angular ball bearing 10 described above, and has the same effect. However, the cylindrical roller bearing 20 is different from the angular ball bearing 10 in the configuration of the raceway member and the rolling element.
  • the cylindrical roller bearing 20 includes an outer ring 11 as a first race member which is a bearing member of a rolling bearing for a machine tool main shaft, an inner ring 12 as a second race member, and cylindrical rollers 23 as a plurality of rolling elements, And a cage 14.
  • the outer ring 11 is formed with an outer ring rolling surface 11A as an annular first rolling surface.
  • the inner ring 12 is formed with an inner ring rolling surface 12A as an annular second rolling surface facing the outer ring rolling surface 11A.
  • the plurality of cylindrical rollers 23 are formed with roller rolling surfaces 23 ⁇ / b> A (outer peripheral surfaces of the cylindrical rollers 23) as rolling element rolling surfaces.
  • the cylindrical roller 23 is in contact with each of the outer ring rolling surface 11A and the inner ring rolling surface 12A at the roller rolling surface 23A, and is arranged at a predetermined pitch in the circumferential direction by the annular retainer 14. It is rotatably held on an annular track. Thereby, the outer ring
  • the manufacturing method of the rolling bearing for machine tool main spindle in an embodiment of the present invention is the same except for the manufacturing method of the rolling bearing for motor and the molding step.
  • steel members formed into a schematic shape such as the outer ring 11, the inner ring 12, the balls 13, and the cylindrical rollers 13 shown in FIGS. 7 and 8 are produced. The description of other manufacturing methods will not be repeated.
  • the lubricating device 40 mainly includes an angular ball bearing 30, a lubricating oil introducing member 31, a lid member 32, and an inner ring spacer 33.
  • FIG. 9 shows the periphery of the portion where the lubricating oil is introduced, and the main shaft, housing, etc. to which the lubricating device 40 is applied are not shown.
  • the inner ring 12 of the angular ball bearing 30 has an oil receiving circumferential groove 34 that receives the lubricating oil discharged from the lubricating oil introducing member 31.
  • the oil receiving circumferential groove 34 is provided on an end surface adjacent to the lubricating oil introducing member 31.
  • the slope portion 12B is formed so as to guide the lubricating oil accumulated in the oil receiving circumferential groove 34 to the inner ring rolling surface 12A of the inner ring 12 by centrifugal force and surface tension acting on the lubricating oil.
  • Lubricating oil introduction member 31 has a bowl-shaped portion 31 a extending in the axial direction from the side surface toward angular ball bearing 30.
  • a seal portion 31b is formed at the tip of the bowl-shaped portion 31a.
  • the seal portion 31 b is disposed in the vicinity of the ball 13 between the inner diameter surface of the cage 14 and the inner ring 12.
  • the seal portion 31 b is formed on an inclined surface having an inner diameter surface of the same angle ⁇ as the inclined surface portion 12 ⁇ / b> B of the inner ring 12.
  • the seal portion 31b is disposed on the slope portion 12B of the inner ring 12 with a gap ⁇ .
  • the lubricating oil introduction member 31 has a lubricating oil supply path 31c and a discharge port 31d.
  • the lubricating oil supply path 31c and the discharge port 31d communicate with each other.
  • the discharge port 31 d is opened facing the oil receiving circumferential groove 34 of the inner ring 12.
  • a drain oil circumferential groove 31e that opens toward the inner diameter side is formed in a portion closer to the base end side than the seal portion 31b of the flange portion 31a.
  • the drain oil circumferential groove 31e communicates with a drain oil recovery path (not shown). The waste oil is collected through the waste oil recovery path.
  • a very small amount of the oil discharged from the discharge port 31d of the lubricating oil introducing member 31 is used as the lubricating oil for the angular ball bearing 30, and the majority is used for cooling the inner ring 12.
  • a very small amount of the oil discharged to the oil receiving circumferential groove 34 of the inner ring 12 is introduced into the angular ball bearing 30 along the inclined surface portion 12 ⁇ / b> B by centrifugal force and surface tension of the oil accompanying the rotation of the inner ring 12. Used as a lubricating oil.
  • this lubricating oil for example, a very low viscosity lubricating oil equivalent to ISO VG2 is used.
  • the manufacturing method of the rolling bearing lubricated with this small amount of lubricating oil is the same as the manufacturing method of the rolling bearing for motor, except for the molding step.
  • steel members formed into a schematic shape such as the outer ring 11, the inner ring 12, and the ball 13 shown in FIG. 9 are produced. The description of other manufacturing methods will not be repeated.
  • this lubrication device 60 mainly has an angular ball bearing 50, a spacer 61, and a grease reservoir forming member 62.
  • this periphery of the portion where the lubricating oil is introduced is illustrated, and the main shaft, the housing, and the like to which the lubricating device 60 is applied are not illustrated.
  • the stepped surface 11 b is provided on the outer ring 11 of the angular ball bearing 50 so as to extend to the outer diameter side of the outer ring 11 that is separated from the ball 13.
  • the grease reservoir forming member 62 is a ring-shaped member in which a grease reservoir 63 for storing grease is formed.
  • the internal space sandwiched between the spacer 61 and the grease reservoir forming member 62 constitutes the grease reservoir 63.
  • the grease pool forming member 62 seals the spacer 61 with the outer side of the side wall portion of the grease pool forming member 62 and the inner side of the side wall portion of the spacer 61 after the grease is sealed in the grease pool portion 63. It is positioned in the axial direction of a main shaft (not shown).
  • a sealing material (not shown) is interposed between the spacer 61 and the grease reservoir forming member 62. This sealing material prevents grease leakage.
  • the tip 62 a of the grease reservoir forming member 62 is disposed along the inner diameter surface of the outer ring 11.
  • the distal end of the distal end portion 62a is arranged to face the step surface 11b.
  • a flow path 64 and a gap 65 are formed between the distal end portion 62 a and the outer ring 11.
  • a flow path 64 is formed by the peripheral wall of the tip portion 62a and the inner diameter surface portion of the outer ring 11 facing the tip wall 62a.
  • a gap 65 having a small gap amount ⁇ is formed in the axial direction of the main shaft (not shown) by the end surface of the tip end portion 62a and the step surface 11b facing the tip portion 62a.
  • the gap 65 communicates with the flow path 64 and opens at the edge of the outer ring rolling surface.
  • the gap amount ⁇ of the gap 65 is, for example, 0.05 to 0.1 mm.
  • the inner diameter surface following the end surface of the front end portion 62 a has a tapered surface 66 close to the ball 13, and is configured so that lubricating oil can easily accumulate between the tapered surface 66 and the ball 13.
  • the distance between the taper surface 66 and the ball 13 is preferably a minimum gap that is large enough to allow the oil adhering to the taper surface 66 to be transferred to the surface of the ball 13, for example, 0.2 mm or less.
  • the manufacturing method of the rolling bearing lubricated with the other small amount of lubricating oil is the same as the manufacturing method of the rolling bearing for motor, except for the molding step.
  • steel members formed into a schematic shape such as the outer ring 11, the inner ring 12, and the ball 13 shown in FIG. 10 are produced. The description of other manufacturing methods will not be repeated.
  • this lubricating device 60 a small amount of base oil is introduced into the angular ball bearing 50 from the grease reservoir 63 by utilizing the capillary phenomenon. In this method, no torque is generated by stirring the grease thickener with the retainer 14 or the like, so that low heat is generated and high speed operation is possible.
  • the rolling bearing of one embodiment of the present invention may be applied to a wheel rolling bearing.
  • a wheel rolling bearing will be described as another example of the rolling bearing according to the embodiment of the present invention, and the configuration of the wheel provided with the same will be described.
  • a double-row angular contact ball bearing 110 that is a rolling bearing for a wheel includes a rotation-side member such as a hub wheel 113 that supports a wheel 120 (drive wheel) including a wheel 111 and a tire 112. It supports so that it can rotate with respect to fixed side members, such as the knuckle 114.
  • FIG. 21 and FIG. 22 a double-row angular contact ball bearing 110 that is a rolling bearing for a wheel includes a rotation-side member such as a hub wheel 113 that supports a wheel 120 (drive wheel) including a wheel 111 and a tire 112. It supports so that it can rotate with respect to fixed side members, such as the knuckle 114.
  • the double-row angular ball bearing 110 mainly includes an outer ring 11, an inner ring 12, a ball 13, a cage 14, a seal member 15, and a magnetic encoder 115.
  • the inner ring 12 is fitted to the outer circumferential surface of the hub wheel 113, and the outer ring 11 is fitted to the inner circumferential surface of the knuckle 114.
  • the outer ring 11 is composed of one member.
  • the inner ring 12 is composed of two members.
