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WO2014013754A1 - Roulement à billes à contact angulaire et roulement à double rangée - Google Patents

Roulement à billes à contact angulaire et roulement à double rangée Download PDF

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Publication number
WO2014013754A1
WO2014013754A1 PCT/JP2013/057263 JP2013057263W WO2014013754A1 WO 2014013754 A1 WO2014013754 A1 WO 2014013754A1 JP 2013057263 W JP2013057263 W JP 2013057263W WO 2014013754 A1 WO2014013754 A1 WO 2014013754A1
Authority
WO
WIPO (PCT)
Prior art keywords
outer ring
ring
axial direction
ball bearing
raceway surface
Prior art date
Application number
PCT/JP2013/057263
Other languages
English (en)
Japanese (ja)
Inventor
晋 高野
友章 坂瀬
Original Assignee
日本精工株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日本精工株式会社 filed Critical 日本精工株式会社
Priority to DE201321000161 priority Critical patent/DE212013000161U1/de
Priority to CN201390000036.9U priority patent/CN203743212U/zh
Publication of WO2014013754A1 publication Critical patent/WO2014013754A1/fr

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Classifications

    • 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
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
    • F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
    • F16C19/543—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact 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
    • F16C19/02—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
    • 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
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
    • 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
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • F16C33/6607—Retaining the grease in or near the bearing
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7843—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc
    • F16C33/7846—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with a gap between the annular disc and the inner race
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7843—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc
    • F16C33/7853—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with one or more sealing lips to contact the inner race
    • F16C33/7856—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with one or more sealing lips to contact the inner race with a single sealing lip
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7886—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted outside the gap between the inner and outer races, e.g. sealing rings mounted to an end face or outer surface of a race
    • 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

