JP2004084858A - Sealing device, and rolling bearing and hub unit with the device integrated - Google Patents

Sealing device, and rolling bearing and hub unit with the device integrated Download PDF

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Publication number
JP2004084858A
JP2004084858A JP2002248756A JP2002248756A JP2004084858A JP 2004084858 A JP2004084858 A JP 2004084858A JP 2002248756 A JP2002248756 A JP 2002248756A JP 2002248756 A JP2002248756 A JP 2002248756A JP 2004084858 A JP2004084858 A JP 2004084858A
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Japan
Prior art keywords
peripheral surface
seal lip
ring
sealing device
rolling bearing
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JP2002248756A
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Japanese (ja)
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JP2004084858A5 (en
Inventor
Kinji Yugawa
湯川　謹次
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NSK Ltd
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NSK Ltd
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Priority to JP2002248756A priority Critical patent/JP2004084858A/en
Publication of JP2004084858A publication Critical patent/JP2004084858A/en
Publication of JP2004084858A5 publication Critical patent/JP2004084858A5/ja
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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
    • F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward
    • F16C33/7879—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a further sealing ring
    • F16C33/7883—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a further sealing ring mounted to the inner race and of generally L-shape, the two sealing rings defining a sealing with box-shaped cross-section
    • 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
    • F16C19/18—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 two or more rows of balls
