WO2022186094A1 - Palier à roulement et cage pour palier à roulement - Google Patents

Palier à roulement et cage pour palier à roulement Download PDF

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Publication number
WO2022186094A1
WO2022186094A1 PCT/JP2022/008113 JP2022008113W WO2022186094A1 WO 2022186094 A1 WO2022186094 A1 WO 2022186094A1 JP 2022008113 W JP2022008113 W JP 2022008113W WO 2022186094 A1 WO2022186094 A1 WO 2022186094A1
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WO
WIPO (PCT)
Prior art keywords
rolling bearing
ball
retainer
diameter surface
pocket
Prior art date
Application number
PCT/JP2022/008113
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English (en)
Japanese (ja)
Inventor
光 石田
直明 辻
千春 伊藤
Original Assignee
Ntn株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2022186094A1 publication Critical patent/WO2022186094A1/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
    • F16C19/02—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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • 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

Definitions

  • the present invention relates to rolling bearings and rolling bearing retainers, and, for example, to techniques for reducing vibration and improving lubrication life in rolling bearings for motors and the like.
  • Patent Document 1 A synthetic resin retainer for use in rolling bearings has been proposed (Patent Document 1).
  • This synthetic resin retainer consists of two annular bodies facing each other in the axial direction, and a plurality of pockets for accommodating balls are formed at intervals in the circumferential direction between the two annular bodies.
  • a rolling bearing has been proposed in which a circumferential groove-shaped grease pocket is formed on the inner diameter surface of the outer ring (Patent Document 2).
  • the band width W which is the radial dimension of the pocket portion Pt, is in the range of 40% to 50% of the ball diameter with the ball PCD as the center. It has a shape in which the ball 30 is held by .
  • the band width W is 70% to 80% of the radial dimension D1 between the inner diameter surface of the outer ring 31 and the outer diameter surface of the inner ring 32 .
  • the gap ⁇ between the ball 30 and the inner diameter side edge of the pocket portion Pt and the gap ⁇ 1 between the ball 30 and the outer diameter side edge of the pocket portion Pt are widened. For this reason, less grease adhering to the ball surface is scraped off by the pocket portion Pt, and more grease is caught between the pocket portion Pt and the ball 30 . As a result, the shear resistance of the grease between the pocket portion Pt and the balls 30 increases, the behavior of the retainer Rt becomes unstable, and the vibration and noise values increase.
  • the static space volume is used as the upper limit of 100%. be done.
  • the "static space volume” is the volume of the space (static space) excluding the rolling elements and cage in the bearing space between the inner and outer rings.
  • the static space volume is the volume of the static space between the seal members on both axial sides in the bearing space between the inner and outer rings.
  • a space in the bearing space that includes the rolling elements and the retainer is called a dynamic space.
  • An object of the present invention is to provide a rolling bearing and a rolling bearing retainer that can reduce vibration, improve lubrication life, and reduce manufacturing costs.
  • a rolling bearing according to the present invention comprises inner and outer rings, a plurality of balls interposed between the inner and outer rings, and a retainer having pockets for holding the respective balls.
  • Each annular body includes a plurality of pocket wall portions that are arranged at regular intervals in the circumferential direction and each constitutes an inner wall surface of the pocket, and the pocket wall portions that are adjacent to each other in the circumferential direction.
  • a rolling bearing having a plurality of coupling plate portions that are coupled, wherein the two annular bodies are overlapped and coupled to each other by the respective coupling plate portions
  • the retainer has cutout portions on the inner diameter surface and the outer diameter surface of the pocket wall portion so that the band width, which is the radial dimension of the pocket wall portion, is smaller than the radial dimension of the coupling plate portion.
  • the center in the radial direction of the band width between the deepest part of the notch on the inner diameter surface and the deepest part of the notch on the outer diameter surface is near the pitch circle diameter of the ball
  • the band width is 35% or less of the diameter of the ball
  • the circumferential range of each notch is 50 to 100% of the diameter of the ball.
  • the vicinity of the pitch diameter of the ball is within a range of ⁇ 5% of the diameter of the ball based on the pitch diameter (PCD) of the ball.
  • the grease adhering to the ball is scraped off by the notches on the inner diameter side and the outer diameter side of the pocket wall, respectively, so that the amount of grease caught between the pocket and the ball is reduced.
  • shear resistance of the grease between the pocket and the balls is reduced, the behavior of the retainer is stabilized, and a remarkable effect is achieved that vibration and noise are reduced.
