JP2004293563A - Ball bearing - Google Patents

Ball bearing Download PDF

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Publication number
JP2004293563A
JP2004293563A JP2003082633A JP2003082633A JP2004293563A JP 2004293563 A JP2004293563 A JP 2004293563A JP 2003082633 A JP2003082633 A JP 2003082633A JP 2003082633 A JP2003082633 A JP 2003082633A JP 2004293563 A JP2004293563 A JP 2004293563A
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Japan
Prior art keywords
inner ring
ball bearing
lip
ring
raceway surface
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Pending
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JP2003082633A
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Japanese (ja)
Inventor
Shinji Fujita
伸二 藤田
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Koyo Seiko Co Ltd
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Koyo Seiko Co Ltd
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Priority to JP2003082633A priority Critical patent/JP2004293563A/en
Publication of JP2004293563A publication Critical patent/JP2004293563A/en
Pending legal-status Critical Current

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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
    • 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
    • F16C33/7853—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 one or more sealing lips to contact the inner race
    • 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
    • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
    • F16C33/782—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region
    • 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
    • F16C19/166—Four-point-contact ball bearings

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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compact ball bearing at a low price, which is capable of preventing grease leakage. <P>SOLUTION: In the end of the inner ring 2 periphery of the bearing in an axial direction, two-step parts 13, 14, 15, 16 with large and small diameters smaller than the shoulder diameter of the trace surface of the inner ring 2 are formed, and the sub lips 35, 36 of seal members 18, 19 are configured to be released to the step parts 13, 15 with large diameters. Thus, the distance between the circular part 39 of a crown holder 7 and the sub lip 35 is enlarged so as not to cause interference between them even when the dimensions of an outer ring 1 and the inner ring 2 is reduced. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

【０００１】
【発明の属する技術分野】
本発明は、玉軸受に関する。
【０００２】
【従来の技術】