    • F16C19/181—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 two or more rows of balls with angular contact
    • F16C19/183—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 two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—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 two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To enhance the follow-up property to the movement of the circumferential surface of a slinger of an inner seal lip 13a located on the innermost side of three seal lips 11, 12 and 13a. <P>SOLUTION: The intermediate seal lip 12a located in the middle of the seal lips 11, 12a and 13a is formed of a thick part 18 provided in a part closer to the tip and a combined part 19 provided in a part closer to the base end and having a thickness smaller than the maximum thickness of the thick part 18. The inner seal lip 13a is provided on the inside surface of the combined part 19 in a radially protruding state. The tip edge of the inner seal lip 13a and the tip edge of the thick part 18 are slid on the circumferential surface of the slinger 2. <P>COPYRIGHT: (C)2004,JPO

Description

【０００１】
【発明の属する技術分野】
この発明に係る密封装置と転がり軸受及びハブユニットは、例えば自動車用車輪の支持装置等の回転支持部に組み込む転がり軸受やハブユニットの密封装置の改良に関する。
【０００２】
【従来の技術】
各種機械装置の回転支持部に、玉軸受、円筒ころ軸受、円すいころ軸受等の転がり軸受が組み込まれている。この様な転がり軸受には密封装置を組み込んで、この転がり軸受の内部に封入したグリースが外部に漏洩する事を防止すると共に、外部に存在する雨水、泥、塵等の各種異物が転がり軸受の内部に入り込む事を防止している。図６〜７は、この様な目的で転がり軸受の端部開口に装着した密封装置の従来構造を示している。
【０００３】
この図６〜７に示した従来構造の密封装置１４、１４は、保持部材である芯金１と、スリンガ２と、シール材３とから成る。このうちの芯金１は、外輪４の端部内周面に内嵌固定自在な外径側円筒部５と、この外径側円筒部５の軸方向内端縁（転がり軸受６の軸方向中央寄り端縁で、図７の左端縁）から直径方向内方に折れ曲がった内側円輪部７を備えた、断面Ｌ字形で全体を円環状としている。又、上記スリンガ２は、内輪８の端部外周面に外嵌固定自在な内径側円筒部９と、この内径側円筒部９の軸方向外端縁（転がり軸受６の軸方向開口寄り端縁で、図７の右端縁）から直径方向外方に折れ曲がった外側円輪部１０とを備えた、断面Ｌ字形で円環状としている。又、上記シール材３は、ゴムの如きエラストマー等の弾性材により造られて、外側、中間、内側の３本のシールリップ１１〜１３を備え、上記芯金１にその基端部を結合固定している。そして、最も外側に位置する外側シールリップ１１の先端縁を、上記スリンガ２を構成する外側円輪部１０の内側面に摺接させ、それぞれが請求項に記載した径方向シールリップに相当する、残り２本のシールリップである中間シールリップ１２及び内側シールリップ１３の先端縁を、上記スリンガ２を構成する内径側円筒部９の外周面に摺接させている。
【０００４】
