JP2008051206A - Angular ball bearing - Google Patents

Angular ball bearing Download PDF

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Publication number
JP2008051206A
JP2008051206A JP2006227888A JP2006227888A JP2008051206A JP 2008051206 A JP2008051206 A JP 2008051206A JP 2006227888 A JP2006227888 A JP 2006227888A JP 2006227888 A JP2006227888 A JP 2006227888A JP 2008051206 A JP2008051206 A JP 2008051206A
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Prior art keywords
outer ring
ball
inner ring
cage
ring
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Japanese (ja)
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Hiroki Tanimura
浩樹 谷村
Yoshimitsu Hirasawa
義光 平澤
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2006227888A priority Critical patent/JP2008051206A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/41—Ball cages comb-shaped
    • F16C33/412—Massive or moulded comb cages, e.g. snap ball cages
    • F16C33/414—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages
    • F16C33/416—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages made from plastic, e.g. injection moulded comb 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts

Abstract

<P>PROBLEM TO BE SOLVED: To provide an outer ring separation type angular ball bearing sized in 200 mm or more of outer diameter of outer ring in which a sufficient vacant space can be kept at a counter portion side of the outer ring, and in such an assembly condition that the outer ring is separated, a ball is prevented from falling out in a state in which the ball does not run up onto a counter portion of inner ring. <P>SOLUTION: Between a plurality of pillar portions 4b extending from an annular portion 4a annually lined at a counter portion 1b side of the inner ring 1, a crown type retainer 4 made of resin in which a pocket 5 supporting the ball 3 is arranged is employed. The back side end face 4c of the annular portion 4a is made flat without depression, and the retainer 4 is prevented from projecting toward the counter portion 2b side of the outer ring 2. A sufficient vacant space can be kept at the counter portion 2b side of the outer ring 2, and the rigidity of the annular portion 4a of the crown type retainer 4 is improved simultaneously. Thus, in an assembly condition that the outer ring 2 is separated, the ball 3 is prevented from falling out in a state in which the ball 3 does not ride onto the counter portion 1b of the inner ring 1. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本発明は、外輪分離型のアンギュラ玉軸受に関する。   The present invention relates to an outer ring separated angular contact ball bearing.

液晶パネルや自動車車体等を搬送する搬送用ロボットに使用される減速機の主軸等を支持するアンギュラ軸受には、内輪と外輪の軌道溝間に配列されるボールが、外輪を分離したアセンブリ状態で、樹脂製の保持器によって内輪と一体に保持されるようにした、組み立て性のよい外輪分離型のものが多く採用されている。このような搬送用ロボットは、搬送されるワークの大型化に伴って減速機の主軸も大径化しており、主軸を支持するアンギュラ玉軸受の外輪の外径寸法も２００ｍｍ以上のものが増えている。   An angular bearing that supports the main shaft of a reducer used in a transfer robot that transfers liquid crystal panels, automobile bodies, etc., has an assembly in which the balls arranged between the inner and outer raceway grooves are separated from the outer ring. In many cases, an outer ring separation type which is held integrally with the inner ring by a resin cage and has good assemblability is adopted. In such a transfer robot, the main shaft of the speed reducer has increased in size with the increase in the size of the workpiece to be transferred, and the outer diameter of the outer ring of the angular ball bearing that supports the main shaft has increased to 200 mm or more. Yes.

このような外輪の外径寸法が２００ｍｍ以上の外輪分離型アンギュラ玉軸受では、外輪を分離したアセンブリ状態で、保持器に保持されたボールが内輪の軌道溝からカウンタ部へ乗り上げて落下しないように、保持器として剛性の高いリング部の周面に円形のポケットを設けたリング型のものが用いられている（例えば、特許文献１参照）。   In such an outer ring separated angular contact ball bearing with an outer ring outer diameter dimension of 200 mm or more, the ball held by the cage does not ride on the counter part from the inner ring raceway groove and fall in the assembled state with the outer ring separated. As a cage, a ring-type one having a circular pocket on the peripheral surface of a highly rigid ring portion is used (see, for example, Patent Document 1).