  • the band width of the notch exceeds 35% of the diameter of the ball, or if the circumferential range of the notch is less than 50% of the diameter of the ball, less grease will be scraped off and the space between the pocket and the ball will be reduced. More grease gets caught. In this case, the behavior of the retainer is not stable, and the effect of suppressing vibration and noise is small.
  • a notch is provided on the outer diameter surface of the pocket wall, increasing the static space.
  • the stationary space volume is increased compared to the case where the notch is provided only on the inner diameter surface of the pocket wall or the case where the pocket wall is not provided with the notch.
  • the band width of the retainer may be 50% or less of the radial dimension between the inner diameter surface of the outer ring and the outer diameter surface of the inner ring. In this case, it is possible to more reliably reduce the amount of grease caught between the pocket and the ball.
  • the retainer may be made of a resin material with a melting point of 200 to 350°C. In this case, no abnormal sliding marks are observed on the retainer, which is preferable.
  • a resin material having a melting point of less than 200° C. melts or wears abnormally due to frictional heat caused by sliding between the ball and the pocket wall.
  • a resin material having a melting point exceeding 350° C. increases manufacturing costs.
  • the ball may be a ceramic ball.
  • the specific gravity smaller than that of a steel ball made of bearing steel or the like, it is possible to increase the speed of the rolling bearing and improve the heat resistance.
  • the rolling bearing may be a rolling bearing for a motor.
  • Rolling bearings for motors can reduce vibration, improve lubrication life, and reduce manufacturing costs. can.
  • the rolling bearing retainer of the present invention is a retainer used in the above-described rolling bearing of the present invention.
  • FIG. 1 is a longitudinal sectional view of a rolling bearing according to a first embodiment of the invention
  • FIG. 2 is an enlarged cross-sectional view of a main part of the same rolling bearing
  • FIG. 3 is a front view of the retainer of the rolling bearing as seen from the axial direction; It is an enlarged front view of the main part of the retainer. It is an expanded sectional view of the same retainer.
  • FIG. 4B is a sectional view along line IVB-IVB of FIG. 4A; It is a schematic diagram showing a rolling bearing for a motor in which the same rolling bearing is applied to a motor.
  • FIG. 11 is an enlarged vertical cross-sectional view of a main part of a conventional rolling bearing.
  • FIG. 3 is a front view of a conventional rolling bearing retainer viewed from the axial direction;
  • FIG. 10 is an enlarged vertical cross-sectional view of a main part of another conventional rolling bearing;
  • FIG. 6 is a front view of another conventional rolling bearing retainer viewed from the axial direction.
  • FIG. 6 is a front view of another conventional rolling bearing retainer viewed from the axial direction.
  • FIG. 1 A rolling bearing and a rolling bearing retainer according to an embodiment of the present invention will be described with reference to FIGS. 1 to 5.
  • the rolling bearing 1 of this example is a deep groove ball bearing comprising an inner ring 2, an outer ring 3, and a plurality of rolling elements interposed between rolling surfaces 2a, 3a of the inner and outer rings 2, 3. , a retainer 6 for holding each ball 5, and a seal 4.
  • the balls 5 are steel balls or ceramic balls.
  • each seal 4 in this example is a non-contact seal in which the lip does not contact the inner ring seal groove 8 .
  • the seal 4 is formed by molding a rubber material 4b on a metal core 4a.
  • the retainer 6 is of a rolling element guide type, and as shown in FIG. 4B, is composed of two synthetic resin annular bodies 10, 10 that overlap each other in the axial direction.
  • the outer diameter surfaces of the annular bodies 10, 10 form cylindrical surfaces having the same diameter except for the notch 13b.
  • Each inner diameter surface of 10, 10 forms a cylindrical surface with the same diameter except for the notch portion 13a.
  • Each annular body 10 is formed by, for example, injection molding a synthetic resin.
  • the two annular bodies 10, 10 have the same shape and can be molded with the same mold.
  • the synthetic resin polyolefin-based resins, thermosetting resins, engineering plastics, and super engineering resins can be used as long as they are injection-moldable and have sufficient heat resistance, oil resistance, mechanical strength, etc. as cage materials.
  • Plastic or the like can be used.
  • the retainer 6 is preferably made of a resin material having a melting point of 200°C to 360°C, preferably 200°C to 350°C. If the melting point is less than 200° C., the resin may be melted or abnormally worn due to frictional heat caused by sliding between the ball and the pocket wall. In order to increase the strength of the resin, 15 to 45% by mass of glass fiber, carbon fiber, aramid fiber, or the like may be added, but resins without these fibers may also be used.
  • thermosetting resin examples include epoxy resin and phenol resin.
  • examples of the engineering plastic include polyacetal resin, polyethylene terephthalate resin, polybutylene terephthalate resin, polycarbonate resin, tetrafluoroethylene-hexafluoroethylene-hexafluoropropylene copolymer resin, tetrafluoroethylene-perfluoroalkyl vinyl ether copolymer resin, Examples include ethylene-tetrafluoroethylene copolymer resins and wholly aromatic polyester resins.