Definitions

  • the present invention relates to an angular ball bearing and a combined bearing.
  • a grease-sealed bearing is suitable for a compact machine design because of its simple lubricating structure.
  • a deep groove ball bearing has been used for a long time, and an angular ball bearing has been used as a rotating body support device in recent years.
  • the life of grease sealed in bearings tends to be reduced, and countermeasures have been required.
  • the outer diameter of the shaft is desirably equal to or greater than that of the conventional product.
  • the bearings used in industrial machines are thin-walled products, for example, ISO diameter series 0 or 9, so that the outer diameter of the rolling elements is also reduced, and the load capacity is disadvantageous.
  • a typical example is a machine tool built-in spindle of a machine tool, and the same applies to a centrifugal separator, a textile machine, and the like.
  • an increase in the ratio “L / d” between the length L and the diameter d of the shaft 100 means a decrease in shaft rigidity, and shaft bending during use tends to occur.
  • What is supported one shaft 100 is supported by three bearings 110) is known.
  • the increase in “L / d” is disadvantageous in maintaining accuracy of the machine parts and in assembling accuracy, and acts on the bearing 110 as misalignment (inclination and displacement of the core of the inner and outer rings). When three points are supported, this misalignment tends to easily affect the bearing 110.
  • the angular ball bearing has a contact angle unlike the deep groove ball bearing (see FIG. 8), and the internal stress generated by the load support shifts in the axial direction (in FIG. 7 and FIG. The generation position is indicated by A.), and the thickness of the side of the raceway surface is required.
  • the angular ball bearing used for industrial machinery needs to be a thin product as described above, if an O-ring groove or a seal groove is provided in the outer ring, the wall thickness is further reduced and the strength is reduced. .
  • the present invention has been made in view of the above-described problems, and an object of the present invention is to provide a long-life angular contact ball bearing and a combination bearing used in grease lubrication.
  • the above object of the present invention can be achieved by the following constitution. (1) an inner ring having an inner ring raceway surface formed on the outer periphery; An outer ring having an outer ring raceway surface formed on the inner periphery; A plurality of balls incorporated with a contact angle between the inner ring raceway surface and the outer ring raceway surface; An angular ball bearing having The axial width of the outer ring is greater than 0 in the width series in ISO, The outer periphery of the inner ring has an inner ring shoulder formed on one axial side with respect to the inner ring raceway surface, and a counter bore formed on the other axial side.
  • An inner peripheral portion of the outer ring includes a pair of outer ring shoulder portions formed on both sides in the axial direction across the outer ring raceway surface, and a seal member on one axial side with respect to the outer ring shoulder portion facing the inner ring shoulder portion. And a seal groove formed to fix another seal member on the other side in the axial direction with respect to the shoulder portion of the outer ring facing the counter bore. And Angular contact ball bearings that are lubricated internally with grease. (2) The angular ball bearing according to (1), wherein an axial width of the outer ring is larger than 1 in a width series in ISO.
  • the axial width of the outer ring is set to be greater than 0 in the width series in ISO, the bearing internal space can be increased and the amount of grease filled can be increased. It is possible to extend the grease life. Furthermore, since the outer ring is a wide product, it is possible to obtain a space for providing a seal groove for fixing the seal member on both axial sides of the inner peripheral portion.
  • the axial width of the outer ring is set to be greater than 1 in the width series in ISO, the amount of grease can be further increased and the outer ring shoulder and seal groove are formed. Space to do.
  • the O-ring groove for fixing the O-ring is provided in the outer ring which is a wide product, so that the design becomes easy.
  • the outer ring formed as a wide product is provided with the seal groove, the O-ring groove, and the outer ring raceway surface being offset in order from one side in the axial direction. Even in the case of a thin product, it is possible to suppress a decrease in strength due to the provision of the seal groove, the O-ring groove, and the outer ring raceway surface. In particular, since the O-ring groove is provided between the seal groove and the outer ring raceway surface in the axial direction, it is possible to prevent the outer ring from extending more than necessary in the axial direction.
  • the outer ring formed as a wide product is provided with the O-ring groove, the seal groove, and the outer ring raceway surface being offset from the one side in the axial direction. Even in the case of a thin product, it is possible to suppress a decrease in strength due to the provision of the O-ring groove, the seal groove, and the outer ring raceway surface.
  • the counter bore can be shortened and the wall thickness necessary for maintaining the strength is ensured. Is possible.
  • the one end surface in the axial direction of the inner ring and the one end surface in the axial direction of the outer ring are substantially at the same position. It is possible to prevent the ball from riding on the counter bore of the inner ring when placed on a board or the like.
  • the counter bore can be shortened and is necessary for maintaining the strength. It is possible to ensure the wall thickness.