  • the plurality of balls 13 are arranged in a double row. The plurality of balls 13 come into contact with each of the outer ring rolling surface 11A and the inner ring rolling surface 12A at the ball rolling surface 13A, and are arranged at a predetermined pitch in the circumferential direction by a comb-shaped cage 14. It is rotatably held on an annular track. Thereby, the outer ring
  • a straight line connecting the contact point between the ball 13 and the outer ring 11 and the contact point between the ball 13 and the inner ring 12 forms an angle with respect to the radial direction (the direction perpendicular to the rotation axis of the double-row angular ball bearing 110). Yes. Therefore, when a radial load is applied, a component force is generated in the axial direction (the direction of the rotation axis of the double-row angular ball bearing 110).
  • the straight line connecting the contact point between the ball 13 and the outer ring 11 of the adjacent ball 13 and the contact point between the ball 13 and the inner ring 12 is arranged in the reverse direction so as to cancel the component force.
  • a seal member 15 is inserted into the inner diameter of the outer ring 11 and the outer diameter of the inner ring 12. This seal member 15 can prevent oil leakage from inside the double row angular ball bearing and entry of foreign matter and moisture from outside the double row angular ball bearing.
  • the magnetic encoder 115 is press-fitted into the outer diameter of the end portion of the inner ring 12, and a magnetic member that is multipolarly magnetized in the circumferential direction in this state is in close proximity to the magnetic sensor 116 fixed to the knuckle 114. Thereby, the rotational speed of the wheel can be detected with high accuracy.
  • the wheel 120 is rotated by the rotation of the rotating side member such as the hub wheel 113 with respect to the fixed side member such as the knuckle 114.
  • the manufacturing method of the wheel rolling bearing according to the embodiment of the present invention is the same as the manufacturing method of the rolling bearing for motor, except for the molding step.
  • steel members formed into a schematic shape such as the outer ring 11, the inner ring 12, and the balls 13 shown in FIG. 22 are produced. The description of other manufacturing methods will not be repeated.
  • a rolling bearing for a motor a rolling bearing for a machine tool spindle, a rolling bearing for a wheel, a grease deep groove ball bearing, an angular contact ball bearing, a cylindrical roller bearing, a double row angular contact ball
  • the bearings and the race members and rolling elements included in the bearings have been described.
  • the rolling bearing and the bearing member thereof according to the present invention are not limited to these, and may be other forms of rolling bearings, raceway members and rolling elements included therein.
  • the rolling bearing of another form may be a radial bearing or a thrust bearing.
  • the track member includes an outer ring and an inner ring.
  • the rolling element may form a rolling surface between the inner ring, the outer ring, and the bearing disc.
  • the rolling elements include balls, cylindrical rollers, tapered rollers and the like.
  • JIS standard SUJ2 has been described as the material for the outer ring, the inner ring and the rolling element as the race member, 52100 (AISI or SAE standard), 100Cr6 (DIN standard), and GCr15, which are equivalent to the JIS standard SUJ2. (GSB standard) can also be applied.
  • the rolling bearing according to one embodiment of the present invention may be applied to an alternator rolling bearing.
  • an alternator rolling bearing will be described as another example of the rolling bearing according to the embodiment of the present invention, and the configuration of the alternator including the same will be described.
  • an alternator 200 includes a shaft (main shaft) 201, a rotor 202, a stator 203, a pulley 204, a housing 205, and grease that is a rolling bearing for an alternator. It mainly has a deep groove ball bearing 1.
  • a housing 205 is disposed so as to surround the rotor 202.
  • a shaft 201 is disposed so as to penetrate the central portion of the rotor 202 and penetrate the wall surface of the housing 205.
  • a stator 203 is disposed inside the housing 205 so as to face the outer peripheral surface of the rotor 202.
  • the housing 205 is disposed so as to face a part of the outer peripheral surface at one end of the shaft 201. Between the shaft 201 and the housing 205, a grease-filled deep groove ball bearing 1 that is a rolling bearing for an alternator is disposed. A shaft 201 is rotatably supported with respect to the housing 205 by the grease-filled deep groove ball bearing 1. A pulley 204 having an annular shape is attached to the tip of one end of the shaft 201 outside the housing 205. On the outer peripheral surface of the pulley 204, there is provided an engagement groove 206 on which a transmission belt (not shown) is hung.
  • the grease-enclosed deep groove ball bearing 1 that is a rolling bearing for an alternator has the same configuration as that of the grease-enclosed deep groove ball bearing 1 as a motor rolling bearing in the embodiment of the present invention.
  • a grease-filled deep groove ball bearing 1 that is a rolling bearing for an alternator is disposed adjacent to a shaft 201 that is rotated by this power in an alternator 200 that operates using power generated by a power source such as an engine (not shown).
  • a power source such as an engine (not shown).
  • it is a rolling bearing for electrical equipment / auxiliary equipment for automobiles that is rotatably supported with respect to the housing 205.
  • the grease-filled deep groove ball bearing 1 disposed at one end of the shaft 201 between the rotor 202 and the pulley 204 is called a front bearing.
  • the grease-filled deep groove ball bearing 1 disposed at the other end of the shaft 201 is called a rear bearing.
  • the grease-filled deep groove ball bearing 1 of the front bearing having a large stress such as a bending moment is more likely to cause hydrogen embrittlement separation than the grease-filled deep groove ball bearing 1 of the rear bearing.
  • a transmission belt (not shown) that rotates by power from a power source such as an engine (not shown) is hung on the outer peripheral surface of the pulley 204 in which the engagement groove 206 is formed.
  • the pulley 204 rotates around the axis of the shaft 201 together with the shaft 201 pivotally supported by the grease-filled deep groove ball bearing 1 with respect to the housing 205.
  • the rotor 202 rotates around the axis of the shaft 201 integrally with the shaft 201.
  • the rotor 202 rotates relative to the stator 203 that faces the outer peripheral surface of the rotor 202 and is fixed to the housing 205.
  • an electromotive force is generated in the coil of the stator 203 due to electromagnetic induction between the rotor 202 and the stator 203.
  • the manufacturing method of the grease-enclosed deep groove ball bearing 1 that is the rolling bearing for the alternator is the same as the manufacturing method of the grease-enclosed deep groove ball bearing 1 as the rolling bearing for a motor in the embodiment of the present invention.
  • serpentine formation means that a plurality of accessory parts are driven by a single belt. By using serpentine, a separate belt is not required for each accessory part, so that space can be saved. With serpentine formation, the load tends to increase and the load fluctuation tends to increase, so that slip is more likely to be induced than in the prior art.
  • the grease-enclosed deep groove ball bearing 1 which is a rolling bearing for an alternator is used for inner ring rotation, and therefore a part of the outer ring 11 is subjected to many load rotations. Therefore, early peeling due to hydrogen embrittlement is likely to occur in a part of the outer ring 11, and the bearing member according to the embodiment of the present invention is preferably applied to the outer ring 11.
  • the rolling bearing of one embodiment of the present invention may be applied to a pulley rolling bearing.
  • a pulley rolling bearing will be described as another example of a rolling bearing according to an embodiment of the present invention, and a configuration of a pulley including the same will be described.
  • a pulley 210 mainly includes a pulley body 211 and a grease-filled deep groove ball bearing 1 that is a rolling bearing for the pulley.
  • the pulley body 211 has an annular shape. On the outer peripheral surface of the pulley body 211, a transmission belt wrapping portion 212 on which a transmission belt (not shown) is laid is provided. A through hole 213 through which the shaft (main shaft) 218 passes is formed in the central portion on the inner diameter side of the pulley body 211.
  • the grease-enclosed deep groove ball bearing 1 is fitted into the pulley body 211 so that the inner peripheral surface of the through hole 213 and the outer ring 11 of the grease-enclosed deep groove ball bearing 1 are in contact with each other.
  • the pulley body 211 includes a cylindrical inner peripheral cylindrical portion 214 having a through hole on the inner peripheral surface, and a radially outer side from one end portion in the width direction (axial direction) of the inner peripheral cylindrical portion 214.
  • a flange portion 215 extending in the width direction
  • an outer peripheral cylindrical portion 216 extending in the width direction (axial direction) from the flange portion 215, and a flange portion extending radially inward from the other end portion in the width direction (axial direction) of the inner peripheral cylindrical portion 214 217.
  • the outer ring 11 of the grease-filled deep groove ball bearing 1 is fitted so as to contact the inner peripheral cylindrical portion 214 and the flange portion 217 of the pulley body 211.
  • shaft 218 is fitted into the inner ring 12 of the grease-filled deep groove ball bearing 1 by being fitted.
  • the grease-enclosed deep groove ball bearing 1 as the pulley rolling bearing has the same configuration as the grease-enclosed deep groove ball bearing 1 as the motor rolling bearing in the embodiment of the present invention.
  • the grease-enclosed deep groove ball bearing 1 that is a rolling bearing for a pulley is a pulley 210 that operates by using power generated by a power source such as an engine (not shown).
  • the pulley body 211 that is rotationally driven by this power passes through the pulley 210.