従来、玉軸受としては、例えば、特開２００２−１５５９５１号公報（特許文献１）に示された４点接触玉軸受がある。この玉軸受は、外輪の軌道面と、内輪の軌道面との間に、冠形保持器によって保持された玉を、周方向に一定の間隔に複数個配置している。上記外輪と内輪の軸方向の両端部には環状溝が形成されている。
【０００３】
また、上記玉軸受の上記外輪の内周面の軸方向の端部と上記内輪の外周面の軸方向の端部の間にはシール部材が配置されている。このシール部材は、シール部材の一端部を上記外輪の環状溝に固定している一方、シール部材の他端部の副リップを上記内輪の外周面に近接させて、上記副リップと上記内輪の外周面との間にラビリンスシールを構成すると共に、シール部材の他端部の主リップを上記内輪の環状溝の側面に摺接させて、外輪と内輪の間をシールしている。上記シール部材は、外輪と内輪の間に充填されているグリースが外部に漏れ出たり、外部の異物が外輪と内輪の間に入り込んだりするのを防止している。
【０００４】
【特許文献１】
特開２００２−１５５９５１号公報
【０００５】
【発明が解決しようとする課題】
しかしながら、上記従来の玉軸受では、上記シール部材の他端部の副リップを上記内輪の外周面に近接させるようにして、上記副リップと上記内輪の外周面との間にラビリンスシールを構成しているので、上記冠形保持器の環状部が存在する側で、上記冠形保持器の環状部と上記シール部材の副リップ部とが接近して、グリースがシール部材のリップ部周辺に溜まり易くなって、このリップ部周辺のグリースの圧力が大きくなって、グリース漏れが起こるという問題がある。
【０００６】
また、上記グリース漏れの問題を回避するために、玉軸受の軸方向の寸法を大きくして、上記冠形保持器の環状部と上記副リップとの間の隙間を充分に確保すると、玉軸受が大型化すると共に、内輪および外輪の材料費が増大して玉軸受の製造コストが増大するという問題がある。
【０００７】
そこで、本発明の目的は、グリース漏れが起こらず、かつ、安価でコンパクトな玉軸受を提供することにある。
【０００８】
【課題を解決するための手段】
上記目的を達成するため、請求項１の発明の玉軸受は、外輪と、内輪と、上記外輪の軌道面と上記内輪の軌道面との間に配置された玉と、この玉を保持する保持器と、上記外輪の内周面の軸方向の少なくとも一方の端部と上記内輪の外周面の軸方向の端部との間をシールするシール部材とを備えた玉軸受において、
上記内輪の外周面の軸方向の端部に、上記内輪の軌道面の肩径よりも小さな大径と小径との二段の段部を形成し、
上記大径の段部と、上記シール部材の副リップとの間にラビリンスシールを構成すると共に、上記小径の段部の側壁に上記シール部材の主リップを摺動させていることを特徴としている。
【０００９】
上記請求項１の発明の玉軸受によれば、上記内輪の外周面の軸方向の端部に、上記内輪の軌道面の肩径よりも小さな大径と小径との二段の段部を形成し、上記副リップを上記大径の段部に逃がすような構成にしたので、上記保持器の環状部と副リップとの距離を従来に比べて格段に大きくできて、玉軸受の軸方向の寸法を小さくしても、上記保持器の環状部と上記副リップが干渉することがない。したがって、内輪および外輪の軸方向の寸法を小さくすることができて玉軸受をコンパクトにできると共に、外輪および内輪の材料費を低減できて玉軸受の製造コストを小さくできる。
【００１０】
また、上記請求項１の発明の玉軸受によれば、上記副リップを上記大径の段部に逃がすような構成にして、上記保持器の環状部と副リップとの距離を大きくしたので、上記副リップと上記保持器の環状部との間にグリースが入り込む十分な空間を確保できて、グリースがシール部材の主リップの周辺に集中的に溜まることがない。したがって、シール部材の主リップ周辺でのグリースの圧力が高くなることがないので、シール部材と上記内輪の間からのグリース漏れが起こることがない。
【００１１】
また、請求項２の発明の玉軸受は、請求項１に記載の玉軸受において、上記外輪と上記内輪は、上記外輪の軌道面と上記内輪の軌道面のセンターを含む面に対して、略面対称になっていることを特徴としている。
【００１２】
上記請求項２の発明の玉軸受によれば、上記外輪と上記内輪は、上記外輪の軌道面と上記内輪の軌道面のセンターを含む面に対して、略面対称になっているので、非対称な場合と比べて、上記外輪および内輪の汎用性を高くして、玉軸受の生産性を向上させることができる。
【００１３】
また、請求項３の発明の玉軸受は、請求項１または２に記載の玉軸受において、上記保持器の環状部の少なくとも一部と、上記副リップの少なくとも一部が径方向に重なることを特徴としている。
【００１４】
上記請求項３の発明の玉軸受によれば、上記保持器の環状部の少なくとも一部と、上記副リップの少なくとも一部とが径方向で重なる構成にしたので、上記外輪および内輪の軸方向の寸法を更に小さくできて、外輪および内輪の材料費を更に低減できる。したがって、玉軸受を更にコンパクトにできると共に、玉軸受の製造コストを更に小さくできる。
【００１５】
【発明の実施の形態】
以下、本発明を図示の実施の形態により詳細に説明する。
【００１６】
図１は、本発明の玉軸受の一実施形態としての４点接触玉軸受の軸方向の断面図である。この４点接触玉軸受は、外輪１の軌道面１ａと、内輪２の軌道面２ａとの間に、冠形保持器７によって保持された玉３を、周方向に一定の間隔に複数個配置している。
【００１７】
上記外輪１は、上記外輪１の軌道面１ａと内輪２の軌道面２ａのセンターを含む平面Ａに対して略左右対称になっており、外輪１の内周面の軸方向の両端部には、環状溝１０，１１が形成されている。また、上記外輪１の軌道面１ａは、平面Ａに対して略左右対称な左側部分と右側部分とから成っており、上記左側部分は玉３と点Ｐ１で接触し、上記右側部分は玉３と点Ｐ２で接触している。
【００１８】