  • a rotating body support device 1 that rotatably supports a rotating shaft of an industrial machine (not shown) such as a machine tool on a housing includes a pair of single-row angular ball bearings 10A and 10B as shown in FIG. It is composed of a combination bearing 10 configured by combining two back surfaces so that the contact angle substantially represents a letter C.
  • Each of the single-row angular ball bearings 10A and 10B is, for example, a thin product of ISO diameter series 0 or 9, and an inner ring 20 having an inner ring raceway surface 22 formed on the outer peripheral portion and an outer ring raceway surface 32 formed on the inner peripheral portion.
  • a plurality of balls 40 incorporated with a contact angle between the outer ring raceway surface 22 and the inner ring raceway surface 22 and the outer ring raceway surface 32, and a cage 50 that holds the plurality of balls 40 in a rollable manner. .
  • the cage 50 is made of mild steel, copper alloy, resin or the like, and a resin that is lightweight and has excellent wear resistance is particularly suitable when operating at high speed under grease lubrication.
  • a resin material a cotton cloth impregnated with a phenol resin and thermally cured is available.
  • Polyamide is a thermoplastic resin that can be mass-produced at low cost, and so-called super engineering plastics such as polyphenylene sulfide and polyetheretherketone are suitable in terms of heat resistance, chemical resistance, and high strength. Furthermore, glass fibers and carbon fibers are mixed with these thermoplastic resins, and the strength increases.
  • the outer periphery of the inner ring 20 has an inner ring shoulder 24 formed on the outer side in the axial direction (one side in the axial direction) with respect to the inner ring raceway surface 22, and a counter bore 26 formed on the inner side in the axial direction (the other side in the axial direction).
  • the inner peripheral portion of the outer ring 30 includes a pair of first and second outer ring shoulder portions 34 and 35 formed on both sides in the axial direction across the outer ring raceway surface 32, and a first outer ring that radially faces the inner ring shoulder portion 24.
  • a first seal groove 36 formed to fix the first seal member 61 on the outer side in the axial direction with respect to the shoulder portion 34, and an axial direction with respect to the second outer ring shoulder portion 35 diametrically opposed to the counter bore 26.
  • a second seal groove 37 formed to fix the second seal member 62 inside.
  • the first and second seal members 61, 62 are made of metal cores 61a, 62a and elastic bodies 61b, 62b covering the cores 61a, 62a. Lips 61c, 62c are provided at the ends of the elastic bodies 61b, 62b. Is formed.
  • the lip 61c of the first seal member 61 is opposed to the recess 28 formed at the axially outer end of the outer periphery of the inner ring 20 with a slight gap, and the lip 62c of the second seal member 62 is By facing the counter bore 26 at the outer peripheral portion in the radial direction through a slight gap, these gaps constitute a labyrinth, so that the grease sealed inside the bearing is sealed, and from the outside to the inside of the bearing Intrusion of foreign matter is prevented.
  • the axial width of the outer ring 30 is formed so as to be larger than 0 in the width series in ISO, more preferably greater than 1 in the width series in ISO, and is larger than the axial width of the inner ring 20. Is set. Therefore, the outer ring 30 has first and second extending portions 30a and 30b extending toward both axial sides from the inner ring 20, and the outer circumferences of the first and second extending portions 30a and 30b.
  • the part is provided with first and second O-ring grooves 38 and 39 for fixing an O-ring (not shown).
  • the inclination with the housing is buffered by the O-ring, so misalignment (inclination of the core of the inner and outer rings Deviation) can be suppressed.
  • the elastic bodies 61b, 62b and O-rings of the first and second seal members 61, 62 are usually made of rubber, and nitrile butadiene is generally used, and an additive is added to improve heat resistance and chemical resistance. When it contains, it is suitable. If further high temperature properties are required, acrylic rubber and fluorine rubber are used. Employed especially when the atmosphere is chemically special. Typical examples are cutting water for machine tools, coolant for power engines, and petrochemical gases.
  • the outer ring 30 is provided with the first O-ring groove 38, the first seal groove 36, the outer ring raceway surface 32, the second seal groove 37, and the second O-ring groove 39 offset from the outside in the axial direction. And are arranged so as not to overlap each other.
  • the pair of outer rings 30 and 30 are positioned in the axial direction by abutting each other, and the pair of inner rings 20 and 20 is paired with the pair of second extending portions 30b and 30b between the pair of inner rings 20 and 20. Is positioned in the axial direction by arranging a spacer 70 having substantially the same width.
  • the outer diameter dimension of the spacer 70 is set slightly smaller than the inner diameter dimension of the adjacent seal member 62. Thereby, even if the spacer 70 and the seal member 62 approach each other due to deformation in the bearing due to a manufacturing error or a load load, interference does not occur, and occurrence of abnormal loss (rotational torque) as a rotating body can be prevented. If there is no such concern, the outer diameter of the spacer 70 is made larger than the inner diameter of the seal member 62, so that the cross-sectional area of the spacer 70 increases and the inner ring 20 side is tightened and fixed with a nut or the like.
  • the outer diameter of the spacer 70 is made smaller than the inner diameter of the seal member 62 in the vicinity of the seal member 62 (outside in the axial direction), and the center side of the spacer 70 (inner side in the axial direction) is sealed.
  • the inner diameter of the member 62 may be equal to or larger than the inner diameter