  • it is a rolling bearing for electrical equipment / auxiliary equipment for automobiles that is rotatably supported with respect to the shaft 218 arranged in this manner.
  • the pulley 210 rotates around the shaft 218 integrally with the shaft 218 supported by the grease-filled deep groove ball bearing 1.
  • the pulley 210 can function as a tensioner that applies tension to the transmission belt when the distance between the shafts on which the transmission belt is hung is fixed.
  • the pulley 210 can serve as an idler for changing the traveling direction of the transmission belt for the purpose of avoiding contact with various devices without an engine room that becomes an obstacle.
  • the manufacturing method of the grease-enclosed deep groove ball bearing 1 as the pulley rolling bearing is the same as the manufacturing method of the grease-enclosed deep groove ball bearing 1 as the motor rolling bearing in the embodiment of the present invention.
  • Rolling bearings for pulleys may be separated at an early stage due to hydrogen embrittlement, especially due to the effects of sliding and energization.
  • belts for driving electrical accessory parts including pulleys have been made serpentine. The load load tends to increase and the load fluctuation tends to increase, and slipping is more easily induced by serpentine formation.
  • the grease-enclosed deep groove ball bearing 1 that is a rolling bearing for pulleys is used for outer ring rotation, and therefore, a part of the inner ring 12 is subjected to many load rotations. Therefore, early peeling due to hydrogen embrittlement is likely to occur in a part of the inner ring 12, and it is preferable that the bearing member according to the embodiment of the present invention is applied to the inner ring 12.
  • the rolling bearing of one embodiment of the present invention may be applied to a rolling bearing for a car air conditioner electromagnetic clutch pulley.
  • a rolling bearing for a car air conditioner electromagnetic clutch pulley will be described as another example of a rolling bearing according to an embodiment of the present invention, and the configuration of a compressor with a car air conditioner electromagnetic clutch pulley mechanism including the same will be described.
  • the compressor includes a swash plate type swash plate compressor 220 and a compressor pulley mechanism 230.
  • a swash plate type swash plate compressor 220 includes a housing 221, a pulley bearing support member 234 fixed to the housing 221 by, for example, a screw, a main shaft 223, a rotating member 225 attached to the main shaft 223, and The swash plate 222 oscillates with the rotation of the rotary member 225, a piston rod 226 connected to the swash plate 222, and a piston 224 connected to the opposite side of the piston rod 226.
  • a rotating member / pulley support member bearing 231 composed of a double row thrust needle roller bearing as a support structure for receiving a thrust load.
  • a swash plate support bearing 233 composed of a double row thrust needle roller bearing is disposed as a support structure for receiving a thrust load.
  • the rotating member 225 rotates with the rotation of the main shaft 223, whereby the swash plate 222 swings.
  • the swing movement of the swash plate 222 causes the piston rod 226 to reciprocate, and the piston 224 connected to the piston rod 226 reciprocates within the cylinder.
  • a pulley bearing support member 234 is fixed to the housing 221 of the compressor 220 with screws.
  • a clutch electromagnet 235 is fixed to the pulley bearing support member 234.
  • a power transmission member 236 is fitted to the shaft end of the main shaft 223.
  • a car air conditioner electromagnetic clutch pulley 237 is fitted to the outer periphery of a grease-filled deep groove ball bearing 1 that is a rolling bearing for pulleys.
  • a main shaft support bearing 232 is disposed between the main shaft 223 and the pulley bearing support member 234. Further, between the inner peripheral surface of the car air conditioner electromagnetic clutch pulley 237 and the pulley bearing support member 234, a grease-filled deep groove ball bearing 1 that is a rolling bearing for the car air conditioner electromagnetic clutch pulley is disposed.
  • the grease-enclosed deep groove ball bearing 1 that is a rolling bearing for a car air conditioner electromagnetic clutch pulley has the same configuration as the grease-enclosed deep groove ball bearing 1 as a motor rolling bearing in the embodiment of the present invention.
  • the rotational driving force of the car air conditioner electromagnetic clutch pulley 237 rotating by a driving force (not shown) is transmitted to the main shaft 223 by exciting or de-energizing the clutch electromagnet 235 to the compressor. Or the rotation driving force of the car air conditioner electromagnetic clutch pulley 237 is not transmitted to the main shaft 223 and the compressor stops operating.
  • the compressor bearing is roughly classified into a compressor bearing used for the compressor 220 and a compressor bearing used for the pulley mechanism 230.
  • the compressor bearing used in the compressor 220 rotatably supports the swash plate support bearing 233 that rotatably supports the swash plate 222 and the rotating member 225, and the rotating member 225 and pulley bearing support member 234.
  • the rotating member / pulley support member bearing 231 corresponds to this.
  • the compressor bearings used in the pulley mechanism 230 include a spindle support bearing 232 that rotatably supports the spindle 223 and the pulley bearing support member 234, and a car air conditioner electromagnetic clutch pulley 237 and a pulley bearing support member 234.
  • the grease-enclosed deep groove ball bearing 1 which is a rolling bearing for a car air-conditioner electromagnetic clutch pulley that supports the rotor in a freely rotating manner corresponds to this.
  • a thrust needle roller bearing is used for the rotating member / pulley support member bearing 231 and the swash plate support bearing 233.
  • a thrust needle roller bearing 270 shown in FIG. 29 described later may be used.
  • the main shaft support bearing 232 a needle roller bearing or a cylindrical roller bearing is used.
  • a cylindrical roller bearing 20 shown in FIG. 8 may be used.
  • a grease-enclosed deep groove ball bearing 1 shown in FIG. 2 is used as a grease-enclosed deep groove ball bearing 1 that is a rolling bearing for a car air conditioner electromagnetic clutch pulley.
  • a double-row angular contact ball bearing may be used as the rolling bearing for the car air conditioner electromagnetic clutch pulley.
  • a double-row angular contact ball bearing 110 shown in FIG. 22 may be used as the double-row angular contact ball bearing.
  • a thrust needle roller bearing having a large roller diameter is used for the compressor bearing used in the compressor 220 in order to withstand the impact of the piston 224.
  • the thrust needle roller bearing has a structure in which the needle roller and the raceway surface are in line contact, and the raceway surface in contact with the needle roller and the rolling line has a circumferential speed from the rotation center of the bearing toward the outer diameter side. Will grow.
  • a thrust needle roller bearing which is a compressor bearing used in the compressor 220, does not have a bearing disc like a normal bearing, and a plurality of needle rollers are held by a cage and are in line contact with the raceway surface. Then rotate.
  • each of the swash plate 222 and the rotation member 225 has a raceway surface.
  • the rotation member / pulley support member bearing 231 the rotation member 225 and the pulley bearing support member 234 each have a raceway surface. It becomes the member which has.
  • the manufacturing method of the grease-enclosed deep groove ball bearing 1 that is a rolling bearing for a car air conditioner electromagnetic clutch pulley is the same as the manufacturing method of the grease-enclosed deep groove ball bearing 1 as a rolling bearing for a motor in the embodiment of the present invention. .
  • the grease-enclosed deep groove ball bearing 1 that is a rolling bearing for an electromagnetic clutch pulley of a car air conditioner is used for rotating the outer ring, and therefore, a part of the inner ring 12 is frequently rotated. Therefore, early peeling due to hydrogen embrittlement is likely to occur in a part of the inner ring 12, and it is preferable that the bearing member according to the embodiment of the present invention is applied to the inner ring 12.
  • the rolling bearing of one embodiment of the present invention may be applied to a continuously variable transmission rolling bearing.
  • a rolling bearing for a continuously variable transmission will be described as another example of a rolling bearing according to an embodiment of the present invention, and the configuration of a continuously variable transmission provided with the same will be described.
  • the belt-type continuously variable transmission 240 includes a primary pulley shaft (pulley shaft) 241, a primary pulley 242, a secondary pulley shaft 243, a secondary pulley (pulley shaft) 244, an endless belt 245, and a casing (housing) 246. And a grease-filled deep groove ball bearing 1 which is a rolling bearing for continuously variable transmission.
  • the primary pulley shaft 241 is provided with a primary pulley 242.
  • the primary pulley 242 has a primary pulley fixed sheave 242a and a primary pulley movable sheave 242b.
  • the primary pulley fixed sheave 242a is configured integrally with the primary pulley shaft 241.
  • the primary pulley movable sheave 242b passes through the primary pulley shaft 241 and is configured to be slidable in the axial direction of the primary pulley shaft 241.
  • One end of the primary pulley shaft 241 is connected to a clutch (not shown).
  • the other end of the primary pulley shaft 241 is rotatably supported by a grease-filled deep groove ball bearing 1 which is a continuously variable transmission rolling bearing fixed to the casing 246.
  • the secondary pulley shaft 243 is provided with a secondary pulley 244.
  • the secondary pulley 244 has a secondary pulley fixed sheave 244a and a secondary pulley movable sheave 244b.
