WO2016052232A1 - Cage de roulement à billes - Google Patents

Cage de roulement à billes Download PDF

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Publication number
WO2016052232A1
WO2016052232A1 PCT/JP2015/076505 JP2015076505W WO2016052232A1 WO 2016052232 A1 WO2016052232 A1 WO 2016052232A1 JP 2015076505 W JP2015076505 W JP 2015076505W WO 2016052232 A1 WO2016052232 A1 WO 2016052232A1
Authority
WO
WIPO (PCT)
Prior art keywords
ball
ball bearing
bearing retainer
annular
cage
Prior art date
Application number
PCT/JP2015/076505
Other languages
English (en)
Japanese (ja)
Inventor
和香奈 井上
峰夫 古山
Original Assignee
Ntn株式会社
和香奈 井上
峰夫 古山
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2015012108A external-priority patent/JP6556454B2/ja
Application filed by Ntn株式会社, 和香奈 井上, 峰夫 古山 filed Critical Ntn株式会社
Priority to KR1020177007617A priority Critical patent/KR102445802B1/ko
Priority to EP15847007.0A priority patent/EP3203099B1/fr
Priority to CN201580052373.6A priority patent/CN107076206B/zh
Publication of WO2016052232A1 publication Critical patent/WO2016052232A1/fr
Priority to US15/463,541 priority patent/US10663001B2/en

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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
    • 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
    • F16C33/3837—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages
    • F16C33/3843—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
    • F16C33/3856—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages made from plastic, e.g. injection moulded window 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
    • F16C33/38—Ball cages
    • F16C33/3887—Details of individual pockets, e.g. shape or ball retaining means
    • 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