  • the super engineering plastics include polyether ether ketone resins, polyphenylene sulfide resins, polyetherimide resins, polyamideimide resins, polyethersulfone resins, thermoplastic polyimide resins, and polyamide resins (e.g. PA46, PA66, PA9T, PA10T, etc.). etc. A mixture of two or more of the above resins, a polymer alloy material, and the like can also be used.
  • each annular body 10 has a plurality of semi-cylindrical pocket wall portions 13 and a plurality of coupling plate portions 14 .
  • a plurality of pocket wall portions 13 are arranged at regular intervals in the circumferential direction and constitute the inner wall surface of the pocket 12 each holding the ball 5 .
  • the plurality of connecting plate portions 14 connect the pocket wall portions 13 adjacent to each other in the circumferential direction.
  • the connecting plate portion 14 has a mating surface 15 that comes into surface contact when the two annular bodies 10, 10 are connected.
  • a connecting claw 16 protruding in the axial direction and a connecting hole 17 into which the connecting claw 16 of the other annular body 10 is inserted are formed near the center in the circumferential direction of the mating surface 15 of the connecting plate portion 14 .
  • a hook portion 19 is formed at the axial tip of the coupling claw 16 , and the hook portion 19 of one annular body 10 engages with a stepped portion 18 formed on the inner surface of the coupling hole 17 of the other annular body 10 . This engagement prevents the coupling claw 16 from slipping out of the coupling hole 17, and the two annular bodies 10, 10 are overlapped and coupled to each other.
  • the coupling plate portion 14 has a projecting wall portion 20 and a housing recess portion 21 .
  • the projecting wall portion 20 is provided at one circumferential end of the mating surface 15 of one annular body 10 so as to project in the axial direction.
  • the accommodation recess 21 is provided at the other end in the circumferential direction of the mating surface 15 of one annular body 10 and accommodates the projecting wall portion 20 of the other annular body 10 . Since the coupling plate portion 14 has the projecting wall portion 20 and the accommodation recess 21 described above, the seam between the annular bodies 10, 10 when the two annular bodies 10, 10 are coupled can be positioned from the center of the pocket 12 in the axial direction. It is designed to come to a misaligned position.
  • the protruding wall portion 20 and the accommodating recess 21 are sized to create circumferential and axial gaps 22, 23 between the protruding wall portion 20 and the accommodating recess 21. ing.
  • the projecting wall portion 20 from interfering with the accommodation recess portion 21 due to the difference in shrinkage after the annular body 10 is injection molded. 15 can be brought into close contact with each other.
  • a partially concave spherical surface 25 along the outer circumference of the ball 5 is formed at both ends of each pocket 12 in the circumferential direction.
  • the partially concave spherical surfaces 25 are formed facing each other in the forward and backward direction of the ball 5 with the ball 5 interposed therebetween.
  • the radius of curvature of the partially concave spherical surface 25 is set slightly larger than the radius of the ball 5 .
  • FIG. 3B is a partially enlarged view of IIIB of FIG. 3A.
  • the retainer 6 is configured such that the pocket wall portion 13 has a band width W1, which is the radial dimension of the pocket wall portion 13, smaller than the radial dimension W2 of the coupling plate portion 14.
  • Notch portions 13a and 13b are provided on the inner diameter surface and the outer diameter surface of each.
  • the notch portions 13a and 13b on the inner diameter surface and the outer diameter surface have a curved surface shape that is a concave curve when viewed from the bearing axial direction.
  • These notches 13a and 13b are formed, for example, during injection molding of the annular body 10, but they can also be formed by machining or the like after injection molding.
  • each pocket wall portion 13 a deepest portion P1 of the notch portion 13a on the inner diameter surface is provided at a circumferential intermediate portion of the inner diameter surface, and a deepest portion P1 of the notch portion 13a is provided at a circumferential intermediate portion of the outer diameter surface.
  • a deepest portion P2 of the notch portion 13b is provided.
  • the band width W1 at the middle portion in the circumferential direction is the smallest, and the band width W1 gradually increases along the curved shape as it goes from the middle portion in the circumferential direction toward both sides in the circumferential direction. formed.
  • the radial center Pc of the band width W1 that is the minimum between the deepest portion P1 of the cutout portion 13a on the inner diameter surface and the deepest portion P2 of the cutout portion 13b on the outer diameter surface is , near the pitch circle diameter (PCD) of the ball 5 .
  • the minimum band width W1 is 20% or more and 35% or less of the diameter BD of the ball 5, and the circumferential range L1 of each of the notches 13a and 13b is 50% or more and 100% or less of the diameter BD of the ball 5.
  • the minimum band width W1 is 50% or less with respect to the radial dimension D1 between the inner diameter surface of the outer ring 3 and the outer diameter surface of the inner ring 2 .
  • the pocket wall portion 13 is formed thick by the volume reduction due to the notch portions 13a and 13b.