一方、上記内輪２は、外輪１の軌道面１ａと内輪２の軌道面２ａのセンターを含む平面Ａに対して略左右対称になっており、内輪２の外周面の軸方向の両端部の夫々には、内輪２の軌道面２ａの肩径よりも小さな大径と小径との二段の段部１３，１４および１５，１６が形成されている。上記内輪２の両端に形成された二段の段部の内で玉側の大径段部１３，１５の大部分は、冠形保持器７の環状部３９の一部と径方向で重なっている。また、上記内輪２の軌道面２ａは、平面Ａに対して略左右対称な左側部分と右側部分から成っており、上記左側部分は玉３とＰ３で接触し、上記右側部分は玉３とＰ４で接触している。
【００１９】
また、この４点接触玉軸受の軸方向の両端部の外輪１の内周面と内輪２の外周面との間にはシール部材１８，１９が配置されている。このシール部材１８，１９の夫々は、芯金部２０，２１とリップ部２３，２４とから成っている。
【００２０】
上記シール部材１８，１９の夫々は、シール部材１８，１９の一端部を外輪１の環状溝に固定する一方、シール部材１８，１９の他端部の副リップ３５，３６を内輪２の大径段部１３，１５に近接させて、副リップ３５，３６と内輪２の大径段部１３，１５との間にラビリンスシールを構成すると共に、シール部材１８，１９の他端部の主リップ３７，３８を内輪２の小径段部１４，１６の玉側の側面に摺接させて、外輪１と内輪２との間をシールしている。上記冠形保持器７の環状部３９と、平面Ａに対して保持器側のシール部材１８の副リップ３５の先端部とは、径方向で重なるようになっている。上記シール部材１８，１９は、外輪１８と内輪１９の間に充填されているグリースが外部に漏れ出たり、外部の異物が外輪１８と内輪１９の間に入り込んだりするのを防止している。
【００２１】
図２は、上記内輪２の保持器側の二段の段部１３，１４の周辺の拡大図である。
【００２２】
図２において、点線Ｃは、大径段部を形成しない従来の内輪の表面を示し、点線Ｄは、大径段部を形成しない従来のシール部材の副リップの存在位置を示している。
【００２３】
図２に示すように、上記冠形保持器７は、環状部３８と副リップ３７との間の距離が大きくなるように、環状部３９の副リップ側の角部が面取りされ、そこに斜面４３が形成されている。
【００２４】
また、図２に示すように、大径段部１３に近接して配置されると共に、大径段部１３との間にラビリンスシールを形成している副リップ３５と、冠形保持器７の環状部３９との間隔は、存在位置が点線Ｄで示される大径段部が形成されない従来の副リップと、冠形保持器７の環状部３９との間隔よりも大きくなっている。
【００２５】
上記実施形態の玉軸受によれば、内輪２の外周面の軸方向の端部に、内輪２の軌道面の肩径よりも小さな大径と小径との二段の段部１３，１４および１５，１６を形成し、副リップ３５，３６を大径の段部１３，１５に逃がすような構成にしたので、冠形保持器７の環状部３９と副リップ３５との距離が、従来の玉軸受よりも格段に大きくなって、玉軸受の軸方向の寸法を小さくしても、冠形保持器７の環状部３９と副リップ３５が近接することがない。したがって、内輪１および外輪２の軸方向の寸法を小さくできて玉軸受をコンパクトにできると共に、内輪１および外輪２の材料費を低減できて玉軸受の製造コストを低減できる。
【００２６】
また、上記実施形態の玉軸受によれば、副リップ３５，３６を大径の段部１３，１５に逃がすような構成にして、冠形保持器７の環状部３９と副リップ３５との距離を大きくしたので、副リップ３５と冠形保持器７の環状部３９との間にグリースが入り込む十分な空間を確保することができて、グリースがシール部材１８のシール位置の周辺に集中的に溜まることがない。したがって、シール部材１８の主リップ３７周辺でのグリースの圧力が高くなることがないので、シール部材１８と内輪２の間からグリースが漏れることがない。
【００２７】
また、上記実施形態の玉軸受によれば、外輪１と内輪２は、外輪１の軌道面１ａと内輪２の軌道面２ａのセンターを含む平面Ａに対して、略面対称になっているので、非対称な場合と比べて、外輪１および内輪２の汎用性を高くして、玉軸受の生産性を格段に上げることができる。
【００２８】
また、上記実施形態の玉軸受によれば、冠形保持器７の環状部３９の一部と副リップ３５の先端部とが径方向で重なるような構成にしたので、外輪１および内輪２の軸方向の寸法を更に小さくできて、玉軸受を更にコンパクトにできる。
【００２９】
尚、上記実施形態の玉軸受では、保持器として冠形保持器７を採用し、かつ、内輪２の外周面の両端部に平面Ａに対して略面対称に２段の段部１３，１４および１５，１６を設けたが、この発明の玉軸受では、保持器として冠形保持器を採用し、かつ、内輪の外周面の平面Ａに対する保持器側の端部に２段の段部を設けると共に、内輪の外周面の平面Ａに対する反対側の段部に主リップ用の１段の段部のみを設けるようにしても良い。また、この発明の玉軸受では、保持器として、二つの環状部の間が複数の柱部で接続されて隣接する柱部の間にポケットが形成された保持器を採用すると共に、内輪の外周面の両端部に略左右対称に２段の段部を設けても良い。
【００３０】
また、上記実施形態の玉軸受では、冠形保持器７の角部を面取りしたが、この発明の玉軸受では、保持器の角部を面取りしなくても良い。
【００３１】
また、上記実施形態の玉軸受では、玉軸受として４点接触玉軸受を採用して、この発明を、４点接触玉軸受で実践したが、この発明を、単列の深溝玉軸受や３点接触玉軸受等の４点接触玉軸受以外の玉軸受で実践しても良い。
【００３２】
【発明の効果】
以上より明らかなように、請求項１の発明の玉軸受によれば、内輪の外周面の軸方向の端部に、上記内輪の軌道面の肩径よりも小さな大径と小径との二段の段部を形成して、シール部材の副リップを上記大径の段部に逃がすような構成にしたので、保持器の環状部と上記副リップとの距離を大きくできて、玉軸受の軸方向の寸法を小さくしても保持器の環状部と上記副リップが干渉することがない。したがって、玉軸受をコンパクトにできると共に、玉軸受の製造コストを低減できる。
【００３３】
また、請求項１の発明の玉軸受によれば、上記シール部材の副リップを上記大径の段部に逃がすような構成にして、保持器の環状部と上記副リップとの距離を大きくしたので、上記副リップと上記保持器の環状部との間に十分な空間を確保できて、グリース漏れを抑制できる。
