JP7535372B2 - Ball bearing cages and rolling bearings - Google Patents

Ball bearing cages and rolling bearings Download PDF

Info

Publication number
JP7535372B2
JP7535372B2 JP2019167218A JP2019167218A JP7535372B2 JP 7535372 B2 JP7535372 B2 JP 7535372B2 JP 2019167218 A JP2019167218 A JP 2019167218A JP 2019167218 A JP2019167218 A JP 2019167218A JP 7535372 B2 JP7535372 B2 JP 7535372B2
Authority
JP
Japan
Prior art keywords
ball bearing
bearing
cage
pocket wall
grease
Prior art date
Legal status (The legal status 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 status listed.)
Active
Application number
JP2019167218A
Other languages
Japanese (ja)
Other versions
JP2020159548A (en
Inventor
光 石田
直明 辻
千春 伊藤
智彦 小畑
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
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 Corp filed Critical NTN Corp
Priority to CN201980061278.0A priority Critical patent/CN112739923B/en
Priority to PCT/JP2019/036854 priority patent/WO2020059829A1/en
Priority to DE112019004733.7T priority patent/DE112019004733T5/en
Publication of JP2020159548A publication Critical patent/JP2020159548A/en
Application granted granted Critical
Publication of JP7535372B2 publication Critical patent/JP7535372B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F16C19/14—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
    • 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
    • F16C33/3837—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages
    • F16C33/3862—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages comprising two annular parts joined together
    • F16C33/3875—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages comprising two annular parts joined together made from plastic, e.g. two injection moulded parts joined by a snap fit
    • 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
    • F16C33/785—Bearing shields made of sheet metal
    • 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
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/52—Positive connections with plastic deformation, e.g. caulking or staking
    • F16C2226/54—Positive connections with plastic deformation, e.g. caulking or staking with rivets
    • 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
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/70—Positive connections with complementary interlocking parts
    • F16C2226/74—Positive connections with complementary interlocking parts with snap-fit, e.g. by clips

Landscapes

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

Description

この発明は、玉軸受用保持器および転がり軸受に関し、工作機械主軸用やモータ用等の転がり軸受の高速化およびグリースの長寿命化を図ることができる技術に関する。 This invention relates to ball bearing cages and rolling bearings, and to technology that can increase the speed of rolling bearings for machine tool spindles, motors, etc., and extend the life of grease.

玉軸受用の合成樹脂製保持器が提案されている（特許文献１）。図３６に示すように、この合成樹脂製保持器は、半球状のポケット５０を円周方向に等間隔に形成し、ポケット５０間の連結板部５１に互いに係合する結合孔５２と結合爪５３を有する。合成樹脂製保持器は、前記結合孔５２に前記結合爪５３を係合することで、二枚の同形状の環状体５４，５４を係合させた保持器である。 A synthetic resin cage for ball bearings has been proposed (Patent Document 1). As shown in Figure 36, this synthetic resin cage has hemispherical pockets 50 formed at equal intervals in the circumferential direction, and has coupling holes 52 and coupling claws 53 that engage with each other on a connecting plate portion 51 between the pockets 50. The synthetic resin cage is a cage in which two identically shaped annular bodies 54, 54 are engaged by engaging the coupling claws 53 with the coupling holes 52.

他の玉軸受用保持器として、鉄板波形保持器が提案されている（特許文献２）。図３７に示すように、この鉄板波形保持器５５は、玉５６との摩擦損失を低減するため、ポケット部５７に軸方向に貫通する貫通穴５８が形成されている。
さらに他の玉軸受用保持器として、図３９に示すように、鉄板波形保持器において、各ポケット６２のある円周方向部分の内周面６３を外径側に凹む形状とした技術が提案されている（特許文献３）。 As another ball bearing cage, a corrugated iron plate cage has been proposed (Patent Document 2). As shown in Fig. 37, this corrugated iron plate cage 55 has a through hole 58 formed in a pocket portion 57 so as to pass through in the axial direction in order to reduce friction loss with the balls 56.
As another type of retainer for ball bearings, a technology has been proposed in which, as shown in Figure 39, in a steel plate corrugated retainer, the inner surface 63 of the circumferential portion in which each pocket 62 is located is shaped to be concave toward the outer diameter side (Patent Document 3).

特開２０１３－７４６８号公報JP 2013-7468 A 特開２０１８－７１７２０号公報JP 2018-71720 A 特開２０１０－６５８１６号公報JP 2010-65816 A 特開２００７－２８５５０６号公報JP 2007-285506 A

図３８に示すように、従来の合成樹脂製の波形保持器は、ポケット部５９の帯幅Ｈ１が玉６０のピッチ円ＰＣＤを中心として、玉径Ｂｄの４０％～５０％で玉６０を保持した形状となっている。また、ポケット部５９は、外輪内径と内輪外径の間の半径方向寸法に対し、７０％～８０％の帯幅Ｈ１となっている。 As shown in Figure 38, a conventional synthetic resin wave cage has a shape in which the width H1 of the pocket portion 59 is 40% to 50% of the ball diameter Bd, centered on the pitch circle PCD of the ball 60, and holds the ball 60. In addition, the pocket portion 59 has a width H1 that is 70% to 80% of the radial dimension between the inner diameter of the outer ring and the outer diameter of the inner ring.

高速回転域ｄｎ＝６０万以上で回転すると、グリースは動空間から静止空間Ｓａへ移動し、静止空間Ｓａに保持されたままとなる。そのため、転走面にグリースが供給され難くなり、潤滑供給不足から発熱が生じ、潤滑寿命が短くなる問題がある。前記「ｄｎ」とは、軸受の内径（ｍｍ）に回転数（ｒｐｍ）を乗じた値である。
また、前記ポケット部５９の前記帯幅Ｈ１では、玉６０とポケット間、保持器背面とシール間でのグリースのせん断抵抗が高く、トルク大または発熱が問題となることがある。 When rotating at a high speed rotational speed dn = 600,000 or more, the grease moves from the moving space to the stationary space Sa and remains in the stationary space Sa. As a result, it becomes difficult to supply grease to the rolling surface, which causes heat generation due to insufficient lubrication supply and shortens the lubrication life. The above "dn" is the value obtained by multiplying the inner diameter (mm) of the bearing by the rotational speed (rpm).
Furthermore, in the band width H1 of the pocket portion 59, the shear resistance of the grease between the balls 60 and the pocket and between the back surface of the cage and the seal is high, which may cause problems such as large torque or heat generation.

さらに、従来の合成樹脂製の波形保持器（図３６）は、玉と保持器のポケット５０の内径縁との軸方向の隙間が広いため、玉の表面に付着したグリースはポケット５０の部分での掻き取りが少なく、ポケット５０とポケット５０間の結合板部５１の内径縁付近で掻き取りが多い。掻き取られたグリースは遠心力で外輪転走面へ飛ばされる為、動空間から静止空間へ排出されるまでに時間を要し、グリースの慣らしに時間がかかる。
軸受組み立て時、保持器ポケット間付近に封入されたグリースは、軸受の運転により動空間で攪拌され、玉の表面等に付着する。
この場合、玉の表面のグリースが、保持器によって掻き取られ、掻き取られたグリースが動空間である転走面の付近から、保持器５９と密閉板６２（図３８）との間等の静止空間Ｓａに排出され、ある程度排出されることで、軸受内のグリースが慣らされることになる。この後は、静止空間Ｓａのグリースの基油が徐々に転走面に供給され、軸受の発熱の少ない微量潤滑が行われることになる。前記のように玉６０に付着したグリースが前記静止空間Ｓａに移動するように慣らされるまでは、グリースの攪拌抵抗により発熱が大きく、早期に慣らすことが望まれる。 Furthermore, in a conventional synthetic resin wave cage (Figure 36), the axial gap between the balls and the inner diameter edge of the cage pocket 50 is wide, so that the grease adhering to the surface of the balls is scraped off little in the pocket 50, but mostly near the inner diameter edge of the connecting plate portion 51 between the pockets 50. The scraped off grease is blown onto the outer ring rolling surface by centrifugal force, so it takes time for it to be discharged from the dynamic space to the static space, and so it takes time for the grease to break in.
When the bearing is assembled, the grease sealed in the vicinity of the cage pockets is agitated in the dynamic space as the bearing operates, and adheres to the surfaces of the balls, etc.
In this case, the grease on the surface of the balls is scraped off by the cage, and the scraped off grease is discharged from the vicinity of the rolling surface, which is the dynamic space, into the stationary space Sa between the cage 59 and the sealing plate 62 (Fig. 38), etc., and by being discharged to a certain extent, the grease in the bearing is broken in. After this, the base oil of the grease in the stationary space Sa is gradually supplied to the rolling surface, and a small amount of lubrication that generates little heat in the bearing is performed. As described above, until the grease attached to the balls 60 is broken in to move to the stationary space Sa, heat generation is large due to the stirring resistance of the grease, so early break-in is desirable.

図３７に示す鉄板波形保持器５５では、貫通穴５８が形成されているため強度不足である。
図３９に示す鉄板波形保持器では、鉄板をプレスにより打ち抜きおよび成形加工して二枚の環状部材を製作しなければならず、製作コストが嵩む。 The steel plate wave retainer 55 shown in FIG. 37 is insufficient in strength because it has through holes 58 formed therein.
In the steel plate wave cage shown in FIG. 39, two annular members must be produced by stamping and forming a steel plate using a press, which increases the production cost.

この発明の目的は、転がり軸受の高速化およびグリースの長寿命化を図れ、グリースの慣らし時間が短縮され、また生産性に優れた玉軸受用保持器および転がり軸受を提供することである。 The object of this invention is to provide a ball bearing retainer and rolling bearing that can increase the speed of rolling bearings, extend the life of grease, shorten the break-in time for grease, and have excellent productivity.

この発明の玉軸受用保持器は、互いに軸方向に重なる二枚の合成樹脂製の環状体を有し、各環状体は、円周方向に所定の間隔で並びそれぞれが玉を保持するポケットの内壁面を構成する複数の半球状のポケット壁部と、円周方向に隣合う前記ポケット壁部同士を連結する複数の結合板部とを有し、前記二枚の環状体が、前記各結合板部で互いに重なって結合された玉軸受用保持器であって、
前記ポケット壁部の径方向寸法である帯幅が、前記結合板部の径方向寸法よりも小さくなるように、前記ポケット壁部の内径面または外径面に切り欠き部が設けられている。 The ball bearing cage of the present invention comprises two synthetic resin annular bodies overlapping each other in the axial direction, each annular body having a plurality of hemispherical pocket wall portions arranged at a predetermined interval in the circumferential direction and constituting an inner wall surface of a pocket for holding balls, and a plurality of connecting plate portions connecting adjacent pocket wall portions in the circumferential direction, the two annular bodies being overlapped and connected to each other at each of the connecting plate portions,
A notch is provided on the inner diameter surface or 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 connecting plate portion.