  • the outer peripheral surface of the spacer 70 may have a cylindrical shape with several stages.
  • the combination bearing 10 configured by combining the single-row angular ball bearings 10A and 10B on the back surface has been described.
  • the combination bearing 10 may be configured by combining the single-row angular ball bearings 10A and 10B on the front surface. I do not care. Further, the single row angular ball bearings 10A and 10B may be used alone without being combined with each other.
  • the axial width of the outer ring 30 is set to 0, more preferably greater than 1 in the width series in ISO. Can be increased, the amount of grease filled can be increased, and the grease life can be extended. Furthermore, since the outer ring 30 becomes a wide product, a space for providing the first and second seal grooves 36 and 37 for fixing the first and second seal members 61 and 62 on both sides in the axial direction of the inner peripheral portion thereof is provided. It is possible to obtain.
  • first and second O-ring grooves 38 and 39 for fixing the O-ring to the outer ring 30 which is a wide product are provided, the design becomes easy.
  • the outer ring 30 that is a wide product is offset by a first O-ring groove 38, a first seal groove 36, an outer ring raceway surface 32, a second seal groove 37, and a second O-ring groove 39 in order from one side in the axial direction. Therefore, even if the outer ring 30 is a thin product, the first and second seal grooves 36 and 37, the first and second O-ring grooves 38 and 39, and the outer ring raceway surface 32 are provided. It is possible to suppress a decrease in strength due to this.
  • first seal member 61 and the second seal member 62 fixed to the outer ring 30 face the outer peripheral portion of the inner ring 20, the sealing performance is maintained even when the angular ball bearings 10A and 10B are handled alone. It is possible to prevent foreign matter from entering from the outside.
  • the counter bore 26 can be shortened, and the wall thickness necessary for maintaining the strength can be ensured.
  • the spacer 70 is disposed between the single-row angular ball bearings 10A and 10B in the axial direction of the inner rings 20 and 20, the counter bores 26 and 26 can be shortened, and the meat required for maintaining the strength can be obtained. It is possible to ensure the thickness.
  • the combination bearing of the present embodiment has the same basic configuration as that of the combination bearing of the first embodiment. Therefore, the same or corresponding parts are denoted by the same reference numerals, and the description thereof is omitted or simplified. The explanation will be focused on.
  • the single-row angular contact ball bearings 10 ⁇ / b> A and 10 ⁇ / b> B of the present embodiment each have an inner ring 20 and an outer ring 30 that have substantially the same axial width, and a pair of inner rings 20, 20 and a pair of The outer rings 30 are positioned in the axial direction by abutting each other.
  • the axially outer side surface 21 of the inner ring 20 and the axially outer side surface 31 of the outer ring 30 are substantially in the same position, so-called “flat”. Therefore, it is possible to prevent the balls 40 from getting on the counter bore 26 of the inner ring 20 when the axially outer sides of the single row angular ball bearings 10A and 10B are placed on a surface plate or the like.
  • the first and second O-ring grooves 38 and 39 are provided between the outer ring raceway surface 32 and the first and second seal grooves 36 and 37 in the axial direction, respectively.
  • the outer ring 30 is provided on the outer peripheral portion of the outer ring 30 so as to overlap the shoulder parts 34 and 35 in the axial direction. That is, the outer ring 30 is provided with a first seal groove 36, a first O-ring groove 38, an outer ring raceway surface 32, a second O-ring groove 39, and a second seal groove 37 in an offset order from the outside in the axial direction. Arranged so as not to overlap each other.
  • the outer ring 30 is a thin product, the first and second seal grooves 36 and 37, the first and second O-ring grooves 38 and 39, and the outer ring raceway surface 32 are reduced in strength. Can be suppressed.
  • the first and second O-ring grooves 38 and 39 are provided between the first and second seal grooves 36 and 37 and the outer ring raceway surface 32 in the axial direction, the outer ring 30 is more than necessary in the axial direction. Can be prevented from being extended.
  • the axial direction of the inner ring 20 is such that the axial inner side surface 23 of the inner ring 20 is positioned axially outside the axial inner side surface 33 of the outer ring 30.
  • the width may be set short.
  • a spacer 70 is disposed between the inner rings 20 and 20 of the single row angular ball bearings 10A and 10B in the axial direction.
  • the second seal groove 37 is formed so that the second seal member 62 faces the counter bore 26 of the inner ring 20, and the spacer 70
  • the axial positional relationship between the second seal groove 37 and the second O-ring groove 39 may be reversed.
  • the sealing performance is good even when the angular ball bearings 10A and 10B are handled alone. It is possible to maintain and prevent entry of foreign matter from the outside.
  • the number of O-ring grooves provided on the outer peripheral portion of the outer ring 30 is not limited to two as in the above-described embodiment, and it is sufficient that at least one is provided, and three considering the strength of the outer ring 30. It does not matter as above.
  • Rotating body support apparatus 10 Combination bearing 10A, 10B Angular contact ball bearing 20
  • Inner ring 21 Axial outer surface (Axial one side surface) 22
  • Inner ring raceway surface 23 Axial inner side surface 24
  • Inner ring shoulder portion 26 Counter bore 28 Recess 30
  • Outer ring 30a, 30b Extension portion 31
  • Axial outer side surface (Axial one side surface) 32
  • Outer ring raceway surface 33