【００３４】
また、請求項２の発明の玉軸受によれば、外輪と内輪は、上記外輪の軌道面と上記内輪の軌道面のセンターを含む面に対して、略面対称になっているので、上記外輪および内輪の汎用性を高くして、玉軸受の生産性を格段に向上させることができる。
【００３５】
また、請求項３の発明の玉軸受によれば、上記保持器の環状部と、上記副リップの少なくとも一部とが径方向で重なっているので、玉軸受を軸方向に更にコンパクトにできて、玉軸受の製造コストを更に低減できる。
【図面の簡単な説明】
【図１】本発明の一実施形態の玉軸受の軸方向の断面図である。
【図２】上記玉軸受の内輪の保持器側の二段の段部の周辺の拡大図である
【符号の説明】
１ 外輪
２ 内輪
３ 玉
７ 冠形保持器
１３，１５ 大径段部
１４，１６ 小径段部
１８，１９ シール部材
２０，２１ 芯金部
２３，２４ リップ部
３５，３６ 副リップ
３７，３８ 主リップ
３９ 環状部
Ａ 平面[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a ball bearing.
[0002]
[Prior art]
Conventionally, as a ball bearing, for example, there is a four-point contact ball bearing disclosed in JP-A-2002-155951 (Patent Document 1). In this ball bearing, a plurality of balls held by a crown-shaped retainer are arranged at regular intervals in a circumferential direction between a raceway surface of an outer race and a raceway surface of an inner race. Annular grooves are formed at both axial ends of the outer ring and the inner ring.
[0003]
In addition, a seal member is disposed between an axial end of an inner peripheral surface of the outer race of the ball bearing and an axial end of an outer peripheral surface of the inner race. The seal member has one end of the seal member fixed to the annular groove of the outer ring, and the sub lip of the other end of the seal member is brought close to the outer peripheral surface of the inner ring, so that the sub lip and the inner ring are A labyrinth seal is formed between the outer ring and the outer peripheral surface, and a main lip at the other end of the seal member is slidably contacted with a side surface of the annular groove of the inner ring to seal between the outer ring and the inner ring. The seal member prevents the grease filled between the outer ring and the inner ring from leaking to the outside and preventing external foreign matter from entering between the outer ring and the inner ring.
[0004]
[Patent Document 1]
JP-A-2002-155951
[Problems to be solved by the invention]
However, in the above-mentioned conventional ball bearing, a labyrinth seal is formed between the sub lip and the outer peripheral surface of the inner ring such that the sub lip at the other end of the seal member is close to the outer peripheral surface of the inner ring. Therefore, on the side where the annular portion of the crown-shaped cage exists, the annular portion of the crown-shaped cage and the auxiliary lip of the seal member approach each other, and grease accumulates around the lip of the seal member. As a result, there is a problem that the grease pressure around the lip portion increases, and grease leakage occurs.