この構成によると、ポケット壁部の帯幅が、結合板部の径方向寸法よりも小さくなるようにポケット壁部の内径面または外径面に切り欠き部が設けられているため、軸受運転時に、静止空間に溜まったグリースが遠心力により切り欠き部から転走面へ供給される。つまり、静止空間に滞留しようとするグリースの一部が切り欠き部で掻き取られることで、グリースの基油が分離して切り欠き部から順次、保持器内、玉表面、転走面へと供給され易くなる。これにより玉軸受の発熱が抑えられ、従来技術よりもグリース寿命を延ばすことができる。またポケット壁部に切り欠き部が設けられているため、玉とポケットの間でのグリースせん断抵抗が低減され、玉軸受の低トルク化および低発熱化を図れる。
また、運転開始時においては、前記切り欠き部が設けられていることで、玉の表面に付着したグリースの掻き取り量が増え、グリースが動空間から静止空間に排出され易くなり、グリースの慣らし時間を削減することができる。
前記切り欠き部は、金型等により簡単に形成することができるため、鋼板製の波形保持器に凹み部を機械加工する従来例よりも加工コストを低減することができ、生産性に優れた玉軸受用保持器とすることができる。
前記静止空間とは、内輪と、外輪と、密閉板とで閉じられた空間のうち、軸受回転時に転動体および保持器が通過しない空間を指す。 According to this configuration, the pocket wall has a notch on the inner or outer diameter surface so that the width of the pocket wall is smaller than the radial dimension of the connecting plate. During operation of the bearing, the grease that has accumulated in the stationary space is supplied to the rolling surface from the notch by centrifugal force. In other words, a part of the grease that is about to remain in the stationary space is scraped off by the notch, so that the base oil of the grease is separated and is easily supplied from the notch to the cage, the ball surface, and the rolling surface. This suppresses heat generation in the ball bearing and extends the grease life compared to the conventional technology. In addition, the pocket wall has a notch, so the grease shear resistance between the ball and the pocket is reduced, resulting in low torque and low heat generation in the ball bearing.
In addition, at the start of operation, the provision of the cutout portion increases the amount of grease adhering to the surface of the ball that is scraped off, making it easier for the grease to be discharged from the moving space to the stationary space, thereby reducing the break-in time for the grease.
The cutout portion can be easily formed using a mold or the like, which reduces processing costs compared to the conventional example in which a recess is machined into a corrugated retainer made of steel plate, resulting in a retainer for ball bearings with excellent productivity.
The stationary space refers to a space enclosed by the inner ring, the outer ring, and the sealing plate, through which the rolling elements and the cage do not pass when the bearing rotates.

この発明において、前記切り欠き部の最深部の軸受径方向の位置が、前記玉のピッチ円付近に位置していてもよい。
前記切り欠き部の最深部が玉のピッチ円付近の径方向位置付近に達していると、玉とポケット壁部の内面との隙間が狭い箇所で切り欠き部が開口することになり、静止空間に近い場所でグリースを多くかきとることができる。そのため、グリースが動空間から排出され易くグリースの慣らし時間をより一層削減することができる。 In the present invention, the deepest part of the cutout portion in the radial direction of the bearing may be located near the pitch circle of the balls.
If the deepest part of the notch reaches the radial position near the pitch circle of the ball, the notch opens at the point where the gap between the ball and the inner surface of the pocket wall is narrow, and a large amount of grease can be scraped off in a place close to the stationary space. Therefore, the grease can be easily discharged from the moving space, and the break-in time of the grease can be further reduced.

この発明において、前記切り欠き部が前記ポケット壁部の外径側に位置し、前記結合板部の外径縁から軸方向に突出するフランジ部が設けられていてもよい。
前記フランジ部を設けることで、ポケット壁部と結合板部との繋がり部の近傍で掻き取られたグリースが遠心力で飛ばされ、動空間となる外輪転走面へ巻き込まれるのを防ぎ、グリースが動空間から静止空間へ排出されるまでの時間がさらに短縮される。 In the present invention, the cutout portion may be located on the outer diameter side of the pocket wall portion, and a flange portion may be provided that protrudes in the axial direction from the outer diameter edge of the connecting plate portion.
By providing the flange portion, the grease scraped off near the connection between the pocket wall portion and the connecting plate portion is blown away by centrifugal force, preventing it from being caught in the outer ring rolling surface which forms the dynamic space, thereby further shortening the time it takes for the grease to be discharged from the dynamic space to the static space.

前記切り欠き部は、前記ポケット壁部の内径面または外径面が軸受軸方向から見て凹曲線となる曲線形状であってもよい。この場合、ポケット壁部の切り欠き部に、局所的な応力集中が作用することを未然に防ぐことができる。また、金型等により切り欠き部を簡単に形成することが可能となる。 The cutout portion may be a curved shape in which the inner diameter surface or the outer diameter surface of the pocket wall is a concave curve when viewed from the bearing axial direction. In this case, it is possible to prevent local stress concentration from acting on the cutout portion of the pocket wall. In addition, it is possible to easily form the cutout portion using a mold or the like.

前記ポケット壁部は、前記切り欠き部による体積減少分だけ軸受軸方向に厚肉にする厚肉部を有するものであってもよい。ポケット壁部が厚肉部を有するため、切り欠き部による玉軸受用保持器の剛性低下を抑制することができる。 The pocket wall may have a thickened portion that is thickened in the axial direction of the bearing by an amount equal to the volume reduction caused by the cutout. Because the pocket wall has a thickened portion, it is possible to suppress a decrease in the rigidity of the ball bearing cage caused by the cutout.

前記互いに重なった二つの結合板部の軸方向寸法を、前記玉の直径の５５％～６５％としてもよい。
前記５５％～６５％とは、玉の直径の５５％を超え、玉の直径の６５％未満を意味する。
この構成によると、玉軸受用保持器が高剛性になり、玉軸受用保持器の固有振動数が上昇することで、回転速度との共振が発生しない。このことにより共振による玉軸受用保持器の振動も発生せず、昇温が抑制され安定した回転が得られる。この場合、結合板部の軸方向寸法を規定するだけで共振点がずれることで昇温が抑制され安定した回転が得られることから、金属部品等を用いて保持器の剛性を高めるよりもコスト低減を図ることができる。 The axial dimension of the two overlapping connecting plate portions may be 55% to 65% of the diameter of the ball.
The above 55% to 65% means more than 55% of the diameter of the ball and less than 65% of the diameter of the ball.
According to this configuration, the ball bearing cage has high rigidity, and the natural frequency of the ball bearing cage increases, so that resonance with the rotation speed does not occur. As a result, the ball bearing cage does not vibrate due to resonance, and temperature rise is suppressed, resulting in stable rotation. In this case, simply by specifying the axial dimension of the connecting plate portion, the resonance point is shifted, so that temperature rise is suppressed and stable rotation is obtained, which allows for cost reduction compared to increasing the rigidity of the cage using metal parts, etc.

この発明の転がり軸受は、前述のいずれかに記載の玉軸受用保持器を備えたものである。そのため、この発明の玉軸受用保持器につき前述した各効果が得られる。 The rolling bearing of this invention is equipped with a ball bearing retainer as described above. Therefore, the effects described above for the ball bearing retainer of this invention can be obtained.

前記玉がセラミックボールであってもよい。この場合、例えば軸受鋼等から成る鋼球よりも比重を小さくして軸受の高速化を図ることができるうえ耐熱性を高めることができる。 The balls may be ceramic balls. In this case, the specific gravity is smaller than that of steel balls made of bearing steel, for example, allowing for faster bearing speeds and improved heat resistance.

この発明の玉軸受用保持器は、互いに軸方向に重なる二枚の合成樹脂製の環状体を有し、各環状体は、円周方向に所定の間隔で並びそれぞれが玉を保持するポケットの内壁面を構成する複数の半球状のポケット壁部と、円周方向に隣合う前記ポケット壁部同士を連結する複数の結合板部とを有し、前記二枚の環状体が、前記各結合板部で互いに重なって結合された玉軸受用保持器であって、前記ポケット壁部の径方向寸法である帯幅が、前記結合板部の径方向寸法よりも小さくなるように、前記ポケット壁部の内径面または外径面に切り欠き部が設けられている。このため、転がり軸受の高速化およびグリースの長寿命化を図れ、グリースの慣らし時間が短縮され、また生産性に優れた玉軸受用保持器とすることができる。 The ball bearing cage of this invention has two synthetic resin rings overlapping each other in the axial direction, each ring having a plurality of hemispherical pocket wall sections arranged at a predetermined interval in the circumferential direction and constituting the inner wall surface of a pocket that holds balls, and a plurality of connecting plate sections connecting adjacent pocket wall sections in the circumferential direction, and the two rings are overlapped and connected to each other at each connecting plate section, and a notch is provided on the inner or outer diameter surface of the pocket wall section so that the band width, which is the radial dimension of the pocket wall section, is smaller than the radial dimension of the connecting plate section. This allows for faster rolling bearings and longer grease life, shortens the break-in time for the grease, and provides a ball bearing cage with excellent productivity.

この発明の転がり軸受は、前述のいずれかに記載の玉軸受用保持器を備えたため、転がり軸受の高速化およびグリースの長寿命化を図れ、また生産性に優れた玉軸受用保持器とすることができる。 The rolling bearing of this invention is equipped with a ball bearing retainer as described above, which allows for faster rolling bearings and longer grease life, and also makes it possible to produce a ball bearing retainer with excellent productivity.