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

Abstract

L'invention porte sur un roulement à billes à contact angulaire et un roulement à double rangée ayant une longue durée de vie, qui sont utilisés avec une lubrification par graisse. La largeur des bagues extérieures (30) dans la direction axiale est supérieure à 0 dans la série des largeurs ISO. La circonférence extérieure des bagues intérieures (20) comprend un épaulement de bague intérieure (24), formé en dehors de la surface de voie de roulement de bague intérieure (22) dans la direction axiale, et un contre-alésage (26) formé sur l'autre côté dans la direction axiale. La circonférence intérieure des bagues extérieures (30) comprend : des premier et second épaulements de bague extérieure (34, 35) qui sont formés sur les deux côtés de la surface de voie de roulement de bague extérieure (32) dans la direction axiale, avec interposition de la surface de voie de roulement ; une première gorge d'étanchéité (36) formée de façon à fixer un premier élément d'étanchéité (61) à l'extérieur, dans la direction axiale, du premier épaulement de bague extérieure (34) qui fait face à l'épaulement de bague intérieure (24) ; et une seconde gorge d'étanchéité (37) formée de façon à fixer un second élément d'étanchéité (62) à l'intérieur, dans la direction axiale, du second épaulement de bague extérieure (35) qui fait face au contre-alésage (26). Le volume intérieur des roulements à billes à contact angulaire (10A, 10B) est lubrifié avec de la graisse.
PCT/JP2013/057263 2012-07-19 2013-03-14 Roulement à billes à contact angulaire et roulement à double rangée WO2014013754A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE201321000161 DE212013000161U1 (de) 2012-07-19 2013-03-14 Schrägkugellager und Kombinationslager
CN201390000036.9U CN203743212U (zh) 2012-07-19 2013-03-14 角接触球轴承以及组合式轴承

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012160611A JP2014020481A (ja) 2012-07-19 2012-07-19 アンギュラ玉軸受
JP2012-160611 2012-07-19

Publications (1)

Publication Number Publication Date
WO2014013754A1 true WO2014013754A1 (fr) 2014-01-23

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PCT/JP2013/057263 WO2014013754A1 (fr) 2012-07-19 2013-03-14 Roulement à billes à contact angulaire et roulement à double rangée

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JP (1) JP2014020481A (fr)
CN (1) CN203743212U (fr)
DE (1) DE212013000161U1 (fr)
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CN108708909A (zh) * 2018-07-24 2018-10-26 安徽利达汽车轴承制造有限公司 一种角接触球轴承密封圈
TWI709695B (zh) * 2016-06-03 2020-11-11 日商恩天股份有限公司 多列組合斜角滾珠軸承裝置
CN112483553A (zh) * 2019-09-11 2021-03-12 斯凯孚公司 滚动轴承装置和滚动轴承

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WO2019044528A1 (fr) * 2017-09-01 2019-03-07 日本精工株式会社 Roulement à billes oblique, dispositif de roulement et dispositif à broche
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CN107429746A (zh) * 2015-03-12 2017-12-01 斯凯孚公司 在滚动轴承中保持润滑剂的装置、滚动轴承组件和滚动轴承组件的组装方法
CN107429746B (zh) * 2015-03-12 2020-07-03 斯凯孚公司 在滚动轴承中保持润滑剂的装置、滚动轴承组件和滚动轴承组件的组装方法
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CN112483553A (zh) * 2019-09-11 2021-03-12 斯凯孚公司 滚动轴承装置和滚动轴承

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