[0006]
In order to avoid the problem of grease leakage, the axial dimension of the ball bearing is increased to sufficiently secure a gap between the annular portion of the crowned cage and the auxiliary lip. However, there is a problem that the material cost of the inner ring and the outer ring increases, and the manufacturing cost of the ball bearing increases.
[0007]
Accordingly, an object of the present invention is to provide an inexpensive and compact ball bearing that does not cause grease leakage.
[0008]
[Means for Solving the Problems]
In order to achieve the above object, a ball bearing according to the first aspect of the present invention provides an outer ring, an inner ring, a ball disposed between a raceway surface of the outer ring and a raceway surface of the inner ring, and a holding member for holding the ball. A ball bearing comprising: a seal member that seals between at least one axial end of the inner peripheral surface of the outer race and the axial end of the outer peripheral surface of the inner race.
At the axial end of the outer peripheral surface of the inner ring, a two-step portion having a large diameter and a small diameter smaller than the shoulder diameter of the raceway surface of the inner ring is formed,
A labyrinth seal is formed between the large-diameter step portion and the auxiliary lip of the seal member, and the main lip of the seal member slides on a side wall of the small-diameter step portion. .
[0009]
According to the ball bearing of the first aspect of the present invention, two step portions having a large diameter and a small diameter smaller than the shoulder diameter of the raceway surface of the inner ring are formed at the axial end of the outer peripheral surface of the inner ring. Since the auxiliary lip is made to escape to the large-diameter step portion, the distance between the annular portion of the retainer and the auxiliary lip can be significantly increased as compared with the conventional case, and the axial direction of the ball bearing can be increased. Even if the size is reduced, the annular portion of the retainer does not interfere with the auxiliary lip. Therefore, the axial dimensions of the inner ring and the outer ring can be reduced to make the ball bearing compact, and the material cost of the outer ring and the inner ring can be reduced, and the manufacturing cost of the ball bearing can be reduced.
[0010]
Further, according to the ball bearing of the first aspect of the present invention, the distance between the annular portion of the retainer and the auxiliary lip is increased by configuring the auxiliary lip to escape to the large-diameter step portion. A sufficient space for grease to enter between the auxiliary lip and the annular portion of the retainer can be ensured, and grease does not collect around the main lip of the seal member. Therefore, since the pressure of the grease around the main lip of the seal member does not increase, no grease leaks from between the seal member and the inner ring.
[0011]
The ball bearing according to the second aspect of the present invention is the ball bearing according to the first aspect, wherein the outer ring and the inner ring are substantially aligned with a raceway surface of the outer race and a plane including a center of the raceway surface of the inner race. It is characterized by plane symmetry.
[0012]
According to the ball bearing of the second aspect of the present invention, the outer race and the inner race are substantially plane-symmetric with respect to the raceway surface of the outer race and the plane including the center of the raceway surface of the inner race. As compared with the case, the versatility of the outer ring and the inner ring can be increased, and the productivity of the ball bearing can be improved.
[0013]
According to a third aspect of the present invention, in the ball bearing according to the first or second aspect, at least a portion of the annular portion of the retainer and at least a portion of the auxiliary lip overlap in a radial direction. Features.
[0014]
According to the ball bearing of the third aspect of the present invention, at least a portion of the annular portion of the retainer and at least a portion of the auxiliary lip overlap in the radial direction. Can be further reduced, and material costs of the outer ring and the inner ring can be further reduced. Therefore, the ball bearing can be made more compact and the manufacturing cost of the ball bearing can be further reduced.
[0015]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, the present invention will be described in detail with reference to the illustrated embodiments.
[0016]
FIG. 1 is an axial sectional view of a four-point contact ball bearing as one embodiment of the ball bearing of the present invention. In this four-point contact ball bearing, a plurality of balls 3 held by a crown-shaped cage 7 are arranged at regular intervals in a circumferential direction between a raceway surface 1a of an outer race 1 and a raceway surface 2a of an inner race 2. are doing.
[0017]
The outer ring 1 is substantially bilaterally symmetric with respect to a plane A including the center of the raceway surface 1a of the outer race 1 and the raceway surface 2a of the inner race 2, and the inner peripheral surface of the outer race 1 has two axially opposite ends. , Annular grooves 10 and 11 are formed. The raceway surface 1a of the outer race 1 includes a left portion and a right portion which are substantially symmetrical with respect to the plane A. The left portion contacts the ball 3 at a point P1, and the right portion contacts the ball 3 at a point P1. At point P2.