この発明の実施形態の玉軸受用保持器を備えた転がり軸受の断面図である。1 is a cross-sectional view of a rolling bearing including a ball bearing cage according to an embodiment of the present invention. 同玉軸受用保持器の斜視図である。FIG. 2 is a perspective view of the cage for the ball bearing. 同玉軸受用保持器の厚肉部を説明するための斜視図である。4 is a perspective view for explaining a thick-walled portion of the cage for the ball bearing according to the first embodiment; FIG. 同玉軸受用保持器を軸方向から見た正面図である。FIG. 2 is a front view of the ball bearing cage as viewed from the axial direction. 同玉軸受用保持器の拡大断面図である。FIG. 2 is an enlarged cross-sectional view of the cage for the ball bearing. 図４（Ａ）のIVB-IVB線断面図である。FIG. 4B is a cross-sectional view taken along line IVB-IVB in FIG. 同玉軸受用保持器に玉と外輪を組み合わせた状態の正面図である。2 is a front view of the ball bearing cage with balls and an outer ring assembled thereto. FIG. 図５のVI-VI線で断面した一部切り欠き断面図である。6 is a partially cutaway cross-sectional view taken along line VI-VI in FIG. 5 . 同玉軸受用保持器のグリース流動解析の結果を示す説明図である。4 is an explanatory diagram showing the results of a grease flow analysis of the cage for the ball bearing according to the embodiment of the present invention. FIG. 従来の玉軸受用保持器のグリース流動解析の結果を示す説明図である。FIG. 13 is an explanatory diagram showing the results of a grease flow analysis of a conventional ball bearing cage. 同実施形態品および従来保持器のグリース慣らし性確認試験の結果を示すグラフである。13 is a graph showing the results of a grease break-in confirmation test for the product of the embodiment and a conventional cage. 各実施形態品および従来保持器の他のグリース慣らし性確認試験の結果を示すグラフである。13 is a graph showing the results of other grease break-in confirmation tests of the products of the embodiments and a conventional cage. この発明の他の実施形態に係る玉軸受用保持器の正面図である。FIG. 4 is a front view of a ball bearing cage according to another embodiment of the present invention. 同玉軸受用保持器を内径側から見た部分側面図である。FIG. 2 is a partial side view of the ball bearing cage as viewed from the inner diameter side. 同玉軸受用保持器の結合板部を示す拡大断面図である。4 is an enlarged cross-sectional view showing a connecting plate portion of the cage for the ball bearing according to the embodiment of the present invention; FIG. 同玉軸受用保持器に玉と外輪を組み合わせた状態の正面図である。2 is a front view of the ball bearing cage with balls and an outer ring assembled thereto. FIG. 図１３のXIV-XIV線で断面した一部切り欠き断面図である。14 is a partially cutaway cross-sectional view taken along line XIV-XIV in FIG. 13. この発明のさらに他の実施形態に係る玉軸受用保持器の斜視図である。FIG. 11 is a perspective view of a ball bearing cage according to still another embodiment of the present invention. 同玉軸受用保持器を軸方向から見た正面図である。FIG. 2 is a front view of the ball bearing cage as viewed from the axial direction. 図１６のXVII-XVII線断面図である。17 is a cross-sectional view taken along line XVII-XVII of FIG. 16. この発明のさらに他の実施形態に係る玉軸受用保持器の斜視図である。FIG. 11 is a perspective view of a ball bearing cage according to still another embodiment of the present invention. 同玉軸受用保持器を軸方向から見た正面図である。FIG. 2 is a front view of the ball bearing cage as viewed from the axial direction. 図１９のXX-XX線断面図である。This is a cross-sectional view taken along line XX-XX in Figure 19. この発明のさらに他の実施形態に係る玉軸受用保持器の斜視図である。FIG. 11 is a perspective view of a ball bearing cage according to still another embodiment of the present invention. 同玉軸受用保持器を軸方向から見た正面図である。FIG. 2 is a front view of the ball bearing cage as viewed from the axial direction. 図２２のXXIII－XXIII線断面図である。This is a cross-sectional view taken along line XXIII-XXIII in Figure 22. この発明のさらに他の実施形態に係る玉軸受用保持器の斜視図である。FIG. 11 is a perspective view of a ball bearing cage according to still another embodiment of the present invention. 同玉軸受用保持器を軸方向から見た正面図である。FIG. 2 is a front view of the ball bearing cage as viewed from the axial direction. 図２５のXXVI－XXVI線断面図である。This is a cross-sectional view taken along line XXVI-XXVI in Figure 25. この発明のさらに他の実施形態に係る玉軸受用保持器を備えた転がり軸受の断面図である。FIG. 11 is a cross-sectional view of a rolling bearing including a ball bearing cage according to still another embodiment of the present invention. この発明のさらに他の実施形態に係る玉軸受用保持器の斜視図である。FIG. 11 is a perspective view of a ball bearing cage according to still another embodiment of the present invention. 同玉軸受用保持器を備えた転がり軸受の断面図である。2 is a cross-sectional view of a rolling bearing including the ball bearing cage. FIG. 高速試験機の概略図である。FIG. 1 is a schematic diagram of a high-speed testing machine. 同玉軸受用保持器の昇温試験結果を示す図である。6 is a diagram showing the results of a temperature rise test of the retainer for the ball bearing. FIG. 従来品の昇温試験結果を示す図である。FIG. 13 is a diagram showing the results of a temperature rise test of a conventional product. この発明の切り欠き部形状の変形例となる実施形態に係る玉軸受用保持器の正面図である。13 is a front view of a ball bearing cage according to an embodiment of the present invention, which is a modified example of the shape of the cutout portion. FIG. この発明の他の切り欠き部形状の変形例となる実施形態に係る玉軸受用保持器の正面図である。FIG. 11 is a front view of a ball bearing cage according to an embodiment of the present invention, which is a modified example of a cutout portion shape. この発明のさらに他の切り欠き部形状の変形例となる実施形態に係る玉軸受用保持器の正面図である。FIG. 11 is a front view of a ball bearing cage according to another embodiment of the present invention, in which the shape of the cutout portion is modified. 従来例の合成樹脂製保持器の斜視図である。FIG. 11 is a perspective view of a conventional synthetic resin cage. 従来例の鉄板波形保持器の斜視図である。FIG. 1 is a perspective view of a conventional steel plate wave cage. 従来例の転がり軸受の断面図である。FIG. 1 is a cross-sectional view of a conventional rolling bearing. 従来例の鉄板波形保持器の一部を示す部分拡大斜視図である。FIG. 13 is a partially enlarged perspective view showing a part of a conventional steel plate wave cage.

［第１の実施形態］
この発明の第１の実施形態に係る玉軸受用保持器および転がり軸受を図１ないし図９
と共に説明する。
＜転がり軸受について＞
図１に示すように、この転がり軸受１は、深溝玉軸受であって、内輪２と、外輪３と、内外輪２，３の転走面２ａ，３ａ間に介在する複数の玉５と、各玉５を保持する玉軸受用保持器６と、非接触シールである密閉板４とを備えている。玉５は、鋼球またはセラミックボールである。 [First embodiment]
A ball bearing cage and a rolling bearing according to a first embodiment of the present invention are shown in FIGS. 1 to 9.
will be explained together.
<About rolling bearings>
1, this rolling bearing 1 is a deep groove ball bearing that includes an inner ring 2, an outer ring 3, a plurality of balls 5 interposed between the rolling surfaces 2a, 3a of the inner and outer rings 2, 3, a ball bearing cage 6 that holds the balls 5, and a sealing plate 4 that is a non-contact seal. The balls 5 are steel balls or ceramic balls.

内輪２の外周と外輪３の内周間に環状空間が形成され、この環状空間の軸方向両端の開口が密閉板４，４により閉鎖されている。閉鎖された環状空間に潤滑用のグリースが封入されている。外輪３の内周面に外輪シール溝が形成され、内輪２の外周面に内輪シール溝が形成されている。密閉板４は、鋼板等から円板状に形成される。密閉板４の外端が外輪シール溝に取付けられ、密閉板４の内端が内輪シール溝に所定の隙間を隔てて挿入されて内輪２に対して非接触とされている。 An annular space is formed between the outer circumference of the inner ring 2 and the inner circumference of the outer ring 3, and the openings at both axial ends of this annular space are closed by sealing plates 4, 4. Lubricating grease is sealed in the closed annular space. An outer ring seal groove is formed on the inner peripheral surface of the outer ring 3, and an inner ring seal groove is formed on the outer peripheral surface of the inner ring 2. The sealing plate 4 is formed into a disk shape from a steel plate or the like. The outer end of the sealing plate 4 is attached to the outer ring seal groove, and the inner end of the sealing plate 4 is inserted into the inner ring seal groove with a specified gap between them, so that it does not come into contact with the inner ring 2.

＜玉軸受用保持器６について＞
図２Ａ，図２Ｂおよび図３に示すように、玉軸受用保持器６は、互いに軸方向に重なる二枚の合成樹脂製の環状体１０，１０を有する。各環状体１０は、合成樹脂を例えば射出成形して形成される。二枚の環状体１０，１０は、同一形状であり同一の金型で成形可能である。前記合成樹脂としては、例えば、ポリアミド（例えばＰＡ４６）、ポリフェニレンサルファイド（ＰＰＳ）、ポリエーテルエーテルケトン（ＰＥＥＫ）等を採用し得る。各環状体１０を形成する合成樹脂には、強度を高めるために、ガラス繊維またはカーボン繊維またはアラミド繊維等が添加されている。 <Regarding ball bearing cage 6>
As shown in Figures 2A, 2B and 3, the ball bearing cage 6 has two synthetic resin annular bodies 10, 10 that overlap each other in the axial direction. 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 using the same mold. As the synthetic resin, for example, polyamide (e.g., PA46), polyphenylene sulfide (PPS), polyether ether ketone (PEEK), etc. can be used. The synthetic resin forming each annular body 10 is added with glass fiber, carbon fiber, aramid fiber, etc. to increase its strength.

図４Ａ，図４Ｂに示すように、各環状体１０は、複数の半球状のポケット壁部１３と、複数の結合板部１４とを有する。複数の半球状のポケット壁部１３は、円周方向に一定の間隔で並びそれぞれが玉５を保持するポケット１２の内壁面を構成する。複数の結合板部１４は、円周方向に隣合うポケット壁部１３同士を連結する。 As shown in Figures 4A and 4B, each annular body 10 has multiple hemispherical pocket wall portions 13 and multiple connecting plate portions 14. The multiple hemispherical pocket wall portions 13 are arranged at regular intervals in the circumferential direction and each constitutes the inner wall surface of a pocket 12 that holds a ball 5. The multiple connecting plate portions 14 connect adjacent pocket wall portions 13 in the circumferential direction.

＜結合爪１６および結合孔１７について＞
結合板部１４は、二枚の環状体１０，１０を結合したときに面接触する合わせ面１５を有する。結合板部１４における合わせ面１５の中央付近には、軸方向に突出する結合爪１６と、他方の環状体１０の結合爪１６が挿入される結合孔１７とが形成されている。
結合爪１６の軸方向先端部に鉤部１９が形成され、一方の環状体１０の鉤部１９は、他方の環状体１０の結合孔１７の内面に形成された段部１８に係合する。この係合により結合爪１６が結合孔１７から抜け止めされ、二枚の環状体１０，１０が互いに結合される。 <Regarding the coupling claws 16 and coupling holes 17>
The connecting plate portion 14 has a mating surface 15 that comes into surface contact when the two annular bodies 10, 10 are connected together. Near the center of the mating surface 15 of the connecting plate portion 14, a connecting claw 16 that protrudes 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.
A hook 19 is formed at the axial tip of the connecting claw 16, and the hook 19 of one annular body 10 engages with a step 18 formed on the inner surface of the connecting hole 17 of the other annular body 10. This engagement prevents the connecting claw 16 from slipping out of the connecting hole 17, and the two annular bodies 10, 10 are connected to each other.