  • the secondary pulley fixed sheave 244a is configured integrally with the secondary pulley shaft 243.
  • the secondary pulley movable sheave 244b passes through the secondary pulley shaft 243 and is configured to be slidable in the axial direction of the secondary pulley shaft 243.
  • Secondary pulley shaft 243 is supported by another bearing at one end to which a gear of a gear mechanism (not shown) is attached.
  • the other end of the secondary pulley shaft 243 is rotatably supported by a grease-filled deep groove ball bearing 1 which is a continuously variable transmission rolling bearing fixed to the casing 246.
  • a V-shaped endless belt 245 is stretched between the primary pulley 242 and the secondary pulley 244.
  • the primary pulley 242 is configured such that the width (primary pulley width) between the primary pulley fixed sheave 242a and the primary pulley movable sheave 242b can be changed by sliding the primary pulley movable sheave 242b.
  • the secondary pulley 244 is configured such that the width (secondary pulley width) between the secondary pulley fixed sheave 244a and the secondary pulley movable sheave 244b can be changed by sliding the secondary pulley movable sheave 244b.
  • the primary pulley 242 and the secondary pulley 244 are configured such that the respective radial positions where the endless belt 245 is stretched are changed.
  • a driving force is transmitted to the primary pulley shaft 241 from an engine (not shown) via a clutch.
  • the primary pulley width and the secondary pulley width By changing the primary pulley width and the secondary pulley width, the respective radial positions where the endless belt 245 is stretched are changed.
  • the driving force of the primary pulley shaft 241 is transmitted to the secondary pulley shaft 243 at a continuously variable speed.
  • a driving force is transmitted from the secondary pulley shaft 243 to the axle through a gear mechanism and a differential. Thereby, continuously variable transmission is achieved.
  • the manufacturing method of the grease-enclosed deep groove ball bearing 1 that is the rolling bearing for continuously variable transmission is the same as the manufacturing method of the grease-enclosed deep groove ball bearing 1 as the rolling bearing for motor in the embodiment of the present invention.
  • the grease-enclosed deep groove ball bearing 1 which is a rolling bearing for continuously variable transmission is used for inner ring rotation, and therefore, part of the outer ring 11 rotates a lot. Therefore, early peeling due to hydrogen embrittlement is likely to occur in a part of the outer ring 11, and the bearing member according to the embodiment of the present invention is preferably applied to the outer ring 11.
  • the rolling bearing of one embodiment of the present invention may be applied to a needle roller bearing.
  • a needle roller bearing When a needle roller bearing is used under conditions involving sliding such as rapid acceleration / deceleration, hydrogen is generated by separation of the lubricant, which may cause premature separation due to penetration into the steel.
  • the use conditions of needle roller bearings will tend to become stricter, and it is expected that those with excellent hydrogen embrittlement resistance will be required.
  • a shell needle roller bearing will be described as an example of a needle roller bearing which is another example of the rolling bearing according to the embodiment of the present invention.
  • the shell needle roller bearing 250 includes a shell outer ring 251 as a race member, needle rollers 252 as a plurality of rolling elements, and a cage 253.
  • the shell outer ring 251 has a raceway surface on the inner diameter surface.
  • the shell outer ring 251 has flange portions 251a that protrude toward the inner diameter side in the radial direction at both ends in the axial direction.
  • the needle rollers 252 are arranged along the raceway surface.
  • the holder 253 is configured to hold the interval between adjacent needle rollers 252.
  • the cage 253 is disposed on the inner side in the axial direction of the flange portion 251 a of the shell outer ring 251.
  • the shell outer ring 251 may be an open end type or a closed end type.
  • the manufacturing method of the shell needle roller bearing 250 according to the embodiment of the present invention is the same as the manufacturing method and the manufacturing process of the rolling bearing for motor according to the embodiment of the present invention.
  • steel members formed into a schematic shape such as the shell outer ring 251, the needle rollers 252, and the cage 253 shown in FIG. 27 are produced. The description of other manufacturing methods will not be repeated.
  • Shell-shaped needle roller bearings are used for supporting air compressors of automobiles that accelerate and decelerate rapidly by switching electromagnetic clutches, and when used for supporting ABS pumps that accelerate quickly when starting. When used at the large end, the rolling elements are likely to slip, and early peeling due to hydrogen embrittlement may occur.
  • a solid needle roller bearing will be described as an example of a needle roller bearing which is another example of the rolling bearing according to the embodiment of the present invention.
  • the solid needle roller bearing 260 includes an outer ring 261 as a race member, needle rollers 252 as a plurality of rolling elements, and a cage 253.
  • the outer ring 261 is formed thick and has flange portions 261a that protrude toward the inner diameter side in the radial direction at both ends in the axial direction.
  • the cage 253 is disposed on the radially inner side of the flange portion 261 a of the outer ring 261.
  • the manufacturing method of the solid needle roller bearing 260 in the embodiment of the present invention is the same as the manufacturing method and the manufacturing process of the rolling bearing for motor in the embodiment of the present invention.
  • steel members formed into a schematic shape such as the outer ring 261, the needle rollers 252 and the cage 253 shown in FIG. 28 are produced. The description of other manufacturing methods will not be repeated.
  • Solid needle roller bearings especially when used to support automobile air compressors that accelerate and decelerate suddenly by switching electromagnetic clutches, when used to support transmissions that accelerate quickly during start-up, are large in connecting rods for general-purpose engines. When used at the end, slippage between contact elements is likely to occur, and early peeling due to hydrogen embrittlement may occur.
  • a thrust needle roller bearing will be described as an example of a needle roller bearing which is another example of the rolling bearing according to the embodiment of the present invention.
  • the thrust needle roller bearing 270 includes a raceway disk 271 as a raceway member, needle rollers 252 as a plurality of rolling elements, and a cage 253.
  • a washer outer diameter portion 271 a on which the needle rollers 252 roll is formed on the outer side of the washer 271.
  • a washer protruding portion 271 b is formed at the tip of the washer 271 so as to protrude toward the inner diameter side in the radial direction.
  • the thrust needle roller bearing 270 is configured such that the needle roller 252 and the retainer 253 are not separated from the washer 271 by disposing the tip of the retainer 253 on the inner side in the axial direction of the washer protrusion 271b. ing.
  • the needle rollers 252 are arranged in the radial direction along the raceway surface.
  • the cage 253 is configured to hold the interval between the adjacent needle rollers 252 in the circumferential direction.
  • the manufacturing method of the thrust needle roller bearing 270 according to the embodiment of the present invention is the same as the manufacturing method and the manufacturing process of the rolling bearing for motor according to the embodiment of the present invention.
  • steel members formed into a schematic shape such as the washer 271, the needle rollers 252, and the cage 253 shown in FIG. 27 are produced. The description of other manufacturing methods will not be repeated.
  • Thrust needle roller bearings are constantly slipping from the rolling wheels during operation due to the peripheral speed difference between the inside and outside of the rolling element, and may cause early separation due to hydrogen embrittlement.
  • the needle roller bearing of one embodiment of the present invention may be a needle roller bearing with a cage.
  • cage 253 of needle roller bearing 280 with a cage may be made of a metal material.
  • the cage 253 made of a metal material has high strength.
  • cage 253 of needle roller bearing 280 with a cage may be made of a polymer material.
  • the cage 253 made of a polymer material has a high degree of freedom in shape and is easy to incorporate.
  • Needle roller bearings with cages especially when used as idler bearings in automobile transmissions that accelerate quickly at start-up, when used as planetary pinion support bearings for CVT, for large-end connecting rods of two-wheeled engines and general-purpose engines When used as a bearing or the like, the rolling elements are likely to slip, and early peeling due to hydrogen embrittlement may occur.
  • At least one bearing member among the outer ring 11 as the race member, the inner ring 12 and the ball 13 as the rolling element is made of JIS standard SUJ3.
  • the electrical resistivity inside is 36 ⁇ cm or less.
  • a SUJ2 standard rolling bearing steel ball having a diameter of 19.05 mm is pressed against at least one bearing member among the outer ring 11 and the inner ring 12 as the raceway member and the ball 13 as the rolling element with a load of 2.30 kN and held for 10 seconds. After the unloading, the depth of the indentation formed in the bearing member is 0.2 ⁇ m or less.
  • the Rockwell C scale hardness of the entire at least one bearing member among the outer ring 11 and the inner ring 12 as the race members and the balls 13 as the rolling elements is HRC 56.8 or more and HRC 58.7 or less.
  • the yield stress of the bearing member is 2196 MPa or more
  • the work hardening index of the bearing member is 0.22 or more and 0.33 or less
  • the plastic constant of the bearing member is 6469 MPa or more and 9825 MPa or less.
  • the balls 13 as rolling elements are made of JIS standard SUJ2, and the electrical resistivity of the balls 13 in the room temperature atmosphere may be 28 ⁇ cm or less.