[0018]
On the other hand, the inner race 2 is substantially bilaterally symmetric with respect to a plane A including the center of the raceway surface 1a of the outer race 1 and the raceway surface 2a of the inner race 2, and each of both ends of the outer circumferential surface of the inner race 2 in the axial direction. Are formed with two steps 13, 14 and 15, 16 of a large diameter and a small diameter smaller than the shoulder diameter of the raceway surface 2a of the inner race 2. Of the two steps formed at both ends of the inner ring 2, most of the large-diameter steps 13, 15 on the ball side radially overlap with a part of the annular section 39 of the crown retainer 7. I have. The raceway surface 2a of the inner race 2 includes a left portion and a right portion which are substantially symmetrical with respect to the plane A, and the left portion contacts the ball 3 and P3, and the right portion contacts the ball 3 and P4. In contact.
[0019]
Seal members 18 and 19 are disposed between the inner peripheral surface of the outer ring 1 and the outer peripheral surface of the inner ring 2 at both ends in the axial direction of the four-point contact ball bearing. Each of the sealing members 18 and 19 is composed of cored bars 20 and 21 and lips 23 and 24.
[0020]
Each of the seal members 18 and 19 fixes one end of the seal members 18 and 19 to the annular groove of the outer ring 1, while attaching the sub lips 35 and 36 at the other ends of the seal members 18 and 19 to the large diameter of the inner ring 2. A labyrinth seal is formed between the sub-lips 35, 36 and the large-diameter steps 13, 15 of the inner ring 2 in the vicinity of the steps 13, 15, and the main lip 37 at the other end of the seal members 18, 19. , 38 are in sliding contact with the ball-side surfaces of the small-diameter steps 14, 16 of the inner ring 2 to seal between the outer ring 1 and the inner ring 2. The annular portion 39 of the crown-shaped retainer 7 and the tip of the auxiliary lip 35 of the seal member 18 on the retainer side with respect to the plane A overlap in the radial direction. The seal members 18 and 19 prevent the grease filled between the outer ring 18 and the inner ring 19 from leaking to the outside and preventing external foreign substances from entering between the outer ring 18 and the inner ring 19.
[0021]
FIG. 2 is an enlarged view of the vicinity of two steps 13 and 14 on the retainer side of the inner ring 2.
[0022]
In FIG. 2, a dotted line C indicates the surface of the conventional inner ring having no large-diameter stepped portion, and a dotted line D indicates the position of the auxiliary lip of the conventional sealing member having no large-diameter stepped portion.
[0023]
As shown in FIG. 2, the crown-shaped retainer 7 is formed such that a corner portion of the annular portion 39 on the sub-lip side is chamfered so that a distance between the annular portion 38 and the sub-lip 37 is increased, and a slope is formed there. 43 are formed.
[0024]
Further, as shown in FIG. 2, the sub-lip 35 which is arranged close to the large-diameter step portion 13 and forms a labyrinth seal with the large-diameter step portion 13, The distance from the annular portion 39 is larger than the distance between the conventional auxiliary lip where the large diameter stepped portion whose existence position is indicated by the dotted line D is not formed and the annular portion 39 of the crown holder 7.
[0025]
According to the ball bearing of the above-described embodiment, two stepped portions 13, 14 and 15 having a large diameter and a small diameter smaller than the shoulder diameter of the raceway surface of the inner ring 2 are provided at the axial end of the outer peripheral surface of the inner ring 2. , 16 are formed so that the auxiliary lips 35, 36 escape to the large-diameter steps 13, 15, so that the distance between the annular portion 39 of the crown-shaped retainer 7 and the auxiliary lip 35 is smaller than that of the conventional ball. The annular portion 39 of the crown-shaped retainer 7 and the auxiliary lip 35 do not come close to each other even when the size of the ball bearing is much larger than that of the bearing and the axial dimension of the ball bearing is reduced. Therefore, the axial dimensions of the inner ring 1 and the outer ring 2 can be reduced, and the ball bearing can be made compact. In addition, the material cost of the inner ring 1 and the outer ring 2 can be reduced, and the manufacturing cost of the ball bearing can be reduced.