実開平４−７８３３１号公報Japanese Utility Model Publication No. 4-78331

上述した搬送用ロボットの減速機は、ワークの大型化に伴って主軸が大径化しているが、減速機自体はコンパクト化が要求されている。このような減速機のコンパクト化を実現するために、図７に示すように、主軸を支持するアンギュラ玉軸受の外輪２のカウンタ部２ｂの長さを短くし、空いたスペースに他の部品Ａを組み込み可能とする設計が望まれている。   In the above-described speed reducer for the transfer robot, the diameter of the spindle is increased with the increase in size of the workpiece, but the speed reducer itself is required to be compact. In order to realize such a reduction gear reducer, as shown in FIG. 7, the length of the counter part 2b of the outer ring 2 of the angular ball bearing supporting the main shaft is shortened, and another part A is formed in the vacant space. A design that can be embedded is desired.

しかしながら、特許文献１に記載された外輪分離型アンギュラ軸受のように、リング型保持器２１を用いたものは、高い剛性によって、ボール３の内輪１のカウンタ部１ｂへの乗り上げは防止できるが、図７に示したように、カウンタ部２ｂの長さを短くした外輪２が組み付けられて組み立てられたときに、内輪１と外輪２の軌道溝１ａ、２ａ間に配列されたボール３の軸方向両側へ保持器２１のリング部が張り出し、外輪２のカウンタ部２ｂ側へ張り出すリング部が部品Ａと干渉する恐れがあるので、部品Ａの組み込み可能スペースが狭くなって、十分なコンパクト化を実現できない問題がある。   However, like the outer ring separated angular bearing described in Patent Document 1, the ring type cage 21 can prevent the ball 3 from riding on the counter portion 1b of the inner ring 1 due to high rigidity. As shown in FIG. 7, the axial direction of the balls 3 arranged between the race grooves 1a, 2a of the inner ring 1 and the outer ring 2 when the outer ring 2 with the counter part 2b having a reduced length is assembled and assembled. Since the ring part of the retainer 21 projects to both sides and the ring part projecting to the counter part 2b side of the outer ring 2 may interfere with the part A, the space in which the part A can be assembled is narrowed, and sufficient compactness is achieved. There are problems that cannot be realized.

そこで、本発明の課題は、外輪のカウンタ部側に十分な空きスペースを確保でき、かつ、外輪を分離したアセンブリ状態で、ボールが内輪のカウンタ部へ乗り上げて落下することのない、外輪の外径が２００ｍｍ以上の外輪分離型アンギュラ玉軸受を提供することである。   Accordingly, an object of the present invention is to secure a sufficient free space on the counter part side of the outer ring and prevent the ball from riding on the counter part of the inner ring and falling in an assembled state where the outer ring is separated. An outer ring separation type angular contact ball bearing having a diameter of 200 mm or more is provided.

上記の課題を解決するために、本発明は、内輪と外輪の軌道溝間に配列されるボールが、外輪を分離した状態で内輪と一体に樹脂製の保持器で保持される外輪分離型で、前記外輪の外径寸法が２００ｍｍ以上とされ、前記内輪の軌道溝の片側にカウンタ部が設けられたアンギュラ玉軸受において、前記樹脂製の保持器を、前記内輪のカウンタ部側で環状に連なる環状部から軸受中心側に延びる複数の柱部の間に、前記ボールを保持するポケットを設けた冠型のものとし、前記環状部の軸受中心側と反対側の背面側端面をぬすみのない平坦面とした構成を採用した。   In order to solve the above-mentioned problems, the present invention is an outer ring separation type in which balls arranged between the inner and outer raceway grooves are held by a resin cage integrally with the inner ring in a state where the outer ring is separated. In the angular ball bearing in which the outer diameter of the outer ring is 200 mm or more and the counter part is provided on one side of the raceway groove of the inner ring, the resin cage is annularly connected on the counter part side of the inner ring. It is a crown type provided with a pocket for holding the ball between a plurality of pillars extending from the annular part to the bearing center side, and the back side end surface opposite to the bearing center side of the annular part is flat and smooth. Adopted a surface configuration.