  • a SUJ2 standard rolling bearing steel ball having a diameter of 19.05 mm is pressed against the ball 13 with a load of 1.97 kN, held for 10 seconds, and then unloaded, whereby the depth of indentation formed on the ball 13 is increased. It is 0.2 ⁇ m or less.
  • the Rockwell C scale hardness of the ball 13 as a whole is HRC 57.0 or more and HRC 59.3 or less.
  • the yield stress of the ball 13 obtained from the relationship between the indentation depth and the indentation load obtained by indenting the triangular pyramid diamond indenter of 115 ° and 100 ° to the ball 13 is 1977 MPa or more, and the ball 13 is work-hardened.
  • the index is 0.23 or more and 0.32 or less, and the plastic constant of the ball 13 is 5828 MPa or more and 8588 MPa or less.
  • a steel material preparation step for preparing a steel material composed of JIS standard SUJ3 is performed. Specifically, for example, steel bars or steel wires composed of JIS standard SUJ3 are prepared.
  • a forming step for producing a steel member formed into the general shape of the bearing member of the rolling bearing for motor is performed. Specifically, for example, forging, turning, and the like are performed on the above-described steel bars and steel wires, and the outer ring 11, the inner ring 12, the balls 13, and the like shown in FIGS. A steel member is produced.
  • the said process (S100) and (S200) comprise the steel member preparation process in which the steel member shape
  • the steel member is cooled from a temperature of A1 point or higher to a temperature of MS point or lower, whereby a quench hardening step is performed in which the steel member is hardened and hardened. Is done.
  • a tempering step is performed in which the quench-hardened steel member is heated to a temperature range of 270 ° C. to 320 ° C. and tempered.
  • the steps (S300) and (S400) constitute a heat treatment step in which the steel member is heat treated. Details of this heat treatment step will be described later.
  • a finishing step is performed. Specifically, the outer ring 11, the inner ring 12, the ball 13 and the like are finished by performing a finishing process such as a grinding process on the steel member that has been subjected to the heat treatment process. Thereby, the manufacturing method of the bearing member of the other rolling bearing for motors of one embodiment of the present invention is completed, and the outer ring 11, the inner ring 12, the ball 13, etc. as the bearing members of the rolling bearing for motor are completed.
  • an assembly process is performed in the process (S600). Specifically, the outer ring 11, the inner ring 12, and the ball 13 produced in steps (S100) to (S500) are combined with a separately prepared cage 14 and the like according to one embodiment of the present invention.
  • a grease-enclosed deep groove ball bearing 1 is assembled as a rolling bearing for the motor. Thereby, the manufacturing method of the other motor rolling bearing of one embodiment of the present invention is completed, and the grease-enclosed deep groove ball bearing 1 as the motor rolling bearing is completed.
  • the horizontal direction indicates time, and the time elapses toward the right.
  • the vertical direction indicates the temperature, and the higher the temperature, the higher the temperature.
  • the steel member produced in the step (S200) is first heated to a temperature T1 which is a temperature equal to or higher than the A1 point, and is held for a time t1. At this time, the steel member is heated, for example, in an RX gas atmosphere. Thereafter, the steel member is immersed, for example, in oil (oil cooling), so that the steel member is cooled from the temperature of the A1 point or higher to the temperature of the MS point or lower to complete the quenching. The quench hardening process is completed by the above procedure.
  • the tempering step is performed by, for example, air cooling (cooling) to room temperature.
  • the temperature T1 is, for example, 810 ° C.
  • the time t1 is, for example, 50 minutes.
  • the temperature T2 is, for example, a temperature of 270 ° C. or higher and 320 ° C. or lower.
  • the time t2 is 120 minutes, for example.
  • the A1 point indicates a point corresponding to a temperature at which the steel structure starts transformation from ferrite to austenite when the steel is heated.
  • MS point shows the point corresponded to the temperature which the structure
  • At least one bearing member among the outer ring 11 as the race member, the inner ring 12 and the ball 13 as the rolling element can have an electrical resistivity in a normal temperature atmosphere of 36 ⁇ cm or less.
  • a steel member made of JIS standard SUJ3 is prepared in the steel member preparation step in view of the cost of the material. Then, after quenching in the quench hardening process, the steel member is heated to 270 ° C. or more and 320 ° C. or less in the tempering process, and tempering is performed.
  • the atomic vacancy density in an unfatigue state is reduced. It is possible to reduce and make it difficult to form an atomic vacancy by making it difficult to plastically deform.
  • the rolling element may be made of JIS standard SUJ2 in view of the cost and procurement of the material.
  • the manufacturing method of the rolling bearing for motors having rolling elements made of JIS standard SUJ2 is the same as described above.
  • the rolling elements may be made of a material containing ceramics as in the case of the above-described JIS standard SUJ2.
  • maintaining a rolling element may be further provided, and the holder
  • rolling bearings include a rolling bearing for a motor (FIG. 1), a rolling bearing for a machine tool spindle (FIG. 6), a rolling bearing for a wheel (FIG. 21), and a rolling bearing for an alternator (FIG. 23), pulley rolling bearing (FIG. 24), car air conditioner electromagnetic clutch pulley rolling bearing (FIG. 25), continuously variable transmission rolling bearing (FIG. 26), shell needle roller bearing (FIG. 27), solid type Needle roller bearings (FIG. 28), thrust needle roller bearings (FIG. 29), and needle roller bearings with cages (FIGS. 30 and 31) can also be applied in the same manner as in the case of the JIS standard SUJ2.
  • At least one bearing member among the outer ring 11 as the race member, the inner ring 12, the ball 13 as the rolling element, and the cylindrical roller 14 is made of JIS standard SUJ2.
  • the electrical resistivity of the bearing member in the normal temperature atmosphere is 28 ⁇ cm or less. It was found that if the bearing member made of JIS standard SUJ2 is tempered at 230 ° C. or higher, the electrical resistivity of the bearing member in the normal temperature atmosphere is 28 ⁇ cm, which is almost the same value.
  • a SUJ2 standard rolling bearing steel ball having a diameter of 19.05 mm is pressed against the bearing member with a load of 1.97 kN, held for 10 seconds, and then unloaded.
  • the depth of the indentation formed on the bearing member is 0.2 ⁇ m or less. If the indentation depth is 0.2 ⁇ m or less as a guide, it can be said that plastic deformation is difficult.
  • tempering is performed at 230 ° C or higher and 280 ° C or lower, a SUJ2 standard rolling bearing steel ball with a diameter of 19.05mm is pressed against the bearing member with a load of 1.97kN, held for 10 seconds, and then unloaded.
  • the depth of the indentation formed in the film was 0.2 ⁇ m or less. Therefore, by setting the tempering temperature to 230 ° C. or higher and 280 ° C. or lower, it is difficult to plastically deform and it is difficult to generate atomic vacancies. Thereby, since hydrogen embrittlement resistance can be improved, early peeling due to hydrogen embrittlement can be suppressed. As described above, since the vacancy density in the unfatigue state can be reduced by setting the tempering temperature to 230 ° C. or higher, by setting the tempering temperature to 230 ° C. or higher and 280 ° C. or lower, It is possible to reduce the atomic vacancy density and make it difficult for plastic deformation to generate atomic vacancies.
  • the Rockwell C scale hardness of the entire bearing member is HRC57.0 or more and HRC59.3 or less.
  • the Rockwell C scale hardness of the entire bearing member in the range of tempering temperature 230 ° C. or higher and 280 ° C. or lower is HRC 57.0 or higher and HRC 59.3 or lower.
  • the bearing is obtained from the relationship between the indentation depth and the indentation load obtained by indenting the triangular pyramid diamond indenter with the opposite ridge angles of 115 ° and 100 ° into the bearing member.
  • the yield stress of the member is 1977 MPa or more
  • the work hardening index of the bearing member is 0.23 or more and 0.32 or less
  • the plastic constant of the bearing member is 5828 MPa or more and 8588 MPa or less.
  • the yield stress of the bearing member determined from the relationship between the indentation depth and the indentation load obtained by indenting the triangular pyramid diamond indenter with a ridge angle of 115 ° and 100 ° into the bearing member in the tempering temperature range of 230 ° C. to 280 ° C. is 1977 MPa.
  • the work hardening index of the bearing member is 0.23 to 0.32
  • the plastic constant of the bearing member is 5828 MPa to 8588 MPa.
  • At least one bearing member among the outer ring 11 as the race member, the inner ring 12, the ball 13 as the rolling element, and the cylindrical roller 14 is made of JIS standard SUJ3.
  • the electrical resistivity of the bearing member in the normal temperature atmosphere is 36 ⁇ cm or less. It was found that if the rolling bearing member made of JIS standard SUJ3 is tempered at 260 ° C. or higher, the electrical resistivity of the bearing member in the room temperature atmosphere is 36 ⁇ cm, which is almost the same value. On the other hand, it was found that when the tempering temperature was less than 260 ° C., the electrical resistivity of the bearing member was larger than 36 ⁇ cm and the fluctuation was large.