[0026]
Further, according to the ball bearing of the above-described embodiment, the auxiliary lips 35 and 36 are configured to escape to the large-diameter steps 13 and 15, and the distance between the annular portion 39 of the crown-shaped cage 7 and the auxiliary lip 35. Is increased, a sufficient space for grease to enter between the sub lip 35 and the annular portion 39 of the crown-shaped retainer 7 can be secured, and the grease concentrates around the seal position of the seal member 18. There is no accumulation. Therefore, the grease pressure around the main lip 37 of the seal member 18 does not increase, so that grease does not leak from between the seal member 18 and the inner ring 2.
[0027]
According to the ball bearing of the above embodiment, the outer race 1 and the inner race 2 are substantially plane-symmetric with respect to the plane A including the center of the raceway surface 1a of the outer race 1 and the raceway surface 2a of the inner race 2. Compared with the asymmetric case, the versatility of the outer ring 1 and the inner ring 2 can be increased, and the productivity of the ball bearing can be remarkably increased.
[0028]
Further, according to the ball bearing of the above-described embodiment, since a part of the annular portion 39 of the crown-shaped cage 7 and the tip of the sub lip 35 are overlapped in the radial direction, the outer ring 1 and the inner ring 2 The axial dimension can be further reduced, and the ball bearing can be made more compact.
[0029]
In the ball bearing of the above embodiment, the crown-shaped cage 7 is employed as a cage, and two stepped portions 13 and 14 are provided at both ends of the outer peripheral surface of the inner ring 2 in substantially plane symmetry with respect to the plane A. In the ball bearing of the present invention, a crown-shaped cage is adopted as the cage, and two steps are provided at the end of the outer peripheral surface of the inner ring on the side of the cage with respect to the plane A. At the same time, only one step for the main lip may be provided on the step on the outer side of the inner ring on the side opposite to the plane A. Further, in the ball bearing of the present invention, as the retainer, a retainer in which two annular portions are connected by a plurality of pillar portions and a pocket is formed between adjacent pillar portions is employed, and the outer periphery of the inner ring is formed. Two steps may be provided substantially symmetrically at both ends of the surface.
[0030]
Further, in the ball bearing of the above embodiment, the corner of the crown-shaped cage 7 is chamfered. However, in the ball bearing of the present invention, the corner of the cage may not be chamfered.
[0031]
Further, in the ball bearing of the above embodiment, a four-point contact ball bearing is employed as the ball bearing, and the present invention is practiced with a four-point contact ball bearing. The present invention may be practiced with a ball bearing other than a four-point contact ball bearing such as a contact ball bearing.
[0032]
【The invention's effect】
As is apparent from the above, according to the ball bearing of the first aspect of the present invention, the two ends of the large diameter and the small diameter smaller than the shoulder diameter of the raceway surface of the inner ring are provided at the axial end of the outer peripheral surface of the inner ring. Is formed to allow the auxiliary lip of the seal member to escape to the large-diameter step, so that the distance between the annular portion of the retainer and the auxiliary lip can be increased, and the shaft of the ball bearing can be formed. Even if the dimension in the direction is reduced, the annular portion of the retainer does not interfere with the sub lip. Therefore, the ball bearing can be made compact and the manufacturing cost of the ball bearing can be reduced.
[0033]
According to the ball bearing of the first aspect of the present invention, the distance between the annular portion of the retainer and the auxiliary lip is increased by making the auxiliary lip of the seal member escape to the large-diameter stepped portion. Therefore, a sufficient space can be secured between the auxiliary lip and the annular portion of the retainer, and grease leakage can be suppressed.
[0034]
According to the ball bearing of the second aspect of the present invention, the outer race and the inner race are substantially plane-symmetric with respect to the raceway surface of the outer race and a plane including the center of the raceway surface of the inner race. In addition, the versatility of the inner ring is enhanced, and the productivity of the ball bearing can be remarkably improved.
[0035]
According to the ball bearing of the third aspect of the present invention, since the annular portion of the retainer and at least a part of the sub lip overlap in the radial direction, the ball bearing can be made more compact in the axial direction. In addition, the manufacturing cost of the ball bearing can be further reduced.
[Brief description of the drawings]
FIG. 1 is an axial sectional view of a ball bearing according to an embodiment of the present invention.
FIG. 2 is an enlarged view of the vicinity of two steps on the retainer side of the inner ring of the ball bearing.