＜突出壁部２０および収容凹部２１について＞
結合板部１４は、突出壁部２０および収容凹部２１を有する。突出壁部２０は、一方の環状体１０の合わせ面１５における円周方向一端に、軸方向に突出するように設けられている。収容凹部２１は、一方の環状体１０の合わせ面１５における円周方向他端に設けられ、他方の環状体１０の突出壁部２０を収容する。 <Regarding the protruding wall portion 20 and the accommodation recess 21>
The connecting plate portion 14 has a protruding wall portion 20 and an accommodating recess 21. The protruding wall portion 20 is provided at one circumferential end of the mating surface 15 of one annular body 10 so as to protrude in the axial direction. The accommodating recess 21 is provided at the other circumferential end of the mating surface 15 of one annular body 10 and accommodates the protruding wall portion 20 of the other annular body 10.

結合板部１４が前述の突出壁部２０および収容凹部２１を有することによって、二枚の環状体１０，１０を結合したときの環状体１０，１０の合わせ目が、ポケット１２の軸方向中央からずれた位置にくるようになっている。これにより、軸受運転時、玉５の遅れまたは進みにより玉５が結合板部１４に接触するとき、二枚の環状体１０，１０の合わせ目の位置に玉５が接触することを防止し得る。したがって、玉５を安定して保持することが可能となる。 By having the connecting plate portion 14 have the protruding wall portion 20 and the accommodating recess 21 described above, the seam of the two annular bodies 10, 10 when they are connected is located at a position offset from the axial center of the pocket 12. This makes it possible to prevent the balls 5 from contacting the connecting plate portion 14 due to a delay or advance of the balls 5 during bearing operation at the position of the seam of the two annular bodies 10, 10. Therefore, it becomes possible to hold the balls 5 stably.

二枚の環状体１０，１０を結合した状態において、突出壁部２０および収容凹部２１は、突出壁部２０と収容凹部２１の間に周方向および軸方向の隙間２２，２３が生じる大きさとされている。これにより、環状体１０を射出成形した後の収縮差により突出壁部２０と収容凹部２１が干渉するのを防止することができ、二枚の環状体１０，１０の結合板部１４における合わせ面１５同士を確実に密着させ得る。 When the two annular bodies 10, 10 are joined together, the protruding wall portion 20 and the accommodating recess 21 are sized to leave circumferential and axial gaps 22, 23 between the protruding wall portion 20 and the accommodating recess 21. This prevents interference between the protruding wall portion 20 and the accommodating recess 21 due to differential shrinkage after injection molding of the annular body 10, and ensures that the mating surfaces 15 of the joining plate portions 14 of the two annular bodies 10, 10 are tightly attached to each other.

各ポケット１２の円周方向両端部には、玉５の外周に沿う部分凹球面２５がそれぞれ形成されている。部分凹球面２５は、玉５のピッチ円と直交する領域をもつ部分凹球面であり、玉５を間に挟んで玉５の進行方向の前後に対向して形成されている。部分凹球面２５の曲率半径は玉５の半径よりも僅かに大きく設定されている。 A partial concave spherical surface 25 is formed on both circumferential ends of each pocket 12, following the outer circumference of the ball 5. The partial concave spherical surfaces 25 are partial concave spherical surfaces with an area perpendicular to the pitch circle of the ball 5, and are formed facing each other at the front and rear of the ball 5 in the direction of travel, sandwiching the ball 5 therebetween. The radius of curvature of the partial concave spherical surfaces 25 is set slightly larger than the radius of the ball 5.

＜切り欠き部７について＞
図２Ａおよび図３に示すように、ポケット壁部１３の内径面に、静止空間Ｓａ（図１）から転走面２ａ，３ａ（図１）へのグリース供給をし易くする切り欠き部７が設けられている。この切り欠き部７は、例えば、環状体１０の射出成形時に形成されるが、射出成形後の追加工によって形成することも可能である。切り欠き部７は、ポケット壁部１３の径方向寸法である帯幅Ｈ１が、結合板部１４の径方向寸法Ｈ２（図３）よりも小さくなるように形成されている。この実施形態おいて、ポケット壁部１３の内径面１３ａは、軸受軸方向から見て凹曲線となる曲面形状である。切り欠き部７は、ポケット壁部１３の円周方向中間部の帯幅Ｈ１が最も小さく、前記円周方向中間部から円周方向両側に向かうに従って帯幅Ｈ１が前記曲面形状に沿って次第に大きくなるように形成されている。 <Regarding the cutout portion 7>
As shown in Fig. 2A and Fig. 3, the pocket wall 13 has an inner diameter surface provided with a notch 7 for facilitating the supply of grease from the stationary space Sa (Fig. 1) to the rolling surfaces 2a, 3a (Fig. 1). The notch 7 is formed, for example, during the injection molding of the annular body 10, but can also be formed by additional processing after the injection molding. The notch 7 is formed so that the width H1, which is the radial dimension of the pocket wall 13, is smaller than the radial dimension H2 (Fig. 3) of the connecting plate 14. In this embodiment, the inner diameter surface 13a of the pocket wall 13 has a curved shape that is a concave curve when viewed from the bearing axial direction. The notch 7 is formed so that the width H1 is smallest at the circumferential middle part of the pocket wall 13, and the width H1 gradually increases along the curved shape from the circumferential middle part toward both sides in the circumferential direction.

具体的には、図１に示すように、ポケット壁部１３の内径面を一部切り欠いた凹曲線となる曲面形状となる切り欠き部７とし、この切り欠き部７が形成されたポケット壁部１３の帯幅Ｈ１が、玉５のピッチ円ＰＣＤを中心として玉径の３５％以下の範囲に収まり、且つ、外輪内径と内輪外径の間の半径方向寸法Ｈ３に対し、５０％以下の帯幅となるように形成されている。このように切り欠き部７を形成することにより、静止空間Ｓａから転走面２ａ，３ａへのグリースの供給をし易くしている。 Specifically, as shown in FIG. 1, the inner diameter surface of the pocket wall 13 is partially cut out to form a concave curved notch 7, and the width H1 of the pocket wall 13 where this notch 7 is formed is within a range of 35% or less of the ball diameter centered on the pitch circle PCD of the ball 5, and is formed so that the width is 50% or less of the radial dimension H3 between the inner diameter of the outer ring and the outer diameter of the inner ring. By forming the notch 7 in this way, it is easier to supply grease from the stationary space Sa to the rolling surfaces 2a, 3a.

＜厚肉部について＞
図２（Ｂ）に示すように、ポケット壁部１３は、前記切り欠き部７による体積減少分だけ軸受軸方向に厚肉にする厚肉部８を有する。この例では、切り欠き部が形成されていないポケット壁部（図示せず）よりもポケット壁部１３の全体が、軸受軸方向に前記体積減少分だけ厚肉に形成されている。換言すれば、ポケット壁部１３の全体が厚肉部８となっている。この厚肉部８により、切り欠き部７による玉軸受用保持器６の剛性低下を抑制し得る。 <About thick parts>
2(B), the pocket wall 13 has a thick-walled portion 8 that is thicker in the axial direction of the bearing by an amount equal to the volume reduction caused by the cutout 7. In this example, the entire pocket wall 13 is thicker in the axial direction of the bearing than a pocket wall (not shown) in which no cutout is formed by an amount equal to the volume reduction. In other words, the entire pocket wall 13 is the thick-walled portion 8. This thick-walled portion 8 can suppress a decrease in rigidity of the ball bearing cage 6 caused by the cutout 7.

＜作用効果＞
以上説明した玉軸受用保持器６およびこの玉軸受用保持器６を備えた転がり軸受１によれば、ポケット壁部１３の帯幅Ｈ１が、結合板部１４の径方向寸法Ｈ２（図３）よりも小さくなるようにポケット壁部１３の内径面１３ａに切り欠き部７が設けられているため、軸受運転時に、静止空間Ｓａに溜まったグリースが遠心力により切り欠き部７から転走面２ａ，３ａへ供給される。つまり、静止空間Ｓａに滞留しようとするグリースの一部が切り欠き部７で掻き取られることで、グリースの基油が分離して切り欠き部７から順次、保持器内、玉表面、転走面２ａ，３ａへと供給され易くなる。これにより転がり軸受１の発熱が抑えられ、従来技術よりもグリース寿命を延ばすことができる。またポケット壁部１３に切り欠き部７が設けられているため、玉５とポケット１２の間でのグリースせん断抵抗が低減され、転がり軸受１の低トルク化および低発熱化を図れる。
また、運転開始時においては、前記切り欠き部７が設けられていることで、玉５の表面に付着したグリースの掻き取り量が増え、グリースが動空間から静止空間Ｓａに排出され易くなり、グリースの慣らし時間を削減することができる。
前記切り欠き部７は、金型等により簡単に形成することができるため、鋼板製の波形保持器に凹み部を機械加工する従来例よりも加工コストを低減することができ、生産性に優れた玉軸受用保持器６とすることができる。 <Action and effect>
According to the ball bearing cage 6 and the rolling bearing 1 equipped with this ball bearing cage 6 described above, the notch 7 is provided in the inner diameter surface 13a of the pocket wall 13 so that the band width H1 of the pocket wall 13 is smaller than the radial dimension H2 (FIG. 3) of the connecting plate 14, so that the grease accumulated in the stationary space Sa is supplied to the rolling surfaces 2a, 3a from the notch 7 by centrifugal force during the operation of the bearing. In other words, a part of the grease that is about to stay in the stationary space Sa is scraped off by the notch 7, so that the base oil of the grease is separated and is easily supplied from the notch 7 to the inside of the cage, the ball surface, and the rolling surfaces 2a, 3a in sequence. This suppresses heat generation in the rolling bearing 1, and the grease life can be extended compared to the conventional technology. In addition, since the notch 7 is provided in the pocket wall 13, the grease shear resistance between the balls 5 and the pockets 12 is reduced, and the torque and heat generation of the rolling bearing 1 can be reduced.
In addition, at the start of operation, the provision of the cutout portion 7 increases the amount of grease adhering to the surface of the ball 5 that is scraped off, making it easier for the grease to be discharged from the moving space to the stationary space Sa, thereby reducing the break-in time for the grease.
The cutout portion 7 can be easily formed using a mold or the like, which reduces processing costs compared to the conventional example in which a recess is machined into a corrugated retainer made of steel plate, resulting in a ball bearing retainer 6 with excellent productivity.