  • the tempering temperature to 260 ° C. or more and setting the electrical resistivity of the bearing member in the normal temperature atmosphere to 36 ⁇ cm or less, the atomic vacancy density in an unfatigue state can be reduced. Thereby, since hydrogen embrittlement resistance can be improved, early peeling due to hydrogen embrittlement can be suppressed.
  • a steel ball for SUJ2 standard rolling bearing having a diameter of 19.05 mm is pressed against the bearing member with a load of 2.30 kN, and is unloaded after being held for 10 seconds.
  • the depth of the indentation formed on the bearing member is 0.2 ⁇ m or less. If the indentation depth is 0.2 ⁇ m or less as a guide, it can be said that plastic deformation is difficult.
  • a tempering treatment is performed at 270 ° C. or higher and 320 ° C. or lower, a SUJ2 standard rolling bearing steel ball having a diameter of 19.05 mm is pressed against the bearing member with a load of 2.30 kN, held for 10 seconds, and then unloaded.
  • the depth of the indentation formed in the film was 0.2 ⁇ m or less. Therefore, by setting the tempering temperature to 270 ° C. or more and 320 ° C. or less, it is difficult to plastically deform and it is possible to make it difficult to generate atomic vacancies. Thereby, since hydrogen embrittlement resistance can be improved, early peeling due to hydrogen embrittlement can be suppressed. As described above, since the vacancy density in the unfatigue state can be reduced by setting the tempering temperature to 260 ° C. or higher, by setting the tempering temperature to 270 ° C. or higher and 320 ° C. or lower, It is possible to reduce the atomic vacancy density and make it difficult for plastic deformation to generate atomic vacancies.
  • the Rockwell C scale hardness of the entire bearing member is HRC56.8 or more and HRC58.7 or less.
  • the Rockwell C scale hardness of the entire bearing member in the tempering temperature range of 270 ° C. to 320 ° C. is HRC 56.8 to HRC 58.7.
  • the bearing is obtained from the relationship between the indentation depth and the indentation load obtained by indenting the triangular pyramid diamond indenter with the opposite ridge angles of 115 ° and 100 ° into the bearing member.
  • the yield stress of the member is 2196 MPa or more
  • the work hardening index of the bearing member is 0.22 or more and 0.33 or less
  • the plastic constant of the bearing member is 6469 MPa or more and 9825 MPa or less.
  • the yield stress of the bearing member determined from the relationship between the indentation depth obtained by indenting the triangular pyramid diamond indenter with a ridge angle of 115 ° and 100 ° into the bearing member in the range of 270 ° C. to 320 ° C. and the indentation load is 2196 MPa.
  • the work hardening index of the bearing member is 0.22 to 0.33
  • the plastic constant of the bearing member is 6469 MPa to 9825 MPa.
  • the ball 13 as the rolling element is made of JIS standard SUJ2, and the electric resistivity of the rolling element in the room temperature atmosphere is 28 ⁇ cm or less. It was found that when the rolling elements made of JIS standard SUJ2 were tempered at 230 ° C. or higher, the electrical resistivity of the rolling elements in the room temperature atmosphere was 28 ⁇ cm, which was almost the same value. On the other hand, it was found that when the tempering temperature was less than 230 ° C., the electric resistivity of the rolling element was larger than 28 ⁇ cm and the fluctuation was large. Therefore, by setting the tempering temperature to 230 ° C.
  • the atomic vacancy density in an unfatigue state can be reduced. Thereby, since hydrogen embrittlement resistance can be improved, early peeling due to hydrogen embrittlement can be suppressed. Since the rolling element is made of JIS standard SUJ2, the procurement can be improved.
  • a SUJ2 standard rolling bearing steel ball having a diameter of 19.05 mm is pressed against the rolling element with a load of 1.97 kN, and then unloaded after being held for 10 seconds.
  • the depth of the indentation formed on the rolling element is 0.2 ⁇ m or less. If the indentation depth is 0.2 ⁇ m or less as a guide, it can be said that plastic deformation is difficult.
  • a tempering treatment is performed at 230 ° C. or higher and 280 ° C. or lower, a SUJ2 standard rolling bearing steel ball having a diameter of 19.05 mm is pressed against the rolling element at a load of 1.97 kN, held for 10 seconds, and then unloaded.
  • the depth of the indentation formed in the film was 0.2 ⁇ m or less. Therefore, by setting the tempering temperature to 230 ° C. or higher and 280 ° C. or lower, it is difficult to plastically deform and it is difficult to generate atomic vacancies. Thereby, since hydrogen embrittlement resistance can be improved, early peeling due to hydrogen embrittlement can be suppressed. As described above, since the vacancy density in the unfatigue state can be reduced by setting the tempering temperature to 230 ° C. or higher, by setting the tempering temperature to 230 ° C. or higher and 280 ° C. or lower, It is possible to reduce the atomic vacancy density and make it difficult for plastic deformation to generate atomic vacancies.
  • the Rockwell C scale hardness of the entire rolling element is HRC 57.0 or more and HRC 59.3 or less.
  • the Rockwell C scale hardness of the entire rolling element in the tempering temperature range of 230 ° C. to 280 ° C. is HRC 57.0 to HRC 59.3.
  • the rolling force obtained from the relationship between the indentation depth and the indentation load obtained by indenting the triangular pyramid diamond indenter with the opposite ridge angle 115 ° and 100 ° into the rolling element is 1977 MPa or more
  • the work hardening index of the rolling element is 0.23 or more and 0.32 or less
  • the plastic constant of the rolling element is 5828 MPa or more and 8588 MPa or less.
  • the yield stress of the rolling element obtained from the relationship between the indentation depth obtained by indenting the triangular pyramid diamond indenter with a ridge angle of 115 ° and 100 ° into the rolling element in the range of tempering temperature 230 ° C. or more and 280 ° C. or less is 1977 MPa.
  • the work hardening index of the rolling element is 0.23 to 0.32
  • the plastic constant of the rolling element is 5828 MPa to 8588 MPa.
  • the rolling element may be made of a material containing ceramics.
  • the hydrogen embrittlement resistance can be improved, so that early peeling due to hydrogen embrittlement can be suppressed.
  • a cage for holding the rolling elements may be further provided, and the cage may be made of a material containing metal.
  • the metal cage is less likely to cause early peeling due to hydrogen embrittlement than the resin cage, and therefore, early peeling due to hydrogen embrittlement can be suppressed.
  • the main shaft 92 may be rotatably supported with respect to the housing 93.
  • a bearing can be provided.
  • rolling bearings of one embodiment of the present invention it is effective even in the case of general grease lubrication or air-oil lubrication, but by lubricating with a small amount of lubricating oil, the race member and the rolling element This is particularly effective when the oil film between the two is thin.
  • the lubrication apparatus 40 that uses a lower viscosity lubricating oil while reducing the amount of oil described above is operated at a higher speed than the air-oil lubrication generally used in rolling bearings for machine tool main spindles that rotate at high speeds. It is prone to basation. Therefore, the oil film is thinner than air-oil lubrication. For this reason, in this lubricating device 40, since hydrogen easily enters, the possibility of early peeling due to hydrogen embrittlement increases. However, application of one and other rolling bearings according to an embodiment of the present invention can suppress early separation due to hydrogen embrittlement.
  • the fixed member disposed so as to face the rotating side member of the wheel 120 and the outer peripheral surface of the rotating side member.
  • the rotating member may be supported rotatably with respect to the fixed member.
  • a main shaft 201 of an alternator 200 and a housing 205 arranged to face the outer peripheral surface of the main shaft 201 may be rotatably supported with respect to the housing 205.
  • the main shaft 218 and the pulley body 211 arranged to face the outer peripheral surface of the main shaft 218 are further provided.
  • the main shaft 218 may be rotatably supported with respect to the pulley body 211.
  • the car air conditioner electromagnetic clutch pulley 237 and the inner peripheral surface of the car air conditioner electromagnetic clutch pulley 237 are opposed to each other.
  • a pulley bearing support member 234 may be further provided, and the car air conditioner electromagnetic clutch pulley 237 may be rotatably supported with respect to the pulley bearing support member 234.
  • rolling bearings for car air conditioner electromagnetic clutch pulleys that have a long service life can be prevented because early peeling due to hydrogen embrittlement can be suppressed even under conditions in which slippage is induced more than before due to increased load load and increased load fluctuation associated with serpentine conversion. Can be provided.
  • the pulley shaft 241 of the continuously variable transmission 240 and the outer peripheral surface of the pulley shaft 241 are arranged to face each other. And a pulley shaft 241 may be rotatably supported with respect to the housing 246.
  • a rolling bearing can be provided.
  • a rolling bearing for a continuously variable transmission can be provided.
  • one and other rolling bearings may be a shell needle roller bearing 250 as shown in FIG.