  • a conventional pocket wall portion 33 (Fig. 6) without cutouts is used for a synthetic resin retainer used in a deep groove ball bearing having the same inner diameter, outer diameter, and width dimensions.
  • the entire pocket wall portion 13 is thickened in the axial direction of the bearing by the volume reduction. As a result, a decrease in rigidity of the retainer 6 due to the notches 13a and 13b can be suppressed.
  • a drive shaft is rotatably supported by a housing via two rolling bearings, and a belt or the like is attached to a pulley at one end in the longitudinal direction of the drive shaft and driven by a motor to rotate around the axis. configured as possible.
  • the rolling bearing on the pulley side is the rolling bearing to be tested, and the other rolling bearing is the supporting bearing.
  • the testing machine is equipped with a preload spring or the like for applying a predetermined axial load to the rolling bearing to be tested.
  • a high-speed test was performed on a rolling bearing provided with a plurality of retainers having different melting points among the retainers according to the present embodiment.
  • the testing machine is substantially the same as the testing machine for the acoustic test described above.
  • Model number (nominal number) of rolling bearing to be tested 6312 Rotation speed: 13500min -1
  • Judgment method Visual judgment after stopping rotation after a predetermined time has passed
  • the stationary space is widened.
  • the notches 33a are provided only on the inner diameter surface of the pocket wall 33 (Fig. 9), or the pocket walls 33 are not provided with notches (Fig. 7).
  • Quiescent space volume increases.
  • the notch portion 13b on the outer diameter surface of the pocket wall portion 13
  • the amount of grease retained in the stationary space on the inner diameter side of the outer ring is increased. Therefore, it is possible to improve the lubrication life without providing a circumferential groove-shaped grease pocket or the like on the inner diameter surface of the outer ring 3 . Therefore, the manufacturing cost can be reduced as compared with the conventional structure (FIG. 8) in which the grease pocket 31b is provided on the inner diameter surface of the outer ring.
  • the retainer 6 may be made of a resin material having a melting point of 200 to 350.degree. In this case, no abnormal sliding marks are observed on the retainer 6, which is preferable.
  • a resin material having a melting point of less than 200° C. is melted or abnormally worn due to frictional heat generated by sliding between the ball 5 and the pocket wall portion 13 .
  • a resin material having a melting point exceeding 350° C. increases manufacturing costs.
  • the ball 5 is a ceramic ball, for example, it is possible to increase the speed of the rolling bearing 1 and improve the heat resistance by making the specific gravity smaller than that of a steel ball made of bearing steel or the like.
  • This rolling bearing is used, for example, as rolling bearings 50, 50 for a motor 51, which is schematically shown in FIG. However, it is also possible to apply this rolling bearing to applications other than motors. If the rolling bearing is a rolling bearing for motors, and if this rolling bearing for motors can reduce vibration, improve lubrication life, and reduce manufacturing costs, it can be applied to motors for various purposes. Versatility as a rolling bearing can be enhanced.
  • each annular body is not limited to a semi-cylindrical shape, and may be semi-spherical.
  • the seal may be a contact seal with a lip contacting the inner ring seal groove.
  • the seal may be a so-called shield plate made only of steel plates. It may be an open rolling bearing without seals. Any rolling bearing can be applied to machine tools, industrial machines, vehicles, and the like. It is also possible to form each annulus by 3D printing or machining.
  • the band width of the retainer is set to 50% of the radial dimension between the inner diameter surface of the outer ring and the outer diameter surface of the inner ring.
  • the following may be used.
  • the configuration is the same as that of the above-described embodiment. Also in this case, the same effects as those described above are obtained.
  • the rolling bearing according to this reference proposal is described as follows.
  • Each annular body includes a plurality of pocket wall portions arranged at regular intervals in the circumferential direction, each forming an inner wall surface of the pocket, and a plurality of connecting plate portions connecting the pocket wall portions adjacent in the circumferential direction.
  • the retainer has cutout portions on the inner diameter surface and the outer diameter surface of the pocket wall portion so that the band width, which is the radial dimension of the pocket wall portion, is smaller than the radial dimension of the coupling plate portion.
  • each pocket wall In each pocket wall, the center in the radial direction of the band width between the deepest part of the notch on the inner diameter surface and the deepest part of the notch on the outer diameter surface is near the pitch circle diameter of the ball,
  • the band width of the retainer is 50% or less of the radial dimension between the inner diameter surface of the outer ring and the outer diameter surface of the inner ring, and the circumferential range of each of the cutouts is the diameter of the ball. 50 to 100% of the rolling bearing.