すなわち、樹脂製の保持器を、内輪のカウンタ部側で環状に連なる環状部から軸受中心側に延びる複数の柱部の間に、ボールを保持するポケットを設けた冠型のものとすることにより、保持器が外輪のカウンタ部側へ張り出さないようにして、外輪のカウンタ部側に十分な空きスペースを確保可能とするとともに、冠型保持器の環状部の背面側端面をぬすみのない平坦面とすることにより、冠型保持器の環状部の剛性を高めて、外輪を分離したアセンブリ状態で、ボールが内輪のカウンタ部へ乗り上げて落下することのないようにした。   That is, by making the cage made of resin a crown type provided with a pocket for holding a ball between a plurality of pillars extending from an annular part that is annularly connected on the counter part side of the inner ring to the bearing center side The retainer does not protrude to the counter part side of the outer ring, so that a sufficient free space can be secured on the counter part side of the outer ring, and the end face on the back side of the annular part of the crown type retainer is flat and smooth. By using the surface, the rigidity of the annular portion of the crown type cage is increased so that the ball does not ride on the counter portion of the inner ring and fall in the assembled state in which the outer ring is separated.

前記樹脂製の保持器を、ガラス繊維または炭素繊維で強化したものとすることにより、冠型保持器の環状部の剛性をより高めることができる。   By making the resin cage reinforced with glass fiber or carbon fiber, the rigidity of the annular portion of the crown type cage can be further increased.

本発明のアンギュラ玉軸受は、樹脂製の保持器を、内輪のカウンタ部側で環状に連なる環状部から軸受中心側に延びる複数の柱部の間に、ボールを保持するポケットを設けた冠型のものとし、環状部の軸受中心側と反対側の背面側端面をぬすみのない平坦面としたので、外輪のカウンタ部側に十分な空きスペースを確保できるとともに、外輪を分離したアセンブリ状態で、ボールが内輪のカウンタ部へ乗り上げて落下するのを防止することができる。   The angular contact ball bearing of the present invention is a crown type in which a resin cage is provided with a pocket for holding a ball between a plurality of column portions extending from an annular portion that is annularly connected on the counter portion side of the inner ring to the bearing center side. As the back side end face opposite the bearing center side of the annular part is a flat surface without dullness, it is possible to secure a sufficient free space on the counter part side of the outer ring and in an assembly state where the outer ring is separated, It is possible to prevent the ball from riding on the counter part of the inner ring and falling.

前記樹脂製の保持器を、ガラス繊維または炭素繊維で強化したものとすることにより、冠型保持器の環状部の剛性をより高めることができる。   By making the resin cage reinforced with glass fiber or carbon fiber, the rigidity of the annular portion of the crown type cage can be further increased.

以下、図面に基づき、本発明の実施形態を説明する。このアンギュラ玉軸受は搬送用ロボットの減速機の主軸を支持する外輪分離型のものであり、図１に示すように、内輪１と外輪２の軌道溝１ａ、２ａ間に配列されたボール３が樹脂製の冠型保持器４で保持され、保持器４で保持したボール３を内輪１と一体にしたアセンブリ状態で、あとから外輪２を組み付けるために、外輪２の軌道溝２ａの片側に、ほとんど盛り上がりのないカウンタ部２ｂが設けられ、このカウンタ部２ｂと反対側で、内輪１の軌道溝１ａの片側にも、少し盛り上がったカウンタ部１ｂが設けられている。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. This angular ball bearing is of the separated outer ring type that supports the main shaft of the speed reducer of the transport robot. As shown in FIG. 1, the balls 3 arranged between the raceway grooves 1a and 2a of the inner ring 1 and the outer ring 2 are arranged. In an assembled state in which the ball 3 held by the resin crown-shaped cage 4 and held by the cage 4 is integrated with the inner ring 1, to assemble the outer ring 2 later, on one side of the raceway groove 2a of the outer ring 2, There is provided a counter part 2b that hardly rises, and a counter part 1b that is slightly raised is provided on one side of the raceway groove 1a of the inner ring 1 on the side opposite to the counter part 2b.

前記外輪２の外径寸法は２００ｍｍ以上とされ、そのカウンタ部２ｂが短く形成されるとともに、このカウンタ部２ｂ側へ冠型保持器４は張り出していないので、外輪２のカウンタ部２ｂ側に広いスペースが空けられ、この広いスペースに他の部品Ａが組み込み可能とされている。   The outer diameter of the outer ring 2 is 200 mm or more, the counter part 2b is formed short, and the crown-shaped cage 4 does not protrude toward the counter part 2b, so that the outer ring 2 is wide on the counter part 2b side. A space is made available, and another part A can be assembled in this wide space.