  • Shell-type needle roller bearings are used in ABS pumps that accelerate quickly when starting, especially when used in support of air compressors in automobiles that suddenly accelerate or decelerate by switching electromagnetic clutches under conditions involving sudden acceleration and deceleration.
  • the rolling elements When used for support or when used for the large end of a connecting rod of a general-purpose engine, the rolling elements are likely to slip, and early peeling due to hydrogen embrittlement may occur.
  • it is possible to suppress the early peeling due to hydrogen embrittlement even under such conditions, and thus to provide a long-life shell needle roller bearing 250. it can.
  • one and other rolling bearings may be a solid needle roller bearing 260 as shown in FIG.
  • Solid needle roller bearings support transmissions that accelerate quickly during start-up, especially when used to support air compressors in automobiles that accelerate and decelerate suddenly by switching electromagnetic clutches under conditions involving sudden acceleration and deceleration.
  • slippage between contact elements is likely to occur, and early peeling due to hydrogen embrittlement may occur.
  • one and other rolling bearings may be a thrust needle roller bearing 270 as shown in FIG.
  • the thrust needle roller bearing is constantly slipped from the rolling wheel during operation due to the difference in peripheral speed between the inside and outside of the rolling element, and may cause early separation due to hydrogen embrittlement.
  • Thrust needle roller bearings may experience early peeling due to hydrogen embrittlement even under conditions involving slippage such as rapid acceleration and deceleration.
  • one and other needle roller bearings may include a cage 253 as shown in FIGS.
  • Needle roller bearings with cages are used under idle conditions such as sudden acceleration / deceleration, especially when used as idler bearings for automobile transmissions that accelerate quickly at start-up, and as planetary pinion support bearings for CVT.
  • the rolling elements When used as a large-end bearing for a connecting rod of a two-wheeled engine or a general-purpose engine, the rolling elements are likely to slip and may cause early separation due to hydrogen embrittlement.
  • Example 1 In order to evaluate the mechanical characteristics of the raceway member and rolling element of the rolling bearing of the present invention, the following tests were conducted. Hereinafter, the test procedure, test conditions, and test results of each test will be described.
  • SUJ2 of this invention should just have a chemical component of JIS specification SUJ2, in this Example, SUJ2 which has a chemical component shown in Table 1 as an example was made into the test piece.
  • C carbon
  • Si silicon
  • Mn manganese
  • P phosphorus
  • S sulfur
  • Cr chromium
  • Mo molybdenum
  • Ni nickel
  • Cu copper
  • Al aluminum
  • Ti titanium
  • O oxygen
  • the tempering temperature dependence of the electrical resistivity of each test piece will be described. As the tempering temperature increased, the electrical resistivity decreased and showed a tendency to reach the lower limit at about 230 ° C. or higher. This corresponds to the generation of atomic vacancies during quenching, the density of which decreases with increasing tempering temperature. From FIG. 11, it was found that if tempering is performed at a temperature of about 230 ° C. or higher, the atomic vacancy density when not fatigued can be reduced. It was found that the electrical resistivity should be 28 ⁇ cm or less.
  • the indentation became shallowest by tempering at around 250 ° C. That is, it can be said that plastic deformation hardly occurs at a tempering temperature of about 250 ° C. below the practical maximum contact surface pressure acting between the contact elements between the raceway member of the rolling bearing and the rolling element.
  • plastic deformation is difficult if it is in the range of 230 ° C. or higher and 280 ° C. or lower, which is the tempering temperature at which the indentation depth is 0.2 ⁇ m or less. Since atomic vacancies are generated by plastic deformation, that is, by interaction of dislocations, the resistance to hydrogen deformation is superior in resistance to plastic deformation. Therefore, it was found that the hydrogen embrittlement resistance was excellent in the range of 230 ° C. or higher and 280 ° C. or lower.
  • HRC Rockwell C scale
  • the HRC hardness of a test piece having the same dimensions as the above (2) indentation test and heat-treated under the same conditions was measured.
  • the test results are shown in Table 4 and FIG. 13, and the relationship between the tempering temperature and the HRC hardness is shown.
  • the HRC hardness in the range where the tempering temperature is 230 ° C. or more and 280 ° C. or less is HRC 57.0 or more and HRC 59.3 or less.
  • the 2-indenter method uses an indentation test on the flat part of the specimen using two types of indenters with different tip angles, and determines the plastic properties of the material (yield stress ⁇ Y , work hardening) from the coefficient of the load curve. This is a method for obtaining an index n and a plastic constant K).
  • yield stress ⁇ Y work hardening index n
  • plastic constant K plastic constant
  • a load-unloading curve showing the relationship between indentation load P and indentation depth h was obtained by an indentation test.
  • the indentation load P is, for example, 50 g.
  • a coefficient C 100 ° of the opposite ridge angle 100 ° and a coefficient C 115 ° of the opposite ridge angle 115 ° were obtained.
  • E * is a synthetic Young's modulus and is defined by the formula (3).
  • ⁇ s is the Poisson's ratio of the test piece, and is 0.3 which is an actual measurement value.
  • ⁇ i is the Poisson's ratio of the indenter, and is 0.07 which is a literature value.
  • E s is Young's modulus of the test piece was to be a measured value 204GPa.
  • E i is the Young's modulus of the indenter, which is a literature value of 1141 GPa.
  • ⁇ r100 ° is a characteristic stress with a ridge angle of 100 °
  • ⁇ r115 ° is a characteristic stress with a ridge angle of 115 °.
  • the stress-strain diagram there are always passing points regardless of the work hardening index n. The stress at this point is the characteristic stress, and the strain corresponding to the characteristic stress is the characteristic strain.
  • the characteristic strain ⁇ r100 ° at the opposite edge angle of 100 ° is 0.07
  • the characteristic strain ⁇ r115 ° at the opposite edge angle of 115 ° is 0.037.
  • ⁇ r100 ° and ⁇ r115 ° were determined from the equations (2) and (3). Also, ⁇ r100 ° and ⁇ r115 ° are known. The work hardening index n and the plastic constant K were determined by substituting these into equation (4) and solving the simultaneous equations.
  • Yield stress ⁇ Y was determined as the stress value at the intersection of equation (5) with the obtained work hardening index n and plastic constant K substituted and equation (6) with Young's modulus E of 204 GPa.
  • Young's modulus E a measured value of 204 GPa that did not depend on the tempering temperature was used.
  • FIG. 16, FIG. 17 and FIG. 18 show the test results, and show the relationship between the tempering temperature and the yield stress, work hardening index, and plastic constant.
  • the yield stress ⁇ Y reached a maximum near the tempering temperature of 250 ° C.
  • the work hardening index n decreased as the tempering temperature increased.
  • the plastic constant K decreased as the tempering temperature increased.
  • the tempering temperature at which the electrical resistivity is 28 ⁇ cm or less is about 230 ° C. or higher
  • the tempering temperature at which indentation is difficult to form is about 230 ° C. or higher. It was the range of 280 degrees C or less. From Table 5, the plastic properties in the range of tempering temperature from 230 ° C. to 280 ° C. are roughly yield stress ⁇ Y is 1977 Mpa or more, work hardening index n is 0.23 to 0.32, plastic constant K is 5828 MPa to 8588 MPa It becomes as follows.
  • the taper-shaped outer ring test piece 80 has a width W of 14 mm (tolerance +0, -0.01 mm), an outer diameter OD ⁇ 72 mm (tolerance +0, -0.01 mm), and an inner diameter ID1 ⁇ 51.19 mm (tolerance ⁇ 0. 025 mm), an inner diameter ID2 ⁇ of 67.12 mm (tolerance ⁇ 0.025 mm) on the side where the taper shape expands, and an opposing angle A between the taper shapes A59.3 ° (tolerance ⁇ 0.5 °).
  • grinding finishing was performed, and the inner raceway surface was superfinished to a surface roughness Rq (root mean square roughness) of 0.03 ⁇ m.
  • tempering was performed at 250 ° C. for 120 minutes, which was the tempering temperature at which the indentation was most difficult in the above (2) indentation test.
  • tempering was performed at 180 ° C., which is a standard tempering temperature, for 120 minutes.
  • the test was conducted by combining tapered outer ring test piece 80 with inner ring 81 of angular ball bearing (JIS standard 7306B), 13 steel balls 82 and cage 83.
  • the inner ring 81 and the steel ball 82 of the angular ball bearing are SUJ2 standard quenching and tempering products.
  • the water-mixed oil is 5 mass in ISO VG100 additive-free turbine oil (density 0.887 g / cm 3 , kinematic viscosity at 40 ° C. 100.9 mm 2 / s, kinematic viscosity at 100 ° C. 11.68 mm 2 / s). % (Tolerance ⁇ 0.01% by mass) of pure water.