切り欠き部７が設けられるポケット壁部１３の内径面１３ａが軸受軸方向から見て凹曲線となる曲面形状であるため、ポケット壁部１３の切り欠き部７に、局所的な応力集中が作用することを未然に防ぐことができる。また、射出成形用の金型等により切り欠き部７を簡単に形成することが可能となる。
前記切り欠き部７の最深部７ａ（図３、図５）の径方向位置は、玉５のピッチ円ＰＣＤ（図１）またはその付近に位置していてもよい。
切り欠き部７の最深部７ａが玉５のピッチ円ＰＣＤの付近の径方向位置付近に達していると、玉５とポケット壁部１３の内面との隙間が狭い箇所で切り欠き部７が開口することになり、静止空間Ｓａに近い場所でグリースを多くかきとることができる。そのため、グリースが動空間から排出され易くグリースの慣らし時間をより一層削減することができる。
玉５がセラミックボールである場合、例えば軸受鋼等から成る鋼球よりも比重を小さくして軸受の高速化を図ることができるうえ耐熱性を高めることができる。 Since the inner diameter surface 13a of the pocket wall 13 on which the cutout 7 is provided has a curved shape that forms a concave curve when viewed from the bearing axial direction, it is possible to prevent local stress concentration from acting on the cutout 7 of the pocket wall 13. Also, it is possible to easily form the cutout 7 using a die for injection molding or the like.
The radial position of the deepest part 7a (FIGS. 3 and 5) of the cutout portion 7 may be located at or near the pitch circle PCD (FIG. 1) of the ball 5.
If the deepest part 7a of the cutout 7 reaches a radial position near the pitch circle PCD of the balls 5, the cutout 7 opens at a location where the gap between the balls 5 and the inner surface of the pocket wall 13 is narrow, and a large amount of grease can be scraped off in a location close to the stationary space Sa. Therefore, the grease can be easily discharged from the dynamic space, and the break-in time of the grease can be further reduced.
When the balls 5 are ceramic balls, their specific gravity can be made smaller than that of steel balls made of bearing steel, for example, allowing for faster bearing speeds and improved heat resistance.

＜＜グリースの挙動解析結果＞＞
グリースの挙動解析結果を、図７Ａ、図７Ｂに示す。
図７Ａは、図１～図６に示す実施形態、すなわち切り欠き部７を有する玉軸受用保持器６の例を、図７Ｂは切り欠き部７を有しない玉軸受用保持器５５Ａの例を示す。両図の玉軸受用保持器６，７０におけるその他の構成は同じである。対応部分に同一符号が付してある。
切り欠き部７がない玉軸受用保持器５５Ａ（図７Ｂ）に対して、切り欠き部７が有る玉軸受用保持器６（図７Ａ）は、表面に付着したグリースＧ（黒塗り部分）から、ポケット壁部１３と結合板部１４との繋がり部１０ａでの掻き取りに加え、ポケット壁部１３の軸受周方向の中央部付近（符号Ａで示す円内）でのグリース掻き取り量が多く、差が認められた。 <<Grease behavior analysis results>>
The results of the analysis of the behavior of the grease are shown in FIG. 7A and FIG. 7B.
1 to 6, i.e., an example of a ball bearing cage 6 having a cutout portion 7, and Fig. 7B shows an example of a ball bearing cage 55A that does not have a cutout portion 7. The other configurations of the ball bearing cages 6 and 70 in both figures are the same. The same reference numerals are used for corresponding parts.
In comparison with ball bearing cage 55A (FIG. 7B) without cutout portion 7, ball bearing cage 6 (FIG. 7A) with cutout portion 7 had a difference in that a larger amount of grease was scraped off from the grease G (blackened portion) adhering to the surface at connecting portion 10a between pocket wall portion 13 and connecting plate portion 14, as well as near the center of pocket wall portion 13 in the circumferential direction of the bearing (within the circle indicated by symbol A).

＜＜解析条件＞＞
玉５は玉軸受用保持器６、５５Ａのポケット中心とし、グリースは玉５の表面に１．５mmの厚さで配置した。玉５の接触角は０°とし、内輪２の回転速度６００ｍｉｎ－１で玉５が１回転したときのグリース流動を求めた。 <<Analysis conditions>>
The balls 5 were placed at the center of the pockets of the ball bearing cages 6 and 55A, and grease was placed to a thickness of 1.5 mm on the surfaces of the balls 5. The contact angle of the balls 5 was set to 0°, and the grease flow was obtained when the balls 5 made one rotation at a rotation speed of 600 min -1 of the inner ring 2.

＜＜グリース慣らし性確認試験(1) ＞＞
図８は、グリース慣らし性確認試験(1) の試験結果を示す。横軸は時間（ｍｉｎ）、縦軸は外輪３の温度（℃）を示す。グリース慣らし性は、玉５の表面にグリースを塗布しておき、軸受の運転を開始した場合に、グリースが前記静止空間に移動して行く性能であり、グリースの攪拌抵抗による軸受温度の上昇によって確認できる。軸受温度の上昇は、外輪温度によって確認できる。
切り欠き部７を有する玉軸受用保持器６（図１～図６に示す実施形態）は、切り欠き部７を有しない玉軸受用保持器５５Ａに対して、各回転速度での外輪ピーク温度が低く、温度安定までに要する時間が短い。切り欠き部７を有する玉軸受用保持器６では、各回転速度３０分で、外輪観点温度が油潤滑時と同等となることが認められた。 <<Grease Break-in Test (1)>>
Figure 8 shows the test results of grease break-in test (1). The horizontal axis indicates time (min) and the vertical axis indicates the temperature (°C) of the outer ring 3. Grease break-in is the ability of grease to migrate into the stationary space when grease is applied to the surfaces of the balls 5 and the bearing is started to operate, and can be confirmed by the rise in bearing temperature caused by the agitation resistance of the grease. The rise in bearing temperature can be confirmed by the outer ring temperature.
The ball bearing cage 6 having the cutout 7 (embodiment shown in Figs. 1 to 6) has a lower outer ring peak temperature at each rotation speed and requires less time for the temperature to stabilize than the ball bearing cage 55A without the cutout 7. It was found that the ball bearing cage 6 having the cutout 7 had an outer ring point-of-view temperature equivalent to that during oil lubrication at each rotation speed for 30 minutes.

＜＜試験条件＞＞
試験機：横型トルク試験機
試験型番：６３１２
回転速度：４０００、６０００、８０００、１００００ｍｉｎ－１
荷重：Ｆｒ＝４１１Ｎ
試験：各回転速度で３０分
確認項目：外輪温度 <<Test conditions>>
Testing machine: Horizontal torque testing machine Test model number: 6312
Rotation speed: 4000, 6000, 8000 , 10000 min-1
Load: Fr = 411N
Test: 30 minutes at each rotation speed Check item: Outer ring temperature

＜＜グリース慣らし性確認試験(2) ＞＞
図９は、グリース慣らし性能確認試験(2) の試験結果を示す。
切り欠き部７を有する玉軸受用保持器６（図１～図６に示す実施形態）は、切り欠き部無し品に比べて、グリース慣らし時間が３０％低減した。後に図１０～図１４と共に説明するフランジ部３１を有する実施形態（フランジ部３１と切り欠き部７の両方有り）の玉軸受用保持器６の場合は、グリース慣らし時間が切り欠き部無し品に比べて、５０％低減した。前記「グリース慣らし時間」は、軸受の運転開始から外輪の温度が安定するまでに要する時間である。 <<Grease Break-in Test (2)>>
FIG. 9 shows the test results of the grease break-in performance verification test (2).
The ball bearing cage 6 having cutouts 7 (the embodiment shown in Figures 1 to 6) reduced the grease break-in time by 30% compared to a product without cutouts. In the case of the ball bearing cage 6 in the embodiment having flanges 31 (having both flanges 31 and cutouts 7) described later in conjunction with Figures 10 to 14, the grease break-in time was reduced by 50% compared to a product without cutouts. The "grease break-in time" is the time required for the temperature of the outer ring to stabilize after the bearing starts operating.

＜＜試験条件＞＞
試験機：横型トルク試験機
試験型番：６３１２
回転速度：５０００、１００００ｍｉｎ－１
荷重：Ｆｒ＝４１１Ｎ
試験：各回転速度で３０分
確認項目：外輪温度 <<Test conditions>>
Testing machine: Horizontal torque testing machine Test model number: 6312
Rotation speed: 5000, 10000 min -1
Load: Fr = 411N
Test: 30 minutes at each rotation speed Check item: Outer ring temperature

＜他の実施形態について＞
以下の説明においては、各実施の形態で先行して説明している事項に対応している部分には同一の参照符号を付し、重複する説明を略する。構成の一部のみを説明している場合、構成の他の部分は、特に記載のない限り先行して説明している形態と同様とする。同一の構成から同一の作用効果を奏する。実施の各形態で具体的に説明している部分の組合せばかりではなく、特に組合せに支障が生じなければ、実施の形態同士を部分的に組合せることも可能である。 <Other embodiments>
In the following description, parts corresponding to matters previously described in each embodiment are given the same reference symbols, and duplicated description is omitted. When only a part of the configuration is described, the other parts of the configuration are the same as the previously described embodiment unless otherwise specified. The same action and effect are achieved from the same configuration. It is possible to combine not only the parts specifically described in each embodiment, but also partially combine the embodiments, provided that there is no particular problem with the combination.

図１０～図１４は、この発明のさらに他の実施形態を示す。この実施形態の玉軸受用保持器６は、図１～図６と共に説明した第１の実施形態に係る玉軸受用保持器６において、結合板部１４の外径縁から軸方向に突出するフランジ部３１が設けられている。フランジ部３１は、結合板部１４の軸方向の両側に延び、かつ結合板部１４の軸受周方向の幅の全体に渡って設けられている。図１４に示すように、結合板部１４は、円周方向の両端に幅広部１４ａを有しているが、フランジ部３１の先端縁の軸方向位置は一定であり、両側のフランジ１４，１４の先端間の軸方向向幅寸法Ｂ（以下、「フランジ幅」と称す）（図１２）は、軸受周方向の全体に渡って一定であり、外輪３の転走面３ａの幅寸法と略同等とされている。 Figures 10 to 14 show yet another embodiment of the present invention. The ball bearing cage 6 of this embodiment is the ball bearing cage 6 according to the first embodiment described with reference to Figures 1 to 6, but is provided with flanges 31 that protrude in the axial direction from the outer diameter edge of the connecting plate 14. The flanges 31 extend on both sides of the connecting plate 14 in the axial direction, and are provided across the entire width of the connecting plate 14 in the circumferential direction of the bearing. As shown in Figure 14, the connecting plate 14 has wide portions 14a at both ends in the circumferential direction, but the axial position of the tip edge of the flanges 31 is constant, and the axial width dimension B between the tips of the flanges 14, 14 on both sides (hereinafter referred to as the "flange width") (Figure 12) is constant across the entire circumferential direction of the bearing and is approximately equal to the width dimension of the rolling surface 3a of the outer ring 3.