尚、上述の図６〜７に示した従来構造の場合、内側シールリップ１３を、先端縁に向かう程、転がり軸受６の軸方向外側に向かう方向に傾斜させている。又、上記各シールリップ１１〜１３のうち、中間に位置する中間シールリップ１２の厚さを、基端部から中間部に亙りほぼ同じ大きさとすると共に、先端寄り部分で急激に大きく（厚く）している。この中間シールリップ１２も、上記内側シールリップ１３と同様に、先端縁に向かう程、上記転がり軸受６の軸方向外側に向かう方向に傾斜させている。又、上記内側シールリップ１３の全長は、上記中間シールリップ１２の全長よりも小さい（短い）。
【０００５】
上述の様な密封装置１４は、転がり軸受６の端部に組み込んで使用する。図５に示す転がり軸受６の場合、１対の内輪８、８の外周面に内輪軌道１５、１５を形成すると共に、これら内輪８、８の周囲に設けた外輪４の内周面に、１対の外輪軌道１６、１６を形成している。そして、これら各外輪軌道１６、１６と上記各内輪軌道１５、１５との間に、複数の転動体１７、１７を転動自在に組み込んでいる。
【０００６】
上述の様な従来構造の場合には、各シール材３に設けたシールリップ１１〜１３の先端縁とスリンガ２とを摺接させる事により、転がり軸受６（図６）の端部開口を塞ぐ。そして、この転がり軸受６の内部に封入したグリースが外部に漏洩する事を防止すると共に、外部に存在する雨水、泥、塵等の各種異物が転がり軸受の内部に入り込む事を防止する。
【０００７】
【発明が解決しようとする課題】
上述の図６〜７に示した従来構造の場合、次の様な点を改良する事が望まれている。即ち、上述した従来構造を、例えば、自動車用車輪の支持装置に組み込む転がり軸受６に使用した場合で、自動車が急旋回した場合には、スリンガ２を外嵌した内輪８と、芯金１を内嵌した外輪４とが、相対的に傾く（両部材８、４の中心軸が不一致になる）可能性がある。この様に内、外両輪８、４が相対的に傾いた場合には、上記スリンガ２と芯金１とが一部で近づいて、上記各シールリップ１１〜１３が一部で過度に圧縮される。又、何らかの理由で、内輪８が外輪４に対し偏心しても、上記各シールリップ１１〜１３が一部で過度に圧縮される可能性がある。この様に各シールリップ１１〜１３が一部で過度に圧縮された場合、これら各シールリップ１１〜１３の先端縁がスリンガ２に押し付けられる力である、所謂緊迫力が大きくなる。この為、上記各シールリップ１１〜１３の先端縁が摩耗し易くなり、これら各シールリップ１１〜１３の先端縁とスリンガ２との摺接部での密封性能が悪化する。又、この場合、転がり軸受６の回転トルクが大きくなったり、この摺接部での摩擦に基づく発熱量が大きくなる。
【０００８】
又、上記内、外両輪８、４同士が相対的に傾いたり、内輪８が外輪４に対し偏心すると、これら両輪８、４の周面同士が、上記スリンガ２と芯金１との一部と径方向反対側部分で互いに遠ざかる。この為、この反対側部分に存在するシールリップ１１〜１３の緊迫力が小さくなり、密封装置１４の内部に雨水等が進入し易くなる。
【０００９】
特に、上記複数のシールリップ１１〜１３のうち、内側に位置する内側シールリップ１３の全長は小さく（短く）、しかも、前記芯金１の中心軸に対し直交する仮想平面に対するこの内側シールリップ１３の傾斜角度α（図７）は小さい。この為、上記スリンガ２からこの内側シールリップ１３の先端縁に加わる径方向の力に対する、この内側シールリップ１３の基端部の変形量が小さい。従って、上記内、外両輪８、４同士が相対的に傾いたり、或は内輪８が外輪４に対し偏心した場合に、上記内側シールリップ１３の先端縁が上記スリンガ２の外周面の動きに対し追従しにくい。例えば、このスリンガ２を固定した内輪８が上記芯金１を固定した外輪４に対し偏心した場合には、図８（Ａ）に示す様に、内側シールリップ１３の円周方向一部で先端縁がスリンガ２の外周面に強く押し付けられて、緊迫力が過大になる。同時に、図８（Ｂ）に示す様に、上記内側シールリップ１３の円周方向一部と径方向反対側部分で、先端縁が上記スリンガ２の外周面から離れたり、緊迫力が過小になる。この為、密封性が悪化したり、転がり軸受６の回転トルクや発熱量が大きくなり易い。尚、図８に二点鎖線で示した部分は、上記芯金１とスリンガ２との中心軸同士が一致した場合での、中間、内側両シールリップ１２、１３とスリンガ２との摺接状態を表している。
【００１０】
一方、上記内側シールリップ１３の全長を十分に大きく（長く）すると共に、上記芯金１の中心軸に対し直交する仮想平面に対するこの内側シールリップ１３の傾斜角度αを十分に大きくすれば、この様な不都合を防止できる。但し、この場合には、この内側シールリップ１３と、この内側シールリップ１３と隣接する状態で設けた中間シールリップ１２とが干渉し易くなり、これら両シールリップ１３、１２の良好な性能を確保する事が難しくなる。
