WO2023189431A1 - Roulement à billes - Google Patents

Roulement à billes Download PDF

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Publication number
WO2023189431A1
WO2023189431A1 PCT/JP2023/009355 JP2023009355W WO2023189431A1 WO 2023189431 A1 WO2023189431 A1 WO 2023189431A1 JP 2023009355 W JP2023009355 W JP 2023009355W WO 2023189431 A1 WO2023189431 A1 WO 2023189431A1
Authority
WO
WIPO (PCT)
Prior art keywords
diameter side
balls
retainer
pocket
ball bearing
Prior art date
Application number
PCT/JP2023/009355
Other languages
English (en)
Japanese (ja)
Inventor
紘哉 磯▲崎▼
孝康 田窪
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 WO2023189431A1 publication Critical patent/WO2023189431A1/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
    • 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
    • F16C33/41—Ball cages comb-shaped
    • 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

  • This invention eliminates the lack of lubricating oil in the pockets of a cage that houses balls, which are rolling elements, during high-speed rotation, and prevents heat generation and damage caused by interference between the cage and balls.
  • ball bearings that can be applied to parts, industrial machinery, and all other high-speed rotation applications.
  • a ball bearing includes an inner raceway member 1 having an inner raceway groove 1a formed on its outer periphery, an outer raceway member 2 having an outer raceway groove 2a formed on its inner periphery, and an inner raceway member 2 having an outer raceway groove 2a formed on its inner periphery. It includes a plurality of balls 3 interposed between the groove 1a and the outer raceway groove 2a, and a retainer 4 that holds the balls 3 at regular intervals.
  • a crown-shaped retainer 4 as shown in FIG. 11 may be used as the retainer 4.
  • the crown-shaped retainer 4 includes an annular base portion 4a and a plurality of pockets 5 provided on one axial end surface of the base portion 4a to rotatably hold balls 3, which are rolling elements.
  • Each pocket 5 is formed of a recess 5a provided on one end surface in the axial direction of the base portion 4a, and a pair of holding claws 5b disposed opposite to each other at an interval at the opening edge of the recess 5a.
  • the mutually opposing surfaces of the pair of holding claws 5b and the inner surface of the recess 5a continuously form one spherical concave surface.
  • Patent Document 1 discloses a ball bearing in which the balls do not come into contact with the inner circumferential end of the pocket portion that accommodates the balls even if the cage is deformed by centrifugal force.
  • the holding pawl 4b is formed into a straight column shape extending in the axial direction, so that even if the column-shaped holding pawl 4b is deformed by centrifugal force. , the ball 3 is prevented from interfering with the inner peripheral side end of the pocket that accommodates the ball 3.
  • a guide portion 4d for positioning the cage 4 by contacting the inner raceway groove 1a is provided on the inner diameter side of the column-shaped holding claw 4b, and the guide portion 4d of the cage 4 and the inner raceway groove 1a are brought into contact with each other.
  • the oil film of the inner raceway groove 1a may run out or friction may occur, leading to concerns about deterioration of the lubrication state.
  • a sufficient distance and clearance between the retainer 4 and the inner raceway groove 1a cannot be ensured, there is a concern that oil permeability may deteriorate.
  • the present invention aims to improve the lubrication performance by making it difficult for the oil film in the raceway groove to run out and friction to occur, while also making it easier for the lubricating oil to flow into the pocket that accommodates the balls, and the contact surface between the inner surface of the pocket and the balls.
  • the present invention aims to provide a ball bearing using a crown-shaped retainer that can reduce pressure and further reduce rotational torque.
  • a ball bearing according to the present invention includes an inner raceway member having an inner raceway groove formed on its outer periphery, an outer raceway member having an outer raceway groove formed on its inner periphery, and an inner raceway member having an outer raceway groove formed on its inner periphery.
  • the cage includes a plurality of balls interposed between the groove and the outer raceway groove, and a cage that holds the balls at regular intervals, and the cage includes an annular base portion and an axially aligned portion of the base portion.
  • a plurality of pockets are provided on the end surface and hold the balls in a rollable manner, and each pocket is arranged opposite to a recess provided on one end surface in the axial direction of the base portion and an opening edge of the recess at a distance from each other.