前記冠型保持器４は、ガラス繊維（配合率：２５体積％）で強化されたポリアミド樹脂で形成され、図２（ａ）、（ｂ）に示すように、内輪１のカウンタ部１ｂ側で環状に連なる環状部４ａから軸受中心側に延びる複数の柱部４ｂの間に、ボール３を保持するポケット５が設けられ、環状部４ａの軸受中心側と反対側の背面側端面４ｃがぬすみのない平坦面とされている。   The crown-shaped cage 4 is formed of a polyamide resin reinforced with glass fibers (mixing ratio: 25% by volume), and on the counter portion 1b side of the inner ring 1 as shown in FIGS. A pocket 5 for holding the ball 3 is provided between a plurality of pillar portions 4b extending from the annular portion 4a that extends in a ring shape toward the bearing center side, and the back side end surface 4c opposite to the bearing center side of the annular portion 4a is thin. There is no flat surface.

図２（ａ）、（ｂ）に示したように、環状部４ａの背面側端面４ｃを平坦面とした冠型保持器４（実施例）と、図６（ａ）、（ｂ）に示す環状部４ａの背面側端面４ｃにぬすみ４ｄを設けた従来の冠型保持器４（比較例）とを用意した。これらの実施例と比較例の冠型保持器４を、図３に示すように、上向の各ポケット５にボール３を保持した状態で、水平にした環状部４ａを円周方向の位相間隔が１８０°の２点で支持し、支持点から９０°離れた位相位置における各環状部４ａの撓み量δをハイトゲージで測定した。実施例と比較例の保持器の寸法は、いずれも、外径２４８ｍｍ、内径２２８ｍｍ、軸方向幅１５．６ｍｍとし、比較例の保持器も、実施例のものと同様に、ガラス繊維（配合率：２５体積％）で強化されたポリアミド樹脂で形成されたものとした。   As shown in FIGS. 2 (a) and 2 (b), the crown type retainer 4 (example) in which the back side end face 4c of the annular portion 4a is a flat surface, and FIGS. 6 (a) and 6 (b). A conventional crown-shaped cage 4 (comparative example) in which a dullness 4d was provided on the back side end surface 4c of the annular portion 4a was prepared. As shown in FIG. 3, the crown-shaped cage 4 of these examples and the comparative example is arranged in a state where the balls 3 are held in the upward pockets 5 and the annular portion 4a that is leveled is arranged in the circumferential phase interval. Was supported at two points of 180 °, and the deflection amount δ of each annular portion 4a at a phase position 90 ° away from the support point was measured with a height gauge. The dimensions of the cages of the example and the comparative example are all 248 mm in outer diameter, 228 mm in inner diameter, and 15.6 mm in the axial width, and the cage of the comparative example is made of glass fiber (mixing ratio) as in the example. : 25% by volume) of the polyamide resin reinforced.

上記比較例の保持器の撓み量δが３０ｍｍであったのに対して、実施例の保持器の撓み量δは、比較例の撓み量δの１／７弱の４ｍｍであった。この測定結果より、環状部にぬすみのない実施例の冠型保持器は、環状部の剛性が著しく高くなることが確認された。   The deflection amount δ of the cage of the comparative example was 30 mm, whereas the deflection amount δ of the cage of the example was 4 mm, which is slightly less than 1/7 of the deflection amount δ of the comparative example. From this measurement result, it was confirmed that the rigidity of the annular portion of the crown type cage of the example in which the annular portion has no dullness is remarkably increased.

上記実施例と比較例の材質と寸法の冠型保持器を用いたアンギュラ玉軸受について、図４に示すように、外輪を分離したアセンブリ状態で、内輪１のカウンタ部１ｂを下向きにしたときの冠型保持器４の撓み変形を、有限要素法を用いた数値計算によって解析し、この解析結果からボール３が内輪１のカウンタ部１ｂへ乗り上げて落下するか否かを検討した。なお、冠型保持器４を形成するガラス繊維で強化されたポリアミド樹脂のヤング率は６０００ＭＰａ、ポアソン比は０．３５とした。   As shown in FIG. 4, the angular ball bearings using the crown type cages of the materials and dimensions of the above examples and comparative examples are shown in FIG. 4 when the counter part 1 b of the inner ring 1 is faced down in the assembled state with the outer ring separated. The bending deformation of the crown-shaped cage 4 was analyzed by numerical calculation using a finite element method, and from this analysis result, it was examined whether or not the ball 3 rides on the counter portion 1b of the inner ring 1 and falls. The Young's modulus of the polyamide resin reinforced with glass fibers forming the crown-shaped cage 4 was 6000 MPa, and the Poisson's ratio was 0.35.