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

Abstract

Une cage (6) comprend deux corps annulaires (10) se chevauchant mutuellement dans la direction axiale. Chaque corps annulaire (10) présente une pluralité de parties de paroi de poche (13) et une pluralité de parties de plaque de liaison (14). La cage (6) est dotée de parties découpées (13a, 13b) dans une surface de diamètre interne et une surface de diamètre externe de la partie de paroi de poche (13) de sorte qu'une largeur de bande (W1) ou une dimension radiale de la partie de paroi de poche (13) est inférieure à une dimension radiale (W2) de la partie de plaque de liaison (14). Dans chaque partie de paroi de poche, le centre radial de la largeur de bande (W1) entre une partie la plus profonde (P1) de la partie découpée (13a) dans la surface de diamètre interne et une partie la plus profonde (P2) de la partie découpée (13b) dans la surface de diamètre externe est définie à proximité du diamètre de cercle primitif d'une bille (5). La largeur de bande (W1) est fixée à 35 % ou moins d'un diamètre (BD) de la bille (5), et une plage circonférentielle (L1) de chacune des parties découpées (13a, 13b) est fixée à 50-100 % du diamètre (BD) de la bille (5).
PCT/JP2022/008113 2021-03-05 2022-02-28 Palier à roulement et cage pour palier à roulement WO2022186094A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2021035427A JP2022135543A (ja) 2021-03-05 2021-03-05 転がり軸受および転がり軸受用保持器
JP2021-035427 2021-03-05

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WO2022186094A1 true WO2022186094A1 (fr) 2022-09-09

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PCT/JP2022/008113 WO2022186094A1 (fr) 2021-03-05 2022-02-28 Palier à roulement et cage pour palier à roulement

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WO (1) WO2022186094A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006322564A (ja) * 2005-05-20 2006-11-30 Ozak Seiko Co Ltd ベアリング
JP2007040421A (ja) * 2005-08-03 2007-02-15 Nsk Ltd 転がり軸受用保持器
JP2009174605A (ja) * 2008-01-23 2009-08-06 Ntn Corp 玉軸受用波形保持器および深溝玉軸受
JP2015017710A (ja) * 2014-10-30 2015-01-29 Ntn株式会社 合成樹脂製保持器および玉軸受
WO2019009069A1 (fr) * 2017-07-04 2019-01-10 Ａｇｃ株式会社 Bille de verre

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006322564A (ja) * 2005-05-20 2006-11-30 Ozak Seiko Co Ltd ベアリング
JP2007040421A (ja) * 2005-08-03 2007-02-15 Nsk Ltd 転がり軸受用保持器
JP2009174605A (ja) * 2008-01-23 2009-08-06 Ntn Corp 玉軸受用波形保持器および深溝玉軸受
JP2015017710A (ja) * 2014-10-30 2015-01-29 Ntn株式会社 合成樹脂製保持器および玉軸受
WO2019009069A1 (fr) * 2017-07-04 2019-01-10 Ａｇｃ株式会社 Bille de verre

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