  • a ball bearing is formed from a pair of disposed retaining claws, and the mutually opposing surfaces of the pair of retaining claws and the inner surface of the recess continuously form one spherical concave surface, wherein each of the retaining claws is It is characterized by comprising an outer diameter side claw part and an inner diameter side claw part which are divided into an outer diameter side and an inner diameter side with a slit part in between.
  • the radial thickness of the outer diameter side claw portion is formed to be thicker than the radial thickness of the inner diameter side claw portion.
  • edges of the outer diameter side claw portion and the inner diameter side claw portion on the slit portion side of the inner surface of the pocket that accommodates the ball be formed into an R shape.
  • the pitch circle diameter of the pocket of the cage is set smaller than the pitch circle diameter of the balls stored in the pocket.
  • the retaining claws forming the pocket portion for storing the balls are divided into the outer diameter side and the inner diameter side with the slit portion in between, so that the retainer is inside the pocket portion. This makes it easier for lubricating oil to flow into the tank. Further, since the lubricating oil can be held in the slit portion, even under dilute lubrication conditions, the lubricating oil held in the slit portion is supplied, so that poor lubrication between the retainer and the balls is less likely to occur.
  • the holding claw by dividing the holding claw into an outer diameter side and an inner diameter side with a slit in between, it is possible to have multiple contact points between the balls and the cage, so the contact surface pressure between the balls and the cage can be increased. is dispersed and reduced, and heat generation and damage caused by interference between the retaining claw and the ball that occur during high-speed rotation can be prevented.
  • outer diameter side claw part and the inner diameter side claw part thicker in the radial direction than the inner diameter side claw part, it is possible to lubricate the inside of the pocket part of the cage. It becomes easier for oil to flow in, the contact surface pressure between the inner surface of the pocket and the ball is reduced, and the rotational torque can be further reduced.
  • the pitch diameter of the pocket smaller than the pitch diameter of the ball, the effect of supplying the lubricating oil held in the slit portion is further improved.
  • the lubricating oil on the ball surface is prevented from being scraped off. , the contact condition between the cage and balls is improved, and wear and heat generation of the cage and balls can be prevented.
  • the mass of the cage is reduced by the slit portion, so centrifugal force during high-speed rotation can be reduced and costs can be reduced.
  • FIG. 1 is a longitudinal cross-sectional view of a ball bearing according to the present invention.
  • FIG. 2 is a perspective view of a cage used in the ball bearing of FIG. 1;
  • FIG. 3 is a partially enlarged view of the retainer in FIG. 2;
  • FIG. 3 is an enlarged view showing an embodiment in which the edges of the outer diameter claw portion and the inner diameter claw portion on the slit portion side of the inner surface of the pocket that accommodates the balls are formed into an R shape.
  • FIG. 3 is an enlarged view showing an embodiment in which the edges of the outer diameter claw portion and the inner diameter claw portion on the slit portion side of the inner surface of the pocket that accommodates the balls are not rounded.
  • FIG. 1 is a longitudinal cross-sectional view of a ball bearing according to the present invention.
  • FIG. 2 is a perspective view of a cage used in the ball bearing of FIG. 1;
  • FIG. 3 is a partially enlarged view of the retainer in FIG. 2;
  • FIG. 3 is an
  • FIG. 7 is a partially enlarged view showing an embodiment in which the opposing curved surfaces of the holding claw are shaped like a Gothic arch having multiple curved surfaces. It is a partially enlarged view showing an embodiment in which the pocket PCD is smaller than the ball PCD.
  • FIG. 3 is a plan view of the retainer in FIG. 2 viewed from the retaining claw side.
  • FIG. 9 is a side view of the cage shown in FIG. 2 taken along line AA in FIG. 8;
  • FIG. 2 is a longitudinal cross-sectional view of a conventional ball bearing.
  • 11 is a perspective view of a cage used in the ball bearing of FIG. 10.
  • FIG. FIG. 3 is a vertical cross-sectional view of another conventional ball bearing.
  • 13 is a partially enlarged perspective view of a cage used in the ball bearing of FIG. 12.
  • FIG. 1 shows a ball bearing 20 according to an embodiment of the present invention. Used in alternators, idler pulleys, electromagnetic clutches for car air conditioners, electric fan motors, etc.
  • the ball bearing 20 according to the embodiment shown in FIG. 1 includes an inner raceway member 21 having an inner raceway groove 21a formed on the outer circumferential surface, and an outer raceway groove 22a disposed on the outside of the inner raceway member 21, and an outer raceway groove 22a on the inner circumferential surface.