図１４は、この転がり軸受１を内輪２側から外輪３側に見た図であり、図６は第１の実施形態における転がり軸受を内輪２側から外輪３側に見た図である。フランジ部３１を設けない図６の実施形では、内輪２側から外輪３を見ると、外輪２の転走面３ａが玉軸受用保持器６の結合板部１４の両側に見えている（転走面３ａが見える箇所３ａａを同図に網点で示している）が、図１４の実施形態のようにフランジ部３１を設けた場合、外輪３の転走面３ａはフランジ部３１に隠れて見えない。 Figure 14 is a view of this rolling bearing 1 from the inner ring 2 side to the outer ring 3 side, and Figure 6 is a view of the rolling bearing in the first embodiment from the inner ring 2 side to the outer ring 3 side. In the embodiment of Figure 6 where the flange portion 31 is not provided, when the outer ring 3 is viewed from the inner ring 2 side, the rolling surface 3a of the outer ring 2 is visible on both sides of the connecting plate portion 14 of the ball bearing cage 6 (the portion 3aa where the rolling surface 3a is visible is shown by dots in the figure), but when the flange portion 31 is provided as in the embodiment of Figure 14, the rolling surface 3a of the outer ring 3 is hidden by the flange portion 31 and cannot be seen.

また、図１２に示すように、フランジ部３１の外径側面３１ａの断面は、軸受径方向に対して垂直であるが、内径側面３１ａは、軸受径方向に対し垂直な方向に対して傾斜角度αを持つ傾斜面とされている。前記傾斜角度αは、３°以上とされている。 As shown in FIG. 12, the cross section of the outer diameter side surface 31a of the flange portion 31 is perpendicular to the bearing radial direction, but the inner diameter side surface 31a is an inclined surface having an inclination angle α with respect to the direction perpendicular to the bearing radial direction. The inclination angle α is set to 3° or more.

この実施形態では、フランジ部３１を有することで、ポケット壁部１３と結合板部１４との繋がり部１０ａ（図７Ａ）の近傍で掻き取られたグリースが遠心力で外輪３の転走面３ａに巻き込まれるのが防止され、外輪３の転走面３ａの付近の動空間から、玉軸受用保持器６と密封板４の間の静止空間Ｓａ（図１）へ排出されるまでの時間がさらに短縮される。 In this embodiment, the flange portion 31 prevents the grease scraped off near the connection portion 10a (Fig. 7A) between the pocket wall portion 13 and the connecting plate portion 14 from being caught in the rolling surface 3a of the outer ring 3 by centrifugal force, further shortening the time it takes for the grease to be discharged from the dynamic space near the rolling surface 3a of the outer ring 3 to the static space Sa (Fig. 1) between the ball bearing cage 6 and the sealing plate 4.

前記フランジ部３１のフランジ幅Ｂ（図１２）は、外輪３の転走面の幅と略同等としているが、具体的には、フランジ幅Ｂは外輪転走面幅の９０～１１０％とし、より好ましいくは９５～１０５％とする。９０％以下では、遠心力で飛ばされたグリースが動空間となる外輪転走面３ａの付近へ巻き込まれるのを防ぎきれない。１１０％以上では、フランジ部３１に阻害されてグリースが動空間から排出され難くなる。
フランジ部３１の内径側面は、３°以上のテーパ形状とすることで、よりグリースが動空間から排出され易くなる。３°以下では、グリースが動空間から排出され難くなる。 The flange width B (FIG. 12) of the flange portion 31 is approximately equal to the width of the rolling surface of the outer ring 3, but specifically, the flange width B is 90-110% of the width of the outer ring rolling surface, and more preferably 95-105%. If it is less than 90%, it is not possible to prevent the grease thrown by centrifugal force from being drawn into the vicinity of the outer ring rolling surface 3a, which forms the dynamic space. If it is more than 110%, the flange portion 31 obstructs the grease from being discharged from the dynamic space.
By forming the inner diameter side surface of the flange portion 31 into a tapered shape of 3° or more, the grease can be more easily discharged from the moving space. If the tapered shape is less than 3°, the grease cannot be easily discharged from the moving space.

なお、参考例として示すと、従来の鉄板波型保持器に前記切り欠き部７およびフランジ部３１を設けても、グリースの挙動に関してはこの実施形態と同様の効果が得られるが、鉄板保持器では製作に手間がかかり製作コストが嵩むと言う課題がある。 As a reference example, if the cutout portion 7 and flange portion 31 are provided on a conventional corrugated steel plate cage, the same effect as in this embodiment can be obtained in terms of grease behavior, but there is a problem that the steel plate cage is time-consuming to manufacture and therefore expensive to manufacture.

＜厚肉部８の変形例＞
図１５～図１７に示すように、ポケット壁部１３における内径部を他の部分よりも軸方向外側に厚肉に形成された厚肉部８としてもよい。この厚肉部８は、切り欠き部７による体積減少分だけポケット壁部１３の内径部を軸受軸方向に厚肉にするものである。厚肉部８により、切り欠き部７による玉軸受用保持器６の剛性低下を抑制し得る。
図１８～図２０に示すように、ポケット壁部１３のうち、玉５のピッチ円ＰＣＤ（図１）に略沿った外側面が他の部分よりも厚肉に形成された厚肉部８としてもよい。この場合にも、切り欠き部７による玉軸受用保持器６の剛性低下を抑制し得る。 <Modifications of thick portion 8>
15 to 17, the inner diameter portion of the pocket wall 13 may be formed as a thick-walled portion 8 that is thicker on the axially outer side than other portions. This thick-walled portion 8 thickens the inner diameter portion of the pocket wall 13 in the axial direction of the bearing by an amount corresponding to the volume reduction caused by the cutout portion 7. The thick-walled portion 8 can suppress a decrease in rigidity of the ball bearing cage 6 caused by the cutout portion 7.
18 to 20, the outer surface of the pocket wall 13 that is generally aligned with the pitch circle PCD (FIG. 1) of the balls 5 may be formed as a thick-walled portion 8 that is thicker than other portions. In this case, too, the reduction in rigidity of the ball bearing cage 6 caused by the cutout portion 7 can be suppressed.

図２１～図２３に示すように、ポケット壁部１３における内径部および外径部がそれぞれ他の部分よりも軸方向外側に厚肉に形成された厚肉部８としてもよい。この場合、厚肉部８を、ポケット壁部１３の内径部と外径部に離隔させて設けたため、軸受運転時における玉軸受用保持器６のバランスがよく、転がり軸受の高速化をより図ることができる。また切り欠き部７による玉軸受用保持器６の剛性低下を抑制し得る。 As shown in Figures 21 to 23, the inner diameter portion and the outer diameter portion of the pocket wall portion 13 may each be formed as a thick-walled portion 8 that is thicker on the axially outer side than the other portions. In this case, since the thick-walled portion 8 is provided at a distance from the inner diameter portion and the outer diameter portion of the pocket wall portion 13, the ball bearing retainer 6 is well balanced when the bearing is in operation, and the rolling bearing can be operated at a higher speed. In addition, the reduction in rigidity of the ball bearing retainer 6 due to the cutout portion 7 can be suppressed.

図２４～図２６に示すように、ポケット壁部１３は、外側面が内径面から外径面に向かうに従って厚肉となるテーパ形状に形成された厚肉部８としてもよい。この場合、ポケット壁部１３の外径側程厚肉となるため、軸受運転時に玉軸受用保持器６に作用するフープ応力に対抗することができる。また切り欠き部７による玉軸受用保持器６の剛性低下を抑制し得る。 As shown in Figures 24 to 26, the pocket wall 13 may be a thick-walled portion 8 formed in a tapered shape in which the outer surface becomes thicker from the inner diameter surface toward the outer diameter surface. In this case, the pocket wall 13 becomes thicker toward the outer diameter side, so that it can withstand the hoop stress acting on the ball bearing retainer 6 during bearing operation. It is also possible to suppress a decrease in the rigidity of the ball bearing retainer 6 due to the cutout portion 7.

＜切り欠き部７の配設箇所の変形例＞
図２７に示すように、ポケット壁部１３の外径面に切り欠き部７が設けられてもよい。このポケット壁部１３の外径面は軸受軸方向から見て凹曲線となる曲面形状である。この構成においても、第１の実施形態と同様の作用効果を奏する。 <Modification of the location of the cutout portion 7>
27, a notch 7 may be provided on the outer diameter surface of the pocket wall 13. The outer diameter surface of the pocket wall 13 has a curved shape that is a concave curve when viewed in the axial direction of the bearing. With this configuration, the same effects as those of the first embodiment can be achieved.

＜切り欠き部７の形状の変形例＞
切り欠き部７の形状、すなわち切り欠き部７が設けられるポケット壁部１３の内径面または外径面は、軸受軸方向から見て多角形状に形成されていてもよい。例えば、切り欠き部７の形状は、図３３に示すように矩形状としてもよく、図３４に示すように三角形状としてもよく、また図３５に示すように軸受径方向に延びるスリット状としてもよい。図３３のように切り欠き部７の軸受周方向幅がポケット壁部の軸受周方向の幅の半分以上となる矩形状であって、かつ切り欠き部７の最深部７ａが玉５のピッチ円ＰＣＤの付近に位置する場合、グリースが動空間から静止空間Ｓａにより一層、流出し易くなる。矩形状に限らず、例えば、円弧状の曲線形状の切り欠き部７を軸受径方向に扁平化させた楕円弧状とするなど、切り欠き部７の深い箇所の軸受周方向幅が広い形状であれば、グリースが動空間から静止空間Ｓａにより流出し易くなる効果がえられる。
図示しないが、転がり軸受に用いられる密閉板は接触シールを用いてもよい。なお玉軸受用保持器は、密閉板が設けられていない開放形の転がり軸受にも適用可能である。
玉軸受用保持器の各環状体を、３Ｄプリンターまたは機械加工により形成することも可能である。 <Modifications of the shape of the cutout portion 7>
The shape of the cutout 7, i.e., the inner diameter surface or the outer diameter surface of the pocket wall 13 on which the cutout 7 is provided, may be formed in a polygonal shape when viewed from the bearing axial direction. For example, the shape of the cutout 7 may be rectangular as shown in FIG. 33, triangular as shown in FIG. 34, or slit-like extending in the bearing radial direction as shown in FIG. 35. When the cutout 7 has a rectangular shape whose circumferential width in the bearing direction is equal to or more than half the circumferential width of the pocket wall as shown in FIG. 33 and the deepest part 7a of the cutout 7 is located near the pitch circle PCD of the balls 5, the grease is more likely to flow out from the dynamic space to the stationary space Sa. The shape is not limited to a rectangular shape, and if the cutout 7 has a wide circumferential width in the bearing at a deep part of the cutout 7, for example, the cutout 7 having a curved arc shape is flattened in the bearing radial direction to an elliptical arc shape, the effect of making it easier for the grease to flow out from the dynamic space to the stationary space Sa can be obtained.
Although not shown, the sealing plate used in the rolling bearing may be a contact seal. The ball bearing cage can also be applied to an open type rolling bearing that is not provided with a sealing plate.
Each annulus of the ball bearing cage can also be formed by 3D printing or machining.