前記ボール３に作用する力は、図４に示したように、各ボール３と保持器４の自重による垂直下向きの重力Ｇと、内輪１から受ける斜め上向きの内輪反力Ｆと、保持器４の弾性力による水平な径方向内向きの保持器反力Ｅとからなり、内輪反力Ｆの垂直な軸方向成分Ｆｓｉｎθは重力Ｇと釣り合う。したがって、内輪反力Ｆの径方向外向き成分Ｆｃｏｓθと径方向内向きの保持器反力Ｅとを比較したときに、
Ｆｃｏｓθ＞Ｅであれば、ボール３はカウンタ部１ｂ側へ押し出され、
Ｆｃｏｓθ＝Ｅであれば、ボール３はその場から動かず、
Ｆｃｏｓθ＜Ｅであれば、ボール３は軌道溝１ａ側へ押し戻されることになる。 As shown in FIG. 4, the force acting on the balls 3 includes vertically downward gravity G due to the weight of each ball 3 and the cage 4, an obliquely upward inner ring reaction force F received from the inner ring 1, and the cage 4. The vertical axial component Fsinθ of the inner ring reaction force F balances with the gravity G. Therefore, when comparing the radially outward component Fcosθ of the inner ring reaction force F and the radially inward cage reaction force E,
If Fcos θ> E, the ball 3 is pushed out to the counter unit 1b side,
If Fcos θ = E, the ball 3 does not move from the spot,
If Fcos θ <E, the ball 3 is pushed back toward the raceway groove 1a.

図５は、図４におけるボール３の径方向位置Ｘを、軌道溝１ａの底（Ｘ＝０ｍｍ）から軌道溝１ａとカウンタ部１ｂとの境界位置Ｐ（Ｘ＝１．４７ｍｍ）まで変化させたときに、上記有限要素法による数値計算で求められた、内輪反力Ｆの径方向外向き成分Ｆｃｏｓθと径方向内向きの保持器反力Ｅの値を示す。Ｆｃｏｓθの値は、実施例と比較例が同じ値となり、Ｘ＝０ｍｍの位置から徐々に大きくなる。一方、Ｅの値は実施例、比較例ともＸ＝０．３３ｍｍの辺りから生じ、ぬすみがなく剛性の高い実施例の保持器４のＥの値は急勾配で大きくなり、Ｘ＝０．４３ｍｍ辺りでＦｃｏｓθの値よりも大きくなる。したがって、実施例の保持器４を用いた場合は、ボール３はＸ＝０．４３ｍｍ辺りよりもカウンタ部１ｂ側へ移動することはなく、カウンタ部１ｂへ乗り上げる恐れもない。これに対して、ぬすみのある剛性の低い比較例の保持器４のＥの値は緩やかな勾配で大きくなり、カウンタ部１ｂとの境界位置ＰまでＦｃｏｓθの値を越えることはない。したがって、比較例の保持器４を用いた場合は、ボール３がカウンタ部１ｂに乗り上げて落下することになる。   5, the radial position X of the ball 3 in FIG. 4 is changed from the bottom of the raceway groove 1a (X = 0 mm) to the boundary position P (X = 1.47 mm) between the raceway groove 1a and the counter portion 1b. Sometimes, the values of the radially outward component Fcosθ of the inner ring reaction force F and the radially inward cage reaction force E obtained by numerical calculation by the finite element method are shown. The value of Fcos θ is the same value in the example and the comparative example, and gradually increases from the position of X = 0 mm. On the other hand, the value of E arises from around X = 0.33 mm in both the example and the comparative example, and the value of E of the cage 4 of the example having no dullness and high rigidity increases steeply and X = 0.43 mm. The value is larger than the value of Fcos θ. Therefore, when the cage 4 of the embodiment is used, the ball 3 does not move to the counter unit 1b side than around X = 0.43 mm, and there is no fear of riding on the counter unit 1b. On the other hand, the value of E of the cage 4 of the comparative example with thin rigidity and low rigidity increases with a gentle gradient, and does not exceed the value of Fcos θ until the boundary position P with the counter unit 1b. Therefore, when the cage 4 of the comparative example is used, the ball 3 rides on the counter portion 1b and falls.