  • a retainer 24 is arranged between the inner race member 21 and the outer race member 22 and holds the balls 23 at equal intervals in the circumferential direction;
  • the main part is constituted by a seal member 26 that seals an annular space 25 formed between the member 21 and the outer raceway member 22.
  • the outer raceway member 22 is attached to a stationary member such as a housing, and the inner raceway member 21 is attached to an electric motor or a rotating shaft rotationally driven by engine output.
  • the seal member 26 is composed of an annular core metal 26a and a rubber-like member 26b that is integrally fixed to the core metal 26a. Fixed in mated state.
  • a seal groove 28 consisting of a circumferential groove is formed at a position corresponding to the inner circumference of the seal member 26, and a seal lip 26c formed at the inner circumference side end of the seal member 26 is formed at a position corresponding to the inner circumference of the seal member 26. It is in sliding contact with the seal groove 28 of 21.
  • this embodiment illustrates a type in which the inner raceway member 21 rotates
  • a type in which the inner raceway member 21 is attached to a stationary member such as a shaft and the outer raceway member 22 is attached to a rotating shaft and rotates may also be used. is also applicable.
  • the inner raceway member 21 rotates while the seal lip 26c at the tip of the seal member 26 remains in sliding contact with the outer peripheral end of the inner raceway member 21. This prevents foreign matter such as water and dust from entering the bearing, or lubricant from leaking from the inside of the bearing to the outside.
  • the cage 24 includes an annular base portion 30 and a plurality of cages provided on one end surface of the base portion 30 in the axial direction to rotatably hold balls 23, which are rolling elements. It has 31 pockets.
  • Each pocket 31 is formed of a recess 31a provided on one end surface in the axial direction of the base portion 30, and a pair of holding claws 32 disposed opposite to each other at an interval at the opening edge of the recess 31a.
  • the mutually opposing surfaces of the pair of holding claws 32 and the inner surface of the recess 31a continuously form one spherical concave surface.
  • the holding claw 32 is composed of an outer diameter claw portion 34 and an inner diameter claw portion 35, which are divided into an outer diameter side and an inner diameter side with the slit portion 33 in between.
  • the radial wall thickness of the outer diameter side claw part 34 and the inner diameter side claw part 35 is such that the outer diameter side claw part 34 is thicker than the inner diameter side claw part 35. This facilitates the flow of lubricating oil into the pockets 31 of the retainer 24, reduces the contact surface pressure between the inner surface of the pockets 31 and the balls 23, and further reduces the rotational torque.
  • the radial width of the slit portion 33 is preferably 40% or less of the radial width of the retainer 24 in order to maintain the strength of the outer diameter claw portion 34 and the inner diameter claw portion 35.
  • the shape of the opposing curved surfaces of the holding claws 32 is not a single curved surface shape in which all the center dimensions of the curved surfaces are the same, but may be a Gothic arch shape with multiple curved surfaces having multiple centers as shown in FIG. good.
  • the centers of the curved surfaces of the outer diameter claw portion 34 and the inner diameter claw portion 35 may be different.
  • the pitch circle diameter (pocket P.C.D.) of the pocket 31 of the retainer 24 and the pitch circle diameter (ball P.C.D.) of the balls 23 may be the same, but as shown in FIG. , the pocket P.C.D. of the retainer 24 may be smaller than the ball P.C.D.
  • the balls 23 are guided by the outer diameter side pawl portion 34 during non-high speed operation, and the holding pawls are guided during high speed rotation. 32 is deformed, by guiding the ball 23 by the inner diameter side claw portion 35, it is possible to prevent an increase in rotational torque due to interference between the holding claw 32 and the ball 23.
  • the radial width w1 of the outer diameter claw portion 34 and the radial width w2 of the inner diameter claw portion 35 are larger than the radial width w1 of the outer diameter claw portion 34 to which centrifugal force is applied more. It is preferable to increase the strength by making the width wider than the radial width w2 of the inner claw portion 35.
  • the radial width w3 of the slit portion 33 between the outer diameter side claw portion 34 and the inner diameter side claw portion 35 is set so that the retainer 24 is preferably 40% or less of the radial width w.