  • the water-mixed oil After making the water-mixed oil, it was sealed with a thin film for food packaging so that water would not evaporate, and stirred with a stirrer for 2 hours or more. Thereafter, a test was conducted with the water-containing oil. 60 mL of water-mixed oil was injected. As shown in FIG. 20, due to the tapered shape, a water-mixed oil flows in the direction of arrow Y in the figure. The water-containing oil was circulated by connecting a water-containing oil inlet / outlet provided in a housing (not shown) with a nylon tube.
  • the calculated life L 10h of the taper-shaped outer ring test piece 80 alone is 2611 hours when converted into a two-cylinder model and calculated. However, the effect of slip was ignored. The separation was detected with a vibrometer. The test was conducted for 20 hours, and if it did not peel off during that time, it was replaced with a newly prepared water-mixed oil. The test for 20 hours and the exchange of water-containing oil were repeated until peeling occurred.
  • the test was performed for each of the Example and the Comparative Example. All peeling occurred on the taper-shaped outer ring test piece 80, and all of the peeling started from the inside of the surface layer.
  • the SUJ2 steel ball 82 is a standard quenching and tempering product, but no peeling occurred. This is probably because the steel ball 82 has a larger effective load volume than the tapered outer ring test piece 80.
  • Table 6 shows the test results, and shows L 10 , L 50 and Weibull slope (shape parameter) e obtained by applying the peeling life of the example and the comparative example to the 2-parameter Weibull distribution.
  • L 10 of the comparative example is 33.7 hours, was calculated life L 10h 1 to about 100 minutes of 2611 hours is.
  • the L 10 embodiment although not inferior to the calculated life L 10h and 517.3 hours, was about 15 times longer life compared with the comparative example. From this, it was found that the examples had an effect of making it difficult to cause early peeling due to hydrogen embrittlement.
  • Example 2 In order to evaluate the mechanical characteristics of the race member and rolling element of the rolling bearing of the present invention when at least one bearing member of the race member and rolling element is made of JIS standard SUJ3, the following test was performed. Hereinafter, the test procedure, test conditions, and test results of each test will be described. In addition, about the matter similar to said Example 1, description other than what is shown below is not repeated. Although SUJ3 of this invention should just have a chemical component of JIS specification SUJ3, in this Example, SUJ3 which has a chemical component shown in Table 7 as an example was used as the test piece.
  • C carbon
  • Si silicon
  • Mn manganese
  • P phosphorus
  • S sulfur
  • Cr chromium
  • Mo molybdenum
  • Ni nickel
  • Cu copper
  • Al aluminum
  • Ti titanium
  • O oxygen
  • the tempering temperature dependence of the electrical resistivity of each test piece will be described. As the tempering temperature increased, the electrical resistivity decreased, and a tendency to reach the lower limit at about 260 ° C. or higher was shown. This corresponds to the generation of atomic vacancies during quenching, the density of which decreases with increasing tempering temperature. From FIG. 32, it was found that if tempering is performed at a temperature of about 260 ° C. or higher, the atomic vacancy density when not fatigued can be reduced. It was found that the electrical resistivity should be 36 ⁇ cm or less.
  • the indentation became shallowest by tempering around 300 ° C. That is, it can be said that plastic deformation hardly occurs at a tempering temperature of about 300 ° C. below the practical maximum contact surface pressure acting between the contact elements between the raceway member of the rolling bearing and the rolling element.
  • plastic deformation is difficult if it is in the range of 270 ° C. to 320 ° C., which is the tempering temperature at which the indentation depth is 0.2 ⁇ m or less. Since atomic vacancies are generated by plastic deformation, that is, by interaction of dislocations, the resistance to hydrogen deformation is superior in resistance to plastic deformation. Therefore, it was found that the hydrogen embrittlement resistance was excellent in the range of 270 ° C to 320 ° C.
  • Example 3 HRC (Rockwell C scale) hardness test As in Example 1, the HRC hardness of a test piece having the same dimensions as the above (2) indentation test and heat-treated under the same conditions was measured. The test results are shown in Table 10 and FIG. 34, and the relationship between the tempering temperature and the HRC hardness is shown.
  • the HRC hardness in the range where the tempering temperature is 270 ° C. or higher and 320 ° C. or lower was HRC 56.8 or higher and HRC 58.7 or lower.
  • FIG. 35, FIG. 36 and FIG. 37 show the test results, and show the relationship between the tempering temperature and each of yield stress, work hardening index, and plastic constant.
  • the yield stress ⁇ Y reached a maximum near the tempering temperature of 300 ° C.
  • the work hardening index n decreased as the tempering temperature increased.
  • the plastic constant K decreased as the tempering temperature increased.
  • the tempering temperature at which the electrical resistivity is 36 ⁇ cm or less is about 260 ° C. or higher
  • the tempering temperature at which indentation is difficult to form is about 270 ° C. or higher. It was the range of 320 degrees C or less.
  • Table 11 the plastic characteristics tempering temperature is in the range of 270 ° C. or higher 320 ° C. is approximately the yield stress sigma Y is more than 2196Mpa, work hardening coefficient n 0.22 or 0.33 or less, the plastic constant K than 6469MPa 9825 It becomes as follows.
  • the heat treatment was performed by quenching by heating in an RX gas atmosphere at 810 ° C. for 50 minutes. Thereafter, in this example, tempering was performed for 120 minutes at 300 ° C., which was the tempering temperature at which indentation was most difficult in the above (2) indentation test. On the other hand, in a comparative example for comparison with the present example, tempering was performed at 180 ° C., which is a standard tempering temperature, for 120 minutes.
  • the test is performed by combining a tapered outer ring test piece 80 with an inner ring 81 of angular ball bearing (JIS standard 7306B), 13 steel balls 82, and a cage 83. It was. Using these, tests were performed under the same conditions as in Example 1.
  • Table 12 shows the test results, and shows L 10 , L 50 and Weibull slope (shape parameter) e obtained by applying the peeling life of the present example and the comparative example to the 2-parameter Weibull distribution.
  • L 10 of the comparative example is 28.2 hours, was calculated life L 10h 1 to about 100 minutes of 2611 hours is.
  • L 10 of the present embodiment although it did not reach the calculated life L 10h and 691.2 hours, showed about 25 times longer life compared with the comparative example. From this, it was found that this example had an effect of making it difficult to cause early peeling due to hydrogen embrittlement.
  • the present invention can be applied particularly advantageously to a rolling bearing in which at least one bearing member of the raceway member and the rolling element is made of JIS standard SUJ2.

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

Abstract

L'invention porte sur un roulement à billes comportant des billes (13) qui sont en contact avec la bague externe (11) et la bague interne (12) et qui sont disposées pour pouvoir rouler dans le chemin de roulement annulaire. Au moins l'un des éléments du roulement, qui sont la bague externe (11), la bague interne (12) et chaque bille (13) est composée de SUJ2 selon une norme JIS et a une résistivité électrique de 28 μΩcm ou moins de prévenir l'apparition d'écaillage précoce provoqué par la fragilité à l'hydrogène dans le roulement à billes.
PCT/JP2010/066179 2009-09-29 2010-09-17 Roulement à billes WO2011040267A1 (fr)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107210689A (zh) * 2015-02-10 2017-09-26 Cts公司 轴向无刷dc电机
US10454403B2 (en) 2016-02-05 2019-10-22 Cts Corporation Axial brushless DC motor with fractional and hold step function

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JP2003065337A (ja) * 2001-08-24 2003-03-05 Nsk Ltd 転がり軸受
JP2005308151A (ja) * 2004-04-23 2005-11-04 Ntn Corp 車輪用軸受装置
JP2008308743A (ja) * 2007-06-15 2008-12-25 Ntn Corp 工作機械用転動部材および工作機械用転がり軸受
JP2009108893A (ja) * 2007-10-29 2009-05-21 Ntn Corp 玉軸受

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JP2003065337A (ja) * 2001-08-24 2003-03-05 Nsk Ltd 転がり軸受
JP2005308151A (ja) * 2004-04-23 2005-11-04 Ntn Corp 車輪用軸受装置
JP2008308743A (ja) * 2007-06-15 2008-12-25 Ntn Corp 工作機械用転動部材および工作機械用転がり軸受
JP2009108893A (ja) * 2007-10-29 2009-05-21 Ntn Corp 玉軸受

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Publication number Priority date Publication date Assignee Title
CN107210689A (zh) * 2015-02-10 2017-09-26 Cts公司 轴向无刷dc电机
EP3257150A4 (fr) * 2015-02-10 2018-08-08 CTS Corporation Moteur à courant continu sans balai axial
US10148152B2 (en) 2015-02-10 2018-12-04 Cts Corporation Axial brushless DC motor
US10658902B2 (en) 2015-02-10 2020-05-19 Cts Corporation Axial brushless DC motor
CN107210689B (zh) * 2015-02-10 2020-12-22 Cts公司 轴向无刷dc电机
US10454403B2 (en) 2016-02-05 2019-10-22 Cts Corporation Axial brushless DC motor with fractional and hold step function

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