本発明は、この様な事情に鑑みて、２本の径方向シールリップのうちの一方の径方向シールリップの性能を損なう事なく、相手側の周面の動きに対する、他方の径方向シールリップの追従性を良好にして、密封性を十分に確保すると共に、回転トルクと発熱量との増大を抑えるべく発明したものである。
【００１１】
【課題を解決するための手段】
本発明の密封装置と転がり軸受及びハブユニットのうち、請求項１に記載した密封装置は、内輪の外周面に設けた内輪軌道と外輪の内周面に設けた外輪軌道との間に複数の転動体を設けて上記内輪と外輪との相対回転を自在とした転がり軸受に組み込み、これら内輪の外周面と外輪の内周面との間を塞ぐものである。この為に、本発明の密封装置は、前述の図６〜７に示した従来構造と同様に、保持部材と、シール材と、２本の径方向シールリップとを備える。このうちの保持部材は、上記内輪の外周面と外輪の内周面とのうちの一方の周面に固定されている。又、上記シール材は、弾性材により造られて上記保持部材にその一部を結合固定している。又、上記各径方向シールリップは、上記シール材の一部に設けられて、それぞれの先端縁を、上記内輪の外周面と外輪の内周面とのうちの他方に設けられた周面又はこの他方に支持された部材の周面に摺接又は近接対向させている。
【００１２】
特に、請求項１に記載した密封装置に於いては、上記２本の径方向シールリップのうちの一方の径方向シールリップが、先端寄り部分に設けられた肉厚部と、基端寄り部分に設けられた、この肉厚部の最大厚さよりも厚さが小さくなった括れ部とを備えたものである。又、上記２本の径方向シールリップのうちの他方の径方向シールリップが、上記括れ部の周面に、上記一方の周面から離れる方向に突出する状態で設けられたものである。そして、上記他方の径方向シールリップの先端縁と上記肉厚部の先端縁とを、上記内輪の外周面と外輪の内周面とのうちの他方に設けられた周面又はこの他方に支持された部材の周面に摺接又は近接対向させている。
【００１３】
又、請求項２に記載した転がり軸受は、請求項１に記載した密封装置を少なくとも１個組み込んでいる。
又、請求項３に記載したハブユニットは、内輪又は外輪が車輪を固定する為のハブであり、請求項１に記載した密封装置を少なくとも１個組み込んでいる。
【００１４】
【作用】
上述の様に構成する本発明の密封装置と転がり軸受とハブユニットによれば、シール材に設けた２本の径方向シールリップのうちの他方の径方向シールリップの、相手側の周面の動きに対する追従性を良好にする事ができる。この為、この他方の径方向シールリップの緊迫力の変化を抑える事ができる。しかも、上記追従性を良好にする為に、上記他方のシールリップの全長を大きくしたり、保持部材の中心軸に対し直交する仮想平面に対するこの他方のシールリップの傾斜角度を大きくする必要がない。この為、上記２本の径方向シールリップ同士が干渉する事を防止できる。この結果、これら２本の径方向シールリップのうちの一方の径方向シールリップの性能を損なう事なく、上記他方の径方向シールリップの先端縁の摩耗を抑えて、良好な密封性能を得る事ができ、しかも、回転トルクと発熱量との増大を抑える事ができる。
【００１５】
【発明の実施の形態】
図１〜２は、本発明の実施の形態の第１例を示している。本発明の密封装置１４ａは、保持部材である芯金１と、スリンガ２と、シール材３ａとから成る。このうちの芯金１は、低炭素鋼板等の金属板にプレス加工等の打ち抜き加工並びに塑性加工を施す事により、一体成形している。この様な芯金１は、転がり軸受６を構成する外輪４（図６参照）の外端部内周面に内嵌固定自在な外径側円筒部５と、この外径側円筒部５の軸方向内端縁（図１、２の左端縁）から直径方向内方に折れ曲がった内側円輪部７とを備えた、断面略Ｌ字形で全体を円環状としている。
【００１６】
又、上記スリンガ２は、ステンレス鋼板等、優れた耐食性を有する金属板に、やはりプレス加工等の打ち抜き加工並びに塑性加工を施す事により、一体成形している。この様なスリンガ２は、上記転がり軸受６を構成する内輪８（図６参照）の外端部外周面に外嵌固定自在な内径側円筒部９と、この内径側円筒部９の軸方向外端縁（図１、２の右端縁）から直径方向外方に折れ曲がった外側円輪部１０とを備えた、断面略Ｌ字形で全体を円環状としている。
【００１７】