上述した実施形態では、冠型保持器を形成する樹脂をポリアミド樹脂としてガラス繊維で強化したが、冠型保持器を形成する樹脂には、ポリアミドイミド樹脂、ポリイミド樹脂、ポリフェニレンスルフィド樹脂等、任意の樹脂を用いることができ、これらを繊維強化する場合は、炭素繊維で強化することもできる。   In the embodiment described above, the resin that forms the crown-shaped cage is reinforced with glass fiber as a polyamide resin. However, the resin that forms the crown-shaped cage may be any resin such as a polyamide-imide resin, a polyimide resin, or a polyphenylene sulfide resin. Resins can be used, and when these are reinforced with fibers, they can be reinforced with carbon fibers.

アンギュラ玉軸受の実施形態を示す縦断面図Longitudinal sectional view showing an embodiment of the angular ball bearing ａは図１の冠型保持器の部分展開平面図、ｂはａのIIb−IIb線に沿った断面図a is a partially developed plan view of the crown type cage shown in FIG. 1, and b is a sectional view taken along line IIb-IIb of a. 冠型保持器の撓み測定方法を説明する正面図Front view for explaining a method for measuring the deflection of a crown type cage 外輪を分離したアセンブリ状態で冠型保持器の撓み変形を計算するモデルを説明する縦断面図Longitudinal sectional view explaining a model for calculating the bending deformation of the crown type cage in the assembled state with the outer ring separated 図４のモデルで計算されたボールの径方向位置とボールに作用する反力の関係を示すグラフ4 is a graph showing the relationship between the radial position of the ball calculated by the model of FIG. 4 and the reaction force acting on the ball. ａは従来の冠型保持器の部分展開平面図、ｂはａのVIb−VIb線に沿った断面図a is a partially developed plan view of a conventional crown type cage, and b is a sectional view taken along line VIb-VIb of a. 従来のリング型保持器を用いたアンギュラ玉軸受を示す縦断面図Longitudinal sectional view showing an angular contact ball bearing using a conventional ring cage

符号の説明Explanation of symbols

１ 内輪
２ 外輪
１ａ、２ａ 軌道溝
１ｂ、２ｂ カウンタ部
３ ボール
４ 冠型保持器
４ａ 環状部
４ｂ 柱部
４ｃ 背面側端面
５ ポケット DESCRIPTION OF SYMBOLS 1 Inner ring 2 Outer ring 1a, 2a Raceway groove 1b, 2b Counter part 3 Ball 4 Crown type holder 4a Annular part 4b Column part 4c Back side end face 5 Pocket

Claims (2)

内輪と外輪の軌道溝間に配列されるボールが、外輪を分離した状態で内輪と一体に樹脂製の保持器で保持される外輪分離型で、前記外輪の外径寸法が２００ｍｍ以上とされ、前記内輪の軌道溝の片側にカウンタ部が設けられたアンギュラ玉軸受において、前記樹脂製の保持器を、前記内輪のカウンタ部側で環状に連なる環状部から軸受中心側に延びる複数の柱部の間に、前記ボールを保持するポケットを設けた冠型のものとし、前記環状部の軸受中心側と反対側の背面側端面をぬすみのない平坦面としたことを特徴とするアンギュラ玉軸受。   A ball arranged between the raceway grooves of the inner ring and the outer ring is an outer ring separation type in which the outer ring is separated and held by a resin cage integrally with the inner ring, and the outer diameter of the outer ring is 200 mm or more, In the angular ball bearing in which a counter part is provided on one side of the raceway groove of the inner ring, the resin cage is formed of a plurality of column parts extending from the annular part annularly connected to the bearing center side from the annular part on the counter part side of the inner ring. An angular contact ball bearing characterized in that it is of a crown type provided with a pocket for holding the ball in between, and the back side end face on the opposite side to the bearing center side of the annular part is a flat surface without dullness. 前記樹脂製の保持器を、ガラス繊維または炭素繊維で強化したものとした請求項１に記載のアンギュラ玉軸受。   The angular contact ball bearing according to claim 1, wherein the resin cage is reinforced with glass fiber or carbon fiber.
JP2006227888A 2006-08-24 2006-08-24 Angular ball bearing Pending JP2008051206A (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102678741A (en) * 2012-05-17 2012-09-19 宁波万丰轴承有限公司 Nonstandard thin-wall waterproof bearing
CN103016546A (en) * 2012-12-10 2013-04-03 中山市盈科轴承制造有限公司 Outer spherical surface angle contact ball bearing with pedestal
WO2014122791A1 (en) * 2013-02-05 2014-08-14 Ntn株式会社 Rolling bearing retainer and method for manufacturing such retainer