ところで、従来の樹脂製波形保持器の課題として、回転速度がｄｎ６０万を超える高速領域において、決まった回転速度で保持器の振動、つまり保持器の固有振動との共振が発生することにより、潤滑剤を巻き込み一時的に急激な昇温が発生する。
金属部品を用いて樹脂保持器の剛性・固有振動数を上昇させることで、高速性を向上させる技術（特許文献４）が提案されているが、金属部品を用いることでコストアップとなる。 However, a problem with conventional resin wave-shaped cages is that in the high-speed range where the rotational speed exceeds dn 600,000, the cage vibrates at a certain rotational speed, that is, resonance occurs with the natural vibration of the cage, causing the lubricant to be drawn in and resulting in a temporary, rapid rise in temperature.
A technology has been proposed to improve high speed performance by using metal parts to increase the rigidity and natural frequency of the resin cage (Patent Document 4), but the use of metal parts increases costs.

そこで、図２８に示すように、互いに重なった二つの結合板部１４，１４の軸方向寸法（結合部肉厚）ｔ１を、玉５（図２９）の直径の５５％～６５％とすることで玉軸受用保持器６が高剛性になり、玉軸受用保持器６の固有振動数が上昇する。前記軸方向寸法ｔ１の下限を玉直径の５５％とすることで、玉軸受用保持器６における、玉５（図２９）を抱えている根元部Ｎｍ（図２８）の厚み（軸方向厚み）が厚くなることで、玉軸受用保持器６が高剛性になり高速回転時の遠心力に対する耐久性を高め得る。玉軸受用保持器６の高剛性化による固有振動数の上昇により、回転速度との共振が発生しない。このことにより共振による玉軸受用保持器６の振動も発生せず、昇温が抑制され安定した回転が得られる。 As shown in FIG. 28, the axial dimension (thickness of the joint) t1 of the two overlapping joint plate portions 14, 14 is set to 55% to 65% of the diameter of the ball 5 (FIG. 29), thereby making the ball bearing retainer 6 highly rigid and increasing the natural frequency of the ball bearing retainer 6. By setting the lower limit of the axial dimension t1 to 55% of the ball diameter, the thickness (axial thickness) of the base portion Nm (FIG. 28) of the ball bearing retainer 6 that holds the ball 5 (FIG. 29) becomes thicker, making the ball bearing retainer 6 highly rigid and increasing its durability against centrifugal forces during high-speed rotation. The increase in the natural frequency due to the high rigidity of the ball bearing retainer 6 prevents resonance with the rotation speed. As a result, vibration of the ball bearing retainer 6 due to resonance does not occur, temperature rise is suppressed, and stable rotation is obtained.

前記軸方向寸法ｔ１の上限を玉直径の６５％にした理由は以下の通りである。
上記玉直径の６５％は、図２９に示す外輪溝幅（外輪転走面幅寸法）Ｌ１の９０％にあたる。転がり軸受１において、玉軸受用保持器６のポケット間（各結合板部の側面）に封入されたグリースは、初期回転時、遠心力で径方向外方の外輪３側へ飛ばされるが、前記軸方向寸法ｔ１（図２８）が外輪溝幅Ｌ１の９０％以上の場合、遠心力で飛ばされたグリースが転走面（軌道面）３ａへ供給され難い。
一方、前記軸方向寸法ｔ１（図２８）が外輪溝幅Ｌ１の９０％未満の場合は、グリースが軌道面３ａへ供給され易く、初期の潤滑供給性が向上する。このため、前記軸方向寸法ｔ１（図２８）は、外輪溝幅Ｌ１の９０％にあたる６５％を上限としている。 The reason why the upper limit of the axial dimension t1 is set to 65% of the ball diameter is as follows.
The above 65% of the ball diameter corresponds to 90% of the outer ring groove width (outer ring rolling surface width dimension) L1 shown in Fig. 29. In the rolling bearing 1, the grease sealed between the pockets (side surfaces of each connecting plate portion) of the ball bearing cage 6 is thrown radially outward toward the outer ring 3 by centrifugal force during initial rotation, but if the axial dimension t1 (Fig. 28) is 90% or more of the outer ring groove width L1, the grease thrown by centrifugal force is difficult to supply to the rolling surface (raceway surface) 3a.
On the other hand, when the axial dimension t1 (FIG. 28) is less than 90% of the outer ring groove width L1, the grease is easily supplied to the raceway surface 3a, improving the initial lubrication supply. For this reason, the axial dimension t1 (FIG. 28) is set at an upper limit of 65%, which corresponds to 90% of the outer ring groove width L1.

結合部肉厚の違いによる昇温試験を実施した。
＜試験条件＞
試験機 ：高速試験機（図３０）
試験軸受：呼び番号６３１２
回転速度：３０００ｍｉｎ－１から１３５００ｍｉｎ－１までステップアップ
荷重 ：アキシアル荷重Ｆａ＝５８８．４Ｎ
測定項目：軸受外輪温度 A temperature rise test was conducted with different joint thicknesses.
<Test conditions>
Testing machine: High-speed testing machine (Fig. 30)
Test bearing: Nominal number 6312
Rotation speed: Step up from 3000 min -1 to 13500 min -1 Load: Axial load Fa = 588.4 N
Measurement item: Bearing outer ring temperature

図３０に示すように、試験軸受として、二個の転がり軸受を軸方向に所定間隔を空けて設置し、モータ２４の駆動による内輪回転とした。モータ２４側に近い図３０の左側の転がり軸受をモータ側軸受Ｂｒ１とし、図３０の右側の転がり軸受を反モータ側軸受Ｂｒ２とした。またハウジング２６に、外輪温度測定用の熱電対２７，２７がそれぞれ設置された。
昇温試験結果の図３１、図３２によると、結合部肉厚を厚くしていない実施形態品に対し、結合部肉厚を厚くした図２８の実施形態に係る試験軸受は、モータ側軸受Ｂｒ１、反モータ側軸受Ｂｒ２共に急激な昇温が抑えられ、ｄｎ＝６０万以上の高速運転が可能である。 As shown in Fig. 30, two rolling bearings were installed as test bearings with a specified distance between them in the axial direction, and the inner ring was rotated by driving the motor 24. The rolling bearing on the left side of Fig. 30, closer to the motor 24, was designated as the motor-side bearing Br1, and the rolling bearing on the right side of Fig. 30 was designated as the anti-motor-side bearing Br2. Thermocouples 27, 27 for measuring the temperature of the outer ring were also installed in the housing 26.
According to the temperature rise test results in Figs. 31 and 32, compared to the embodiment where the joint thickness is not increased, the test bearing according to the embodiment of Fig. 28 where the joint thickness is increased suppresses sudden temperature increases in both the motor-side bearing Br1 and the anti-motor side bearing Br2, and high-speed operation of dn = 600,000 or more is possible.

以上、実施形態に基づいてこの発明を実施するための形態を説明したが、今回開示された実施の形態はすべての点で例示であって制限的なものではない。この発明の範囲は上記した説明ではなくて特許請求の範囲によって示され、特許請求の範囲と均等の意味および範囲内でのすべての変更が含まれることが意図される。 The above describes the mode for carrying out the present invention based on the embodiment, but the embodiment disclosed herein is illustrative in all respects and is not restrictive. The scope of the present invention is indicated by the claims, not the above description, and is intended to include all modifications within the meaning and scope of the claims.

１…転がり軸受、２…内輪、２ａ…転走面、３…外輪、３ａ…転走面、４…密閉板、５…玉、６…玉軸受用保持器、７…切り欠き部、８…厚肉部、１０…環状体、１２…ポケット、１３…ポケット壁部、１４…結合板部、３１…フランジ部、Ｓａ…静止空間

 Reference Signs List 1... rolling bearing, 2... inner ring, 2a... rolling surface, 3... outer ring, 3a... rolling surface, 4... sealing plate, 5... ball, 6... ball bearing cage, 7... notch portion, 8... thick portion, 10... annular body, 12... pocket, 13... pocket wall portion, 14... connecting plate portion, 31... flange portion, Sa... stationary space

Claims (6)