DESCRIPTION OF SYMBOLS 1 Outer ring 2 Inner ring 3 Ball 7 Crowned retainer 13,15 Large diameter step 14,16 Small diameter step 18,19 Seal member 20,21 Core metal part 23,24 Lip part 35,36 Secondary lip 37,38 Main lip 39 Annular part A plane

Claims (3)

外輪と、内輪と、上記外輪の軌道面と上記内輪の軌道面との間に配置された玉と、この玉を保持する保持器と、上記外輪の内周面の軸方向の端部と上記内輪の外周面の軸方向の端部との間をシールするシール部材とを備えた玉軸受において、
上記内輪の外周面の軸方向の少なくとも一方の端部に、上記内輪の軌道面の肩径よりも小さな大径と小径との二段の段部を形成し、
上記大径の段部と、上記シール部材の副リップとの間にラビリンスシールを構成すると共に、上記小径の段部の側壁に上記シール部材の主リップを摺動させていることを特徴とする玉軸受。An outer ring, an inner ring, a ball disposed between the raceway surface of the outer ring and the raceway surface of the inner ring, a retainer for holding the ball, an axial end of an inner peripheral surface of the outer ring, A ball bearing provided with a seal member for sealing between the outer peripheral surface of the inner ring and an axial end thereof;
At least one end in the axial direction of the outer peripheral surface of the inner ring, a two-step portion of a large diameter and a small diameter smaller than the shoulder diameter of the raceway surface of the inner ring,
A labyrinth seal is formed between the large-diameter step portion and the sub lip of the seal member, and the main lip of the seal member slides on a side wall of the small-diameter step portion. Ball bearings. 請求項１に記載の玉軸受において、上記外輪と上記内輪は、上記外輪の軌道面と上記内輪の軌道面のセンターを含む面に対して、略面対称になっていることを特徴とする玉軸受。The ball bearing according to claim 1, wherein the outer ring and the inner ring are substantially plane-symmetric with respect to a surface including a raceway surface of the outer ring and a center of the raceway surface of the inner ring. bearing. 請求項１または２に記載の玉軸受において、上記保持器の環状部の少なくとも一部と、上記副リップの少なくとも一部が径方向に重なることを特徴とする玉軸受。3. The ball bearing according to claim 1, wherein at least a part of the annular portion of the cage and at least a part of the sub lip overlap in a radial direction. 4.
JP2003082633A 2003-03-25 2003-03-25 Ball bearing Pending JP2004293563A (en)

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010038353A (en) * 2008-08-08 2010-02-18 Nsk Ltd Roller bearing
CN102434590A (en) * 2011-10-14 2012-05-02 青岛泰德汽车轴承有限责任公司 Bearing sealing device for automobile silicon oil fan clutch
WO2016083133A1 (en) * 2014-11-28 2016-06-02 Aktiebolaget Skf Sealed bearing
CN106996422A (en) * 2016-01-26 2017-08-01 株式会社捷太格特 Rolling bearing
US10221893B2 (en) 2015-06-03 2019-03-05 Jtekt Corporation Rolling bearing
US10260561B2 (en) * 2017-03-22 2019-04-16 Jtekt Corporation Rolling bearing
US10539183B2 (en) 2017-03-31 2020-01-21 Jtekt Corporation Rolling bearing
US10788075B2 (en) 2017-10-04 2020-09-29 Jtekt Corporation Ball bearing

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010038353A (en) * 2008-08-08 2010-02-18 Nsk Ltd Roller bearing
CN102434590A (en) * 2011-10-14 2012-05-02 青岛泰德汽车轴承有限责任公司 Bearing sealing device for automobile silicon oil fan clutch
WO2016083133A1 (en) * 2014-11-28 2016-06-02 Aktiebolaget Skf Sealed bearing
US10221893B2 (en) 2015-06-03 2019-03-05 Jtekt Corporation Rolling bearing
CN106996422A (en) * 2016-01-26 2017-08-01 株式会社捷太格特 Rolling bearing
US10174790B2 (en) 2016-01-26 2019-01-08 Jtekt Corporation Rolling bearing
US10253813B2 (en) 2016-01-26 2019-04-09 Jtekt Corporation Rolling bearing
US10260561B2 (en) * 2017-03-22 2019-04-16 Jtekt Corporation Rolling bearing
US10539183B2 (en) 2017-03-31 2020-01-21 Jtekt Corporation Rolling bearing
US10788075B2 (en) 2017-10-04 2020-09-29 Jtekt Corporation Ball bearing

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