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58102823A (en) * 1981-12-14 1983-06-18 Koyo Seiko Co Ltd Manufacture of synthetic resinous retainer
JPS5981814U (en) * 1982-11-25 1984-06-02 日本精工株式会社 Cage for ball bearings
JPH0656516U (en) * 1993-01-20 1994-08-05 日本精工株式会社 Cage for thrust ball bearing
JPH09264321A (en) * 1996-03-29 1997-10-07 Ntn Corp Angular ball bearing
JPH1019045A (en) * 1996-07-03 1998-01-20 Koyo Seiko Co Ltd Deep groove ball bearing and supercharger employing it
JP2005009643A (en) * 2003-06-20 2005-01-13 Nsk Ltd Nonseparable angular contact ball bearing
JP2005147372A (en) * 2003-11-20 2005-06-09 Nachi Fujikoshi Corp Tandem duplex angular ball bearing and separation method thereof
JP2006105384A (en) * 2004-09-08 2006-04-20 Nsk Ltd Double row ball bearing
JP2006153094A (en) * 2004-11-26 2006-06-15 Nsk Ltd Ball bearing and rotary table device for machine tool using ball bearing

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58102823A (en) * 1981-12-14 1983-06-18 Koyo Seiko Co Ltd Manufacture of synthetic resinous retainer
JPS5981814U (en) * 1982-11-25 1984-06-02 日本精工株式会社 Cage for ball bearings
JPH0656516U (en) * 1993-01-20 1994-08-05 日本精工株式会社 Cage for thrust ball bearing
JPH09264321A (en) * 1996-03-29 1997-10-07 Ntn Corp Angular ball bearing
JPH1019045A (en) * 1996-07-03 1998-01-20 Koyo Seiko Co Ltd Deep groove ball bearing and supercharger employing it
JP2005009643A (en) * 2003-06-20 2005-01-13 Nsk Ltd Nonseparable angular contact ball bearing
JP2005147372A (en) * 2003-11-20 2005-06-09 Nachi Fujikoshi Corp Tandem duplex angular ball bearing and separation method thereof
JP2006105384A (en) * 2004-09-08 2006-04-20 Nsk Ltd Double row ball bearing
JP2006153094A (en) * 2004-11-26 2006-06-15 Nsk Ltd Ball bearing and rotary table device for machine tool using ball bearing

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102678741A (en) * 2012-05-17 2012-09-19 宁波万丰轴承有限公司 Nonstandard thin-wall waterproof bearing
CN102678741B (en) * 2012-05-17 2015-01-21 宁波万丰轴承有限公司 Nonstandard thin-wall waterproof bearing
CN103016546A (en) * 2012-12-10 2013-04-03 中山市盈科轴承制造有限公司 Outer spherical surface angle contact ball bearing with pedestal
CN103016546B (en) * 2012-12-10 2015-07-29 中山市盈科轴承制造有限公司 A kind of band base spherical outside surface angular contact ball bearing
WO2014122791A1 (en) * 2013-02-05 2014-08-14 Ntn株式会社 Rolling bearing retainer and method for manufacturing such retainer
JP2014152788A (en) * 2013-02-05 2014-08-25 Ntn Corp Rolling bearing
KR20150114975A (en) * 2013-02-05 2015-10-13 엔티엔 가부시키가이샤 Rolling bearing retainer and method for manufacturing such retainer
CN104981619A (en) * 2013-02-05 2015-10-14 Ntn株式会社 Rolling bearing retainer and method for manufacturing such retainer
US9771980B2 (en) 2013-02-05 2017-09-26 Ntn Corporation Rolling bearing retainer and method for manufacturing such retainer
TWI603010B (en) * 2013-02-05 2017-10-21 Ｎｔｎ股份有限公司 Retainer for rolling contact bearing assembly
CN104981619B (en) * 2013-02-05 2018-06-12 Ntn株式会社 Cage for rolling bearing
KR101991300B1 (en) * 2013-02-05 2019-06-20 엔티엔 가부시키가이샤 Rolling bearing retainer

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