  • This invention relates to a ball bearing retainer used for a machine tool spindle, for example.
  • Angular contact ball bearings used for machine tool spindles have a high rotational speed, so there are few metal cages with heavy specific gravity. Resins such as nylon polyamide, PPS, PEEK or phenol reinforced with glass fiber or carbon fiber. A cage is used.
  • Patent Documents 1 to 3 disclose a ball guide angular contact ball bearing of an inner diameter restraint type.
  • Patent Document 3 discloses an inner diameter restraint type ball guide holder.
  • an outer diameter constraint type roller guide cage has also been proposed (Patent Document 4).
  • the rolling element guide cage is a guide (contact) with a ball that is controlled with high precision and fine surface roughness. Unlike the inner ring guide cage and outer ring guide cage, the rolling element guide cage has an inner ring outer diameter surface and an inner ring outer diameter surface. There is no need for a ground finish. Therefore, the rolling element guide retainer is superior in cost compared to the inner ring guide retainer and the outer ring guide retainer.
  • FIG. 8 is a cross-sectional view of an angular ball bearing using a conventional ball bearing cage
  • FIG. 9 is a perspective view of the ball bearing cage
  • FIG. 10 is the ball bearing cage. It is the top view seen from the outer diameter side.
  • the conventional inner diameter constrained rolling element guide retainer 30 is formed with a circular pocket Pt as viewed from the radially outer side. That is, the pocket Pt has a substantially cylindrical shape.
  • 11 is a cross-sectional view taken along line XI-XI in FIG.
  • An object of the present invention is to provide a ball bearing cage capable of high-speed operation while being in a ball guide type.
  • a ball bearing retainer holds balls interposed between inner and outer rings in pockets provided at a plurality of locations in the circumferential direction of the annular portion, and the annular portions are disposed on both axial sides.
  • a ball having an annular portion and pillar portions arranged at a plurality of locations in the circumferential direction connecting the annular portions, and the pocket being formed by the annular portions on both sides in the axial direction and the pillar portions adjacent in the circumferential direction.
  • the contact portion in the circumferential direction with the ball in each pillar portion is a plane extending along the axial direction, compared to the circular hole contact portion of the conventional inner diameter restraint type rolling element guide retainer
  • the contact area with the ball can be reduced.
  • fever in the said contact part can be suppressed. Therefore, the ball bearing cage of the present application can be operated at high speed because heat generation of the ball and the contact portion can be suppressed even when centrifugal force is applied during high speed operation.
  • it is a ball guide it is not necessary to grind the inner ring outer diameter surface or the inner ring outer diameter surface, so that the number of processing steps can be reduced.
  • each annular portion with the ball may be a plane extending along the circumferential direction, and the ball may be guided on this plane.
  • the load when the ball contacts the pocket is divided into the load acting in the bearing rotation direction and the load acting in the axial direction. Can be made. Therefore, it is possible to reduce the contact area with the ball as compared with the conventional inner diameter restraint type cage and to suppress local heat generation at the contact portion.
  • the connecting portion between the column portion and the annular portion may be formed in an R shape or an arc shape.
  • a space for lubrication is formed between the R-shaped or arc-shaped connecting portion and the ball.
  • the “space” is formed, so that smooth oil supply / discharge is possible, and an appropriate amount of oil is always supplied to the contact portion between the ball and the cage pocket.
  • the “space” contributes to holding the grease in the vicinity of the contact portion, and the grease held in the “space” is supplied to the balls and the cage pocket. As a result, lubrication reliability during high-speed operation is improved, and friction and wear due to contact are suppressed.
  • the connecting portion between the column portion and the annular portion is formed in an arc shape, and the arc-shaped portion of the connecting portion is an arc surface offset from the center of the pocket, and the arc surface and the ball are between A gap may be formed.
  • a gap for lubrication is formed between the arc-shaped connecting portion and the ball.
  • the “gap” is formed, so that smooth oil supply / discharge is possible, and an appropriate amount of oil is always supplied to the contact portion between the ball and the cage pocket.
  • the “gap” contributes to holding the grease in the vicinity of the contact portion, and the grease held in the “gap” is supplied to the balls and the cage pocket. As a result, lubrication reliability during high-speed operation is improved, and friction and wear due to contact are suppressed.
  • the radial dimension of the connecting portion may be 15% or more with respect to the total axial width of the pocket.
  • the radial dimension of the connecting portion is determined based on, for example, results of tests and simulations.
  • the ball bearing cage of the present invention may be an angular ball bearing cage or a resin.
  • the resin ball bearing cage may be manufactured by injection molding. In this case, it is excellent in mass productivity and cost reduction as compared with manufacturing the cage by machining.
  • the annular portion may include two annular bodies facing each other in the axial direction of the annular portion, and the annular bodies may be combined to face the axial direction to form a plurality of pockets. .
  • the cage can be easily assembled by combining two annular bodies from both sides in the axial direction.
  • this cage is made of resin and the two annular bodies have the same shape, the two annular bodies can be molded with one type of molding die, so that the cost of the cage can be reduced while suppressing the cost of the mold, There is no need to separate the two annular bodies to be combined, and the management of the annular bodies is easy.
  • the ball bearing of the present invention may be an angular ball bearing for a machine tool spindle using the ball bearing retainer of the present invention.
  • FIG. 9 is a sectional view taken along line XI-XI in FIG. 8.
  • FIG. 1 is a cross-sectional view of an angular ball bearing using a ball bearing cage.
  • a ball 4 held by a cage 3 is interposed between an inner ring 1 and an outer ring 2.
  • the cage 3 is a ball guide and is an inner diameter restraint type.
  • the ball 4 is made of, for example, a steel ball or ceramics.
  • the cage 3 holds the balls 4 interposed between the inner and outer rings 1 and 2 in pockets Pt provided at a plurality of locations in the circumferential direction of the annular portion 5.
  • the cage 3 is made of resin, for example, and is manufactured by injection molding.
  • Resin materials used for the cage 3 include 20-40% carbon fiber or glass fiber in super engineer plastic represented by high-rigidity PEEK resin, which is advantageous for high-speed rotation, and cost considerations Engineered plastics typified by polyamide resin containing 20 to 40% carbon fiber or glass fiber are applied.
  • FIG. 2A is a perspective view of the cage 3, and FIG. 2B is an enlarged view of the main part of FIG. 2A.
  • FIG. 3A is a plan view of the cage 3 as viewed from the outer diameter side, and FIG. 3B is an enlarged view of the main part of FIG. 3A.
  • the annular portion 5 of the cage 3 is arranged at a plurality of locations in the circumferential direction by connecting the annular portions 6 and 6 disposed on both sides in the axial direction and connecting these annular portions 6 and 6.
  • the column part 7 is provided.
  • the pockets Pt are formed by the annular portions 6 and 6 on both sides in the axial direction and the column portions 7 and 7 adjacent in the circumferential direction.
  • the pocket Pt is formed in a substantially rectangular shape in a plan view when the cage 3 is viewed from the outer diameter side.
  • a pair of pillar parts 7 and 7 are arrange
  • a contact portion of each column portion 7 with the ball 4 (FIG. 1) is a plane 8 extending along the axial direction.
  • the ball 4 (FIG. 1) is guided by the plane 8.
  • the plane 8 in the column portion 7 is referred to as “rotation direction straight surface 8”.
  • each rotation direction straight surface 8 and 8 in each pocket Pt extend a predetermined distance inward in the radial direction from the middle portion in the thickness direction of each column portion 7 and gradually approach each other in the circumferential direction toward the tip. It is provided as follows. Moreover, each rotation direction straight surface 8 is formed so that it becomes narrow as it goes to a front-end
  • the cage 3 is a ball guide inner diameter restraint type by the rotation direction straight surface 8 in the column portion 7.
  • each annular portion 6 The contact portion in the axial direction of each annular portion 6 is a plane 9 extending along the circumferential direction, and the ball 4 (FIG. 1) is guided also on this plane 9.
  • the plane 9 in the annular portion 6 is referred to as “axial straight surface 9”.
  • Two axial straight surfaces 9, 9 in each pocket Pt are formed in parallel to each other. Since the ball 4 (FIG. 1) is guided by the aforementioned rotational straight surface 8 and the axial straight surface 9, the load when the ball 4 (FIG. 1) contacts the pocket Pt acts in the bearing rotational direction. The load and the load acting in the axial direction can be shared.
  • the connecting portion 10 between the column portion 7 and the annular portion 6 is formed in an R shape or a circular arc shape formed by round chamfering.
  • the R-shaped or arc-shaped arc center is located in the pocket Pt.
  • Connecting portions 10 are formed at the four corners of each pocket Pt formed in a substantially rectangular shape.
  • the radius of the connecting portion 10 is 15% or more of the total axial width L1 of the pocket Pt.
  • the radial dimension of the connecting portion 10 is determined by the results of tests and simulations, for example.
  • FIG. 4 is a diagram illustrating a comparison between the cage 3 (right side of the figure) and the conventional cage 50 (left side of the figure) of the present embodiment.
  • the ball 4 contacts the circular hole surface 51 of the pocket Pt, whereas in the cage 3 of the present embodiment, the ball 4 contacts the rotational direction straight surface 8 of the pocket Pt.
  • a space 11 for lubrication is formed between the R-shaped or arc-shaped connecting portion 10 and the ball 4.
  • the formation of the space 11 enables smooth supply and discharge of oil, and an appropriate amount of oil is always supplied to the contact portion between the ball 4 and the cage pocket Pt.
  • the space 11 contributes to holding the grease near the contact portion, and the grease held in the space 11 is supplied to the balls 4 and the cage pocket Pt. As a result, lubrication reliability during high-speed operation is improved, and friction and wear due to contact are suppressed.
  • the contact portion in the circumferential direction of each pillar portion 7 with the ball 4 is a plane 8 extending along the axial direction.
  • bowl 4 can be decreased compared with the circular hole contact part which the conventional inner diameter restraint type rolling element guide retainer has.
  • the ball bearing retainer 3 of this embodiment can suppress the heat generation of the ball 4 and the contact portion even when centrifugal force is applied during high speed operation, and high speed operation is possible.
  • it is a ball guide, it is not necessary to finish the inner ring outer diameter surface or the inner ring outer diameter surface, so that the number of processing steps can be reduced.
  • each annular portion 6 with the ball 4 is a plane 9 extending along the circumferential direction, and the ball 4 is guided by this plane 9. Since the ball 4 is guided by the plane 8 of the column portion 7 and the plane 9 of the annular portion 6, the load when the ball 4 comes into contact with the pocket Pt is applied to the load acting in the bearing rotation direction and the axial direction. It can be shared with the load to be performed. Therefore, it is possible to reduce the contact area with the ball as compared with the conventional inner diameter restraint type cage and to suppress local heat generation at the contact portion.
  • the connecting portion 10 between the column portion 7 and the annular portion 6 is formed in an arc shape.
  • the arcuate portion of the connecting portion 10 is an arc surface offset in the axial direction and the circumferential direction from the center O1 of the pocket Pt, and a gap is formed between the arc surface and the ball.
  • the arcuate portion of the connecting portion 10 is an arc surface offset in the axial direction from the center O1 of the pocket Pt, and a gap is formed between the arc surface and the ball. ing.
  • a gap for lubrication is formed between the arc-shaped connecting portion 10 and the ball.
  • air-oil lubrication the formation of this “gap” enables smooth oil supply / discharge, and an appropriate amount of oil is always supplied to the contact portion between the ball and the cage pocket Pt.
  • this gap contributes to holding the grease in the vicinity of the contact portion, and the grease held in the gap is supplied to the ball and the cage pocket Pt. As a result, lubrication reliability during high-speed operation is improved, and friction and wear due to contact are suppressed.
  • the annular portion 5 of the cage 3 ⁇ / b> A has two annular bodies 12, 12 that can be divided in the axial direction, and by combining these two annular bodies 12, 12, A cage 3A having a plurality of pockets Pt is formed.
  • the two annular bodies 12, 12 of the fourth embodiment have the same shape and are combined in the opposite directions.
  • the column portion 7 is formed with a mating surface 13 that comes into surface contact when the two annular bodies 12 and 12 are combined.
  • the mating surface 13 is a plane perpendicular to the axial direction except for the central portion in the circumferential direction of each column portion 7.
  • the mating surface 13 is formed at a position shifted in the axial direction from the center in the axial direction of the annular portion 5.
  • the annular portion 5 having a plurality of pockets Pt is configured by combining the two annular bodies 12 and 12 that can be divided in the axial direction so as to face each other in the axial direction. For this reason, after inserting a plurality of balls 4 (FIG. 1) between the raceway surfaces of the inner and outer rings 1 and 2 (FIG. 1), the two annular bodies 12 and 12 are combined from both sides in the axial direction. 3A can be assembled easily.
  • the cage 3A is made of resin and the two annular bodies 12 and 12 have the same shape, the two annular bodies 12 and 12 can be molded with one type of molding die. For this reason, it is possible to reduce the cost of the retainer 3A by suppressing the mold cost, and it is not necessary to separate the two annular bodies 12 and 12 to be combined, and the management of the annular body 12 is easy.