互いに軸方向に重なる二枚の合成樹脂製の環状体を有し、各環状体は、円周方向に所定の間隔で並びそれぞれが玉を保持するポケットの内壁面を構成する複数の半球状のポケット壁部と、円周方向に隣合う前記ポケット壁部同士を連結する複数の結合板部とを有し、前記二枚の環状体が、前記各結合板部で互いに重なって結合された玉軸受用保持器であって、
前記ポケット壁部の径方向寸法である帯幅が、前記結合板部の径方向寸法よりも小さくなるように、前記ポケット壁部の内径面または外径面に切り欠き部が設けられ、
前記ポケット壁部は、前記ポケット壁部における内径部を前記ポケット壁部の他の部分よりも軸受軸方向外側に厚肉にする厚肉部を有し、
前記結合板部の外径縁から軸方向に突出するフランジ部が設けられ、
前記フランジ部の内径側面が、軸受径方向に対し垂直な方向に対して傾斜角度を持つ傾斜面であり、前記傾斜面が、前記フランジ部の突出する方向に向かうに従って前記フランジ部の外径側面に向かって傾斜しており、前記傾斜角度が３°以上である玉軸受用保持器。 A cage for a ball bearing, comprising two synthetic resin annular bodies overlapping each other in the axial direction, each annular body having a plurality of hemispherical pocket wall portions arranged at a predetermined interval in the circumferential direction and constituting an inner wall surface of a pocket for holding balls, and a plurality of connecting plate portions connecting adjacent pocket wall portions in the circumferential direction, the two annular bodies being overlapped and connected to each other at the connecting plate portions,
A notch is provided on an inner diameter surface or an outer diameter surface of the pocket wall portion so that a band width, which is a radial dimension of the pocket wall portion, is smaller than a radial dimension of the connecting plate portion,
the pocket wall portion has a thick-walled portion that makes an inner diameter portion of the pocket wall portion thicker toward an outer side in the axial direction of the bearing than other portions of the pocket wall portion,
A flange portion is provided protruding in the axial direction from an outer diameter edge of the connecting plate portion,
A retainer for a ball bearing, wherein the inner diameter side surface of the flange portion is an inclined surface having an inclination angle with respect to a direction perpendicular to the radial direction of the bearing, the inclined surface inclining toward the outer diameter side surface of the flange portion as it proceeds in the direction in which the flange portion protrudes, and the inclination angle is 3° or more. 請求項１に記載の玉軸受用保持器において、前記切り欠き部は、前記ポケット壁部の内径面または外径面が軸受軸方向から見て凹曲線となる曲線形状である玉軸受用保持器。 The ball bearing cage according to claim 1, wherein the cutout portion is a curved shape in which the inner diameter surface or the outer diameter surface of the pocket wall portion is a concave curve when viewed from the bearing axial direction. 請求項１または請求項２に記載の玉軸受用保持器において、前記切り欠き部の最深部の軸受径方向の位置が、前記玉のピッチ円付近に位置する玉軸受用保持器。 The ball bearing cage according to claim 1 or 2, in which the deepest part of the cutout portion is located in the radial direction of the bearing near the pitch circle of the ball. 請求項１ないし請求項３のいずれか１項に記載の玉軸受用保持器において、前記互いに重なった二つの結合板部の軸方向寸法を、前記玉の直径の５５％～６５％とした玉軸受用保持器。 4. The ball bearing cage according to claim 1, wherein the axial dimension of the two overlapping connecting plate portions is 55% to 65% of the diameter of the balls. 請求項１ないし請求項４のいずれか１項に記載の玉軸受用保持器を備えた転がり軸受。 A rolling bearing comprising the cage for a ball bearing according to any one of claims 1 to 4 . 請求項５に記載の転がり軸受において、前記玉がセラミックボールである転がり軸受。 6. The rolling bearing according to claim 5 , wherein said balls are ceramic balls.
JP2019167218A 2018-09-21 2019-09-13 Ball bearing cages and rolling bearings Active JP7535372B2 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201980061278.0A CN112739923B (en) 2018-09-21 2019-09-19 Retainer for ball bearing and rolling bearing
PCT/JP2019/036854 WO2020059829A1 (en) 2018-09-21 2019-09-19 Ball bearing retainer and rolling bearing
DE112019004733.7T DE112019004733T5 (en) 2018-09-21 2019-09-19 Ball bearing holder and roller bearing

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2018177772 2018-09-21
JP2018177772 2018-09-21
JP2019054026 2019-03-22
JP2019054026 2019-03-22

Publications (2)

Publication Number Publication Date
JP2020159548A JP2020159548A (en) 2020-10-01
JP7535372B2 true JP7535372B2 (en) 2024-08-16

Family

ID=72642647

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2019167218A Active JP7535372B2 (en) 2018-09-21 2019-09-13 Ball bearing cages and rolling bearings

Country Status (3)

Country Link
JP (1) JP7535372B2 (en)
CN (1) CN112739923B (en)
DE (1) DE112019004733T5 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113931929B (en) * 2021-09-16 2024-01-23 上海工程技术大学 Rolling bearing device capable of autonomously reducing vibration and noise
CN114001094B (en) * 2021-11-23 2024-05-24 苏州汇智精保持架科技有限公司 Multifunctional glass fiber injection molding bearing retainer and preparation method thereof

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006226447A (en) 2005-02-18 2006-08-31 Ntn Corp Retainer made of synthetic resin and ball bearing
JP2008064166A (en) 2006-09-06 2008-03-21 Ntn Corp Ball bearing
JP2008281196A (en) 2007-04-11 2008-11-20 Ntn Corp Bearing for two-wheeled vehicle reduction gear
JP2009174605A (en) 2008-01-23 2009-08-06 Ntn Corp Wavy cage for ball bearing, and deep groove ball bearing
JP2012172784A (en) 2011-02-23 2012-09-10 Nsk Ltd Ball bearing
JP2013213555A (en) 2012-04-03 2013-10-17 Ntn Corp Synthetic resin retainer and ball bearing
JP2017203551A (en) 2011-02-25 2017-11-16 日本精工株式会社 Ball bearing, and motor and spindle device using the same
US20180010640A1 (en) 2016-07-06 2018-01-11 Regal Beloit America, Inc. Bearing retainer, bearing and associated method

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11315840A (en) * 1998-05-07 1999-11-16 Nippon Seiko Kk Rolling bearing holder
JP3891741B2 (en) * 1999-09-14 2007-03-14 日本精工株式会社 Crown type cage for ball bearings and ball bearings
JP2002349579A (en) * 2001-05-22 2002-12-04 Nsk Ltd Ball bearing
JP2009008170A (en) * 2007-06-28 2009-01-15 Nsk Ltd Retainer made of resin, and ball bearing using this retainer
JP2009156391A (en) * 2007-12-27 2009-07-16 Ntn Corp Cage for roller bearing and needle roller bearing
JP5583460B2 (en) * 2009-05-14 2014-09-03 Ｎｔｎ株式会社 Transmission bearings
CN102032275A (en) * 2011-01-18 2011-04-27 常熟长城轴承有限公司 Solid cage for bearing
CN102242764B (en) * 2011-07-15 2013-04-17 常州光洋轴承股份有限公司 Four-point contact ball bearing
CN103438103A (en) * 2013-05-04 2013-12-11 安徽华之杰机械有限公司 Retainer with double curvature special-shaped pockets
CN203585105U (en) * 2013-11-05 2014-05-07 日本精工株式会社 Bearing device for railway vehicle axle
DE102014200278A1 (en) * 2014-01-10 2015-07-16 Schaeffler Technologies AG & Co. KG Rolling Element
JP6742068B2 (en) * 2014-11-04 2020-08-19 Ntn株式会社 Synthetic resin cage and ball bearing
DE102015224859A1 (en) * 2015-12-10 2017-06-14 Schaeffler Technologies AG & Co. KG A ball bearing retainer
JP2017116008A (en) * 2015-12-25 2017-06-29 株式会社ジェイテクト Rolling bearing
CN106050933A (en) * 2016-07-21 2016-10-26 洛阳鸿元轴承科技有限公司 Retainer and crossed roller bearing provided with same
TWI704298B (en) * 2016-11-04 2020-09-11 日商日本精工股份有限公司 Cage and rolling bearing provided with it

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006226447A (en) 2005-02-18 2006-08-31 Ntn Corp Retainer made of synthetic resin and ball bearing
JP2008064166A (en) 2006-09-06 2008-03-21 Ntn Corp Ball bearing
JP2008281196A (en) 2007-04-11 2008-11-20 Ntn Corp Bearing for two-wheeled vehicle reduction gear
JP2009174605A (en) 2008-01-23 2009-08-06 Ntn Corp Wavy cage for ball bearing, and deep groove ball bearing
JP2012172784A (en) 2011-02-23 2012-09-10 Nsk Ltd Ball bearing
JP2017203551A (en) 2011-02-25 2017-11-16 日本精工株式会社 Ball bearing, and motor and spindle device using the same
JP2013213555A (en) 2012-04-03 2013-10-17 Ntn Corp Synthetic resin retainer and ball bearing
US20180010640A1 (en) 2016-07-06 2018-01-11 Regal Beloit America, Inc. Bearing retainer, bearing and associated method

Also Published As

Publication number Publication date
JP2020159548A (en) 2020-10-01
CN112739923B (en) 2023-03-17
CN112739923A (en) 2021-04-30
DE112019004733T5 (en) 2021-06-02

Similar Documents

Publication Publication Date Title
US8292512B2 (en) Ball bearing and supporting construction
US9022662B2 (en) Retainer made of synthetic resin for use in ball bearing and ball bearing
JP7535372B2 (en) Ball bearing cages and rolling bearings
CN109690101B (en) Bearing with seal
JP5894491B2 (en) Rolling bearing
JP2014119029A (en) Rolling bearing
JP2006518023A (en) Thrust bearing with spacer member
JP2009281399A (en) Deep groove ball bearing cage and deep groove ball bearing
JP5435843B2 (en) Ball bearing cage
JP2008128296A (en) Crown type synthetic resin cage for radial ball bearing, and radial ball bearing
JP2022036002A (en) Ball bearing
WO2020059829A1 (en) Ball bearing retainer and rolling bearing
JP2011196422A (en) Rolling bearing
WO2022186094A1 (en) Rolling bearing and cage for rolling bearing
JP5715001B2 (en) Radial ball bearings
JP2014005913A (en) Rolling bearing
JP2002295480A (en) Ball bearing
JP2000161365A (en) Crown type retainer, ball bearing and rotary machine device
JP7526585B2 (en) Rolling bearing cage and rolling bearing
WO2016121562A1 (en) Retainer for ball bearing, and ball bearing using said retainer for ball bearing
WO2016208352A1 (en) Retainer and deep groove ball bearing
JP2007187207A (en) Thrust roller bearing
JP6505446B2 (en) Corrugated cage for ball bearing and ball bearing using the corrugated cage for the ball bearing
JP2021195973A (en) Ball bearing
JP2008111456A (en) Synthetic resin crown type retainer for radial ball bearing, and radial ball bearing

Legal Events

Date Code Title Description
RD01 Notification of change of attorney

Free format text: JAPANESE INTERMEDIATE CODE: A7421

Effective date: 20210106

RD03 Notification of appointment of power of attorney

Free format text: JAPANESE INTERMEDIATE CODE: A7423

Effective date: 20210319

A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20220826

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20230314

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20230424

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20230801

A601 Written request for extension of time

Free format text: JAPANESE INTERMEDIATE CODE: A601

Effective date: 20230929

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20231129

A02 Decision of refusal

Free format text: JAPANESE INTERMEDIATE CODE: A02

Effective date: 20240206

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20240424

A911 Transfer to examiner for re-examination before appeal (zenchi)

Free format text: JAPANESE INTERMEDIATE CODE: A911

Effective date: 20240502

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20240709

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20240805

R150 Certificate of patent or registration of utility model

Ref document number: 7535372

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150