  • the minimum width in the radial direction of the slit portion 33 be at least one half of the radial width w2 of the inner claw portion 35. If the minimum width in the radial direction of the slit portion 33 is less than half of the radial width w2 of the inner claw portion 35, the radial width of the slit portion 33 will be too narrow and the lubricating oil will not flow (inflow). (sexuality) etc.
  • the radial upper end surface of the slit portion 33 may be located below the center line of the radial width w of the retainer 24, or the radial lower end surface of the slit portion 33 may be located below the center line of the radial width w of the retainer 24.
  • the center line of the radial width w of the retainer 24 may be located within the radial width of the slit portion 33 without being located above the center line of the radial width w of the retainer 24. preferable.
  • the depth of the slit portion 24d (h shown in FIG. It is desirable to make the distance deeper than the center of the pocket 31, as shown in FIGS. 3 and 9.
  • the retainer 24 used in the ball bearing 20 according to the present invention has the slit portion 33 between the outer diameter claw portion 34 and the inner diameter claw portion 35. It is possible to reduce the weight of the cage 24 compared to one without it, and the center of gravity of the cage 24 can be moved toward the back side, so that the eccentricity of the cage 24 can be lowered. Thereby, when centrifugal force acts on the holding claws 32 during high-speed rotation, the moment applied to the holding claws 32 can be reduced, and the amount of deformation of the holding claws 32 can be reduced.
  • a resin with excellent wear resistance and seizure resistance can be used, and in particular, a resin with excellent tensile elongation, tensile strength, impact resistance, abrasion resistance, lubricity, etc.
  • Polyamide resins such as PA66 (polyamide 66), PA46 (polyamide 46), PA9T (polyamide 9T), PA11 (polyamide 11) or PA6 (polyamide 6) are desirable.
  • the inner raceway member 21, the outer raceway member 22, and the balls 23 are formed of metal such as bearing steel or carburized steel.
  • the grease filled in this ball bearing 20 is a semi-solid lubricant consisting of base oil, thickener, and additives.
  • the base oil constituting the lubricating grease include mineral oils such as paraffinic mineral oil and naphthenic mineral oil, hydrocarbon synthetic oils such as polybutene, poly- ⁇ -olefin, alkylbenzene, alkylnaphthalene, and alicyclic compounds; Natural oils and fats, polyol ester oils, phosphate esters, diester oils, polyglycol oils, silicone oils, polyphenyl ether oils, alkyldiphenyl ether oils, non-hydrocarbon synthetic oils such as fluorinated oils, etc. are generally used as base oils for lubricating greases. Any conventional oil can be used without particular limitation.
  • thickeners examples include metal soap thickeners such as aluminum soap, lithium soap, sodium soap, composite lithium soap, composite calcium soap, and composite aluminum soap, and urea compounds such as diurea compounds and polyurea compounds. These thickeners may be used alone or in combination of two or more.
  • additives for lubricating greases include extreme pressure agents, amine-based and phenolic antioxidants, metal deactivators such as benzotriazole, viscosity index improvers such as polymethacrylate and polystyrene, and molybdenum disulfide. , solid lubricants such as graphite, etc. These can be added alone or in combination of two or more.
  • the retainer 24 used in the ball bearing 20 according to the present invention is of a type in which rotational motion is guided by balls 23 as rolling elements.
  • the rotational motion may be either a so-called inner ring guide type in which the rotational motion is guided by the outer diameter surface of the inner raceway member 21 or a so-called outer ring guide type in which the rotational motion is guided by the inner diameter surface of the outer raceway member 22. It is desirable that the sliding portion of the outer raceway member 22 with the retainer 24 be ground.
  • the holding claw 32 is divided into the outer diameter claw part 34 and the inner diameter claw part 35 with the slit part 33 in between, and lubricating oil can be retained in the slit part 33.
  • the weight can be reduced compared to the one without the slit part 33, and even in the ultra-high speed rotation region, lubricating oil can be retained and supplied well, the frictional resistance between the cage 24 and the balls 23 is eased, and the cage Heat generation and damage due to interference between the ball 24 and the ball 23 can be prevented, and rotational torque can be further reduced.
  • Ball bearing 21 Inner raceway member 21a Inner raceway groove 22 Outer raceway member 22a Outer raceway groove 23 Balls 24 Cage 24d Slit portion 25 Annular space 26 Seal member 30 Base portion 31 Pocket 31a Recessed portion 32 Holding claw 33 Slit portion 34 Outer diameter side Claw portion 35 Inner diameter side claw portion