又、上記シール材３ａは、ゴムの如きエラストマー等の弾性材により造られて、外側、中間、内側の３本のシールリップ１１、１２ａ、１３ａを備え、上記芯金１にその基端部を結合固定している。又、請求項に記載した一方の径方向シールリップに相当する、上記中間シールリップ１２ａは、先端寄り部分に設けた肉厚部１８と、基端寄り部分に設けた、この肉厚部１８の最大厚さよりも厚さが小さくなった括れ部１９とを備える。又、この肉厚部１８の厚さを、この括れ部１９との連続部分付近で急激に大きく（厚く）し、先端縁付近で小さくしている。そして、この括れ部１９の内周面の中間部に、請求項に記載した他方の径方向シールリップに相当する、上記内側シールリップ１３ａを、径方向内方に突出する状態で設けている。この内側シールリップ１３ａの全長は、上記中間シールリップ１２ａの全長よりも小さい（短い）。又、上記外側シールリップ１１を、先端縁に向かう程、径方向外方に傾斜させている。そして、上記外側シールリップ１１の先端縁を上記スリンガ２を構成する外側円輪部１０の内側面（図１、２の左側面）に摺接させ、残り２本のシールリップである、中間シールリップ１２ａと内側シールリップ１３ａとの先端縁を、上記スリンガ２を構成する内径側円筒部９の外周面の軸方向に離隔した位置に摺接させている。
【００１８】
上述の様に構成する本発明の密封装置と転がり軸受とハブユニットによれば、３本のシールリップ１１、１２ａ、１３ａのうち、中間に位置する中間シールリップ１２ａの性能を損なう事なく、径方向に向いた相手側の周面の動きに対する、最も内側に位置する内側シールリップ１３ａの追従性を良好にして、密封性を十分に確保する事ができる。即ち、本発明の場合には、この内側シールリップ１３ａを、中間シールリップ１２ａの一部で厚さが小さくなった括れ部１９の内周面に、径方向内方に突出する状態で設けている。又、この中間シールリップ１２ａは、全長を大きくできると共に、芯金１の中心軸に対し直交する仮想平面に対する傾斜角度も大きくできる。この為、上記スリンガ２を構成する内径側円筒部９の外周面から加わる径方向の力に対する、上記中間シールリップ１２ａの基端部の変形量を大きくできる。更に、この中間シールリップ１２ａの剛性を、上記括れ部１９部分で小さくできる。従って、上記内径側円筒部９の外周面から上記内側シールリップ１３ａに加わる径方向の力に対する、この内側シールリップ１３ａの先端縁の変位量を十分に大きくできる。この結果、使用時に、内輪８が外輪４に対し傾いたり、或は偏心する事により、芯金１とスリンガ２の外周面とが一部で近づいたり、或は遠ざかった場合に、上記内側シールリップ１３ａの先端縁を、このスリンガ２の外周面の動きに対して良好に追従させる事ができる。例えば、このスリンガ２を固定した内輪８が、上記芯金１を固定した外輪４に対し偏心した場合には、図２（Ａ）に示す様に、上記内側シールリップ１３ａの円周方向一部で、この内側シールリップ１３ａの先端縁が上記内径側円筒部９の外周面に強く押し付けられる傾向となる。これに対して、本発明の場合には、上記中間シールリップ１２ａで上記内側シールリップ１３ａの基端部を結合した部分である括れ部１９が外径側に変位するのに伴って、この内側シールリップ１３ａの基端部も外径側に変位する。この為、この内側シールリップ１３ａの先端縁と上記スリンガ２の外周面との緊迫力が過大になる事を防止できる。又、上述の様に内輪８が外輪４に対し偏心した場合には、図２（Ｂ）に示す様に、上記内側シールリップ１３ａの円周方向一部と径方向反対側部分で、この内側シールリップ１３ａの先端縁が上記内径側円筒部９の外周面から離れる傾向となる。これに対して、本発明の場合には、上記中間シールリップ１２ａで上記内側シールリップ１３ａの基端部を結合した括れ部１９が内径側に変位する為、上記緊迫力が過小になったり、上記先端縁が上記内径側円筒部９の外周面から離れる事を防止できる。尚、図２に二点鎖線で示した部分は、前記芯金１と上記スリンガ２との中心軸同士が一致した場合での、中間、内側両シールリップ１２ａ、１３ａとスリンガ２との摺接状態を表している。
【００１９】
この様に、本発明の場合には、上記内側シールリップ１３ａの先端縁が上記スリンガ２の外周面の動きに対し良好に追従する為、この内側シールリップ１３ａの緊迫力の変化を抑える事ができる。又、この内側シールリップ１３ａの全長を大きくしたり、上記芯金１の中心軸に対し直交する仮想平面に対するこの内側シールリップ１３ａの傾斜角度α´（図１）を大きくする必要がない。この為、この内側シールリップ１３ａと上記中間シールリップ１２ａとが干渉する事を防止できる。この結果、この中間シールリップ１２ａの性能を損なう事なく、上記内側シールリップ１３ａの先端縁の摩耗を抑えて、良好な密封性能を得る事ができ、しかも回転トルクと発熱量との増大を抑える事ができる。