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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 une cage de roulement à billes (3) qui maintient des billes entre des bagues interne et externe dans des poches (Pt) agencées à des emplacements multiples dans la direction circonférentielle d'une partie bague circulaire (5). La partie bague circulaire (5) comprend des sections annulaires (6, 6), et des sections de colonne (7) disposées à des emplacements multiples dans la direction circonférentielle de sorte à relier les sections annulaires (6, 6). Les poches (Pt), qui guident les billes, sont formées par les sections annulaires (6, 6) sur les deux côtés dans la direction axiale, et par des sections de colonne (7, 7) qui sont adjacentes dans la direction circonférentielle. Sur chacune des sections de colonne (7, 7), des parties circonférentielles de contact avec les billes présentent des surfaces plates (8) s'étendant le long de la direction axiale, et les billes sont guidées par ces surfaces plates (8).
PCT/JP2015/076505 2014-09-30 2015-09-17 Cage de roulement à billes WO2016052232A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
KR1020177007617A KR102445802B1 (ko) 2014-09-30 2015-09-17 볼베어링용 유지기
EP15847007.0A EP3203099B1 (fr) 2014-09-30 2015-09-17 Cage de roulement à billes
CN201580052373.6A CN107076206B (zh) 2014-09-30 2015-09-17 滚珠轴承用保持器
US15/463,541 US10663001B2 (en) 2014-09-30 2017-03-20 Ball bearing cage