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

Abstract

La présente invention concerne un roulement à billes utilisant un dispositif de retenue de type couronne, qui présente de bonnes performances de lubrification et une pression de surface de contact réduite entre une surface interne d'une cavité et une bille, et qui peut réduire davantage un couple de rotation. Ce roulement à billes comporte une cavité (31) d'un élément de retenue (24) pour stocker une bille (23), la cavité (31) étant formée par une partie de base annulaire (30), une partie évidée (31a) disposée dans la partie de base (30), et une paire de pinces de retenue (32) disposées sur un bord d'ouverture de la partie évidée (31a) de façon à être espacées l'une de l'autre et à se faire face. Chacune des pinces de retenue (32) est formée par une partie de pince côté diamètre externe (34) et une partie de pince côté diamètre interne (35) séparées sur le côté de diamètre interne et le côté de diamètre externe avec une fente (33) entre celles-ci.
PCT/JP2023/009355 2022-03-28 2023-03-10 Roulement à billes WO2023189431A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2022051077A JP2023144210A (ja) 2022-03-28 2022-03-28 玉軸受
JP2022-051077 2022-03-28

Publications (1)

Publication Number Publication Date
WO2023189431A1 true WO2023189431A1 (fr) 2023-10-05

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PCT/JP2023/009355 WO2023189431A1 (fr) 2022-03-28 2023-03-10 Roulement à billes

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JP (1) JP2023144210A (fr)
WO (1) WO2023189431A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10220480A (ja) * 1997-02-10 1998-08-21 Nippon Densan Corp ころがり軸受用転動体保持器
JP2007292093A (ja) * 2006-04-21 2007-11-08 Ntn Corp 深溝玉軸受
JP2012163172A (ja) * 2011-02-08 2012-08-30 Ntn Corp 玉軸受用保持器および玉軸受
JP2018071720A (ja) * 2016-11-01 2018-05-10 日本精工株式会社 波形保持器及び玉軸受
JP2020041605A (ja) * 2018-09-11 2020-03-19 Ntn株式会社 車輪用軸受装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10220480A (ja) * 1997-02-10 1998-08-21 Nippon Densan Corp ころがり軸受用転動体保持器
JP2007292093A (ja) * 2006-04-21 2007-11-08 Ntn Corp 深溝玉軸受
JP2012163172A (ja) * 2011-02-08 2012-08-30 Ntn Corp 玉軸受用保持器および玉軸受
JP2018071720A (ja) * 2016-11-01 2018-05-10 日本精工株式会社 波形保持器及び玉軸受
JP2020041605A (ja) * 2018-09-11 2020-03-19 Ntn株式会社 車輪用軸受装置

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JP2023144210A (ja) 2023-10-11

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