【００２０】
又、本例の場合には、上記内側シールリップ１３ａを含め、３本のシールリップ１１、１２ａ、１３ａを総て、それぞれの先端縁に向かう程流体の流れ方向に関して外側に向かう方向に傾斜させている。この為、転がり軸受６の内部に封入したグリースが上記各シールリップ１１、１２ａ、１３ａの先端縁とスリンガ２との摺接部に、適度に供給される。従って、これら各摺接部の潤滑状態を良好に保持して、転がり軸受６の回転トルクを低く抑えると共に、各摺接部をグリースにより塞いで、これら各摺接部の密封性能を向上させる事ができる。
【００２１】
次に、図３は、本発明の実施の形態の第２例を示している。本例の場合には、上述した第１例の場合と異なり、内側シールリップ１３ａを非接触シールとしている。即ち、本例の場合には、この内側シールリップ１３ａの先端縁を、スリンガ２を構成する内径側円筒部９の外周面に、厚さ寸法ｄを有する微小隙間を介して近接対向させている。この様な本例の場合には、上述した第１例の場合よりも回転トルクを小さくできる。又、前述の図７に示した従来構造で、本例と同様に、内側シールリップ１３を非接触シールとした場合には、使用時にスリンガ２の中心軸が芯金５の中心軸に対し傾斜したり、これら両部材２、５同士が偏心する可能性がある事を考慮して、上記内側シールリップ１３の先端縁と内径側円筒部９の外周面との間の隙間の厚さを大きく設定する必要がある。そして、この様に隙間の厚さを大きく設定した場合には、シール性能を良好に確保する事が難しくなる。これに対して、本例の場合には、内側シールリップ１３ａの先端縁が、スリンガ２の外周面の動きに対して良好に追従する。この為、上記微小隙間の厚さ寸法ｄを小さく設定しても、上記内側シールリップ１３ａとスリンガ２とが接触する事を防止でき、回転トルクを小さくしつつ、良好なシール性能を確保できる。
その他の構成及び作用に就いては、上述した第１例の場合と同様である為、同等部分には同一符号を付して重複する説明は省略する。
【００２２】
次に、図４は、本発明の実施の形態の第３例を示している。本例の場合には、上述した第１例の場合と異なり、内側シールリップ１３ｂを、先端縁に向かう程転がり軸受６（図６参照）の軸方向内側（図４の左側）に向かう方向に傾斜させている。この様な本例の場合には、転がり軸受６の内部に封入したグリースが、上述した第１例の場合に比べて、中間シールリップ１２ａ及び外側シールリップ１１の先端縁とスリンガ２との摺接部に供給されにくくはなる。但し、本例の場合には、上記中間シールリップ１２ａの肉厚部１８と内側シールリップ１３ｂとの干渉を防止しつつ、この内側シールリップ１３ｂの全長を大きくすると共に、芯金１の中心軸に対し直交する仮想平面に対する傾斜角度α´を大きくする事ができる。
その他の構成及び作用に就いては、前述の図１〜２に示した第１例の場合と同様である為、同等部分には同一符号を付して重複する説明は省略する。
【００２３】
尚、本発明の密封装置及びこれを組み込んだ転がり軸受は、使用時に転がり軸受６を構成する内輪８と外輪４との何れが回転する場合でも実施できる。又、本発明は、外輪４にスリンガ２を内嵌固定すると共に、内輪８にシール材３ａを結合した芯金１を外嵌固定した構造でも実施できる。この場合には、このシール材３ａを構成する中間シールリップの外周面に径方向外方に突出する状態で設けた内側シールリップの先端縁を、上記スリンガ２の内周面に摺接させる。又、本発明の密封装置及びこれを組み込んだ転がり軸受は、内輪８を、車輪を支持する為のハブの外周面に外嵌固定すると共に、外輪４を、自動車の懸架装置を構成するナックルの支持孔に内嵌固定自在とした、ハブユニットに組み込んで使用する事もできる。又、この場合に、上記外輪４の外周面に、上記ナックルの端面に固定する為の固定側フランジを形成する事もできる。更に、図５に示す様に、ハブ２０の内端部（図５の右端部）外周面に、外周面に内輪軌道１５を有する内輪８を外嵌固定すると共に、上記ハブ２０の中間部外周面でこの内輪８から外れた部分に別の内輪軌道１５を形成したハブユニットに、本発明の密封装置１４ａを組み込む事もできる。又、この図５に示したハブユニットの場合には、外輪４の外周面に、ナックル２１の端面に固定する為の固定側フランジ２２を形成している。又、上記ハブ２１の外端寄り部分（図５の左端寄り部分）外周面に、車輪を固定する為の回転側フランジ２３を形成している。
尚、同図に示したハブユニットで、ハブ２０の中間部外