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2014199923 2014-09-30
JP2014-199923 2014-09-30
JP2015012108A JP6556454B2 (ja) 2014-09-30 2015-01-26 玉軸受用保持器
JP2015-012108 2015-01-26

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US15/463,541 Continuation US10663001B2 (en) 2014-09-30 2017-03-20 Ball bearing cage

Publications (1)

Publication Number Publication Date
WO2016052232A1 true WO2016052232A1 (fr) 2016-04-07

Family

ID=55630272

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2015/076505 WO2016052232A1 (fr) 2014-09-30 2015-09-17 Cage de roulement à billes

Country Status (1)

Country Link
WO (1) WO2016052232A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU173278U1 (ru) * 2017-02-13 2017-08-21 Публичное акционерное общество "Научно-производственное объединение "Сатурн" Радиально-упорный подшипник качения
US10451112B2 (en) * 2015-11-25 2019-10-22 Schaeffler Technologies AG & Co. KG Ball bearing cage

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006161882A (ja) * 2004-12-03 2006-06-22 Ntn Corp 転がり軸受用保持器
JP2007147010A (ja) * 2005-11-29 2007-06-14 Ntn Corp 玉軸受用保持器、玉軸受および工作機械
JP2009058039A (ja) * 2007-08-31 2009-03-19 Jtekt Corp 転がり軸受用保持器

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006161882A (ja) * 2004-12-03 2006-06-22 Ntn Corp 転がり軸受用保持器
JP2007147010A (ja) * 2005-11-29 2007-06-14 Ntn Corp 玉軸受用保持器、玉軸受および工作機械
JP2009058039A (ja) * 2007-08-31 2009-03-19 Jtekt Corp 転がり軸受用保持器

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10451112B2 (en) * 2015-11-25 2019-10-22 Schaeffler Technologies AG & Co. KG Ball bearing cage
RU173278U1 (ru) * 2017-02-13 2017-08-21 Публичное акционерное общество "Научно-производственное объединение "Сатурн" Радиально-упорный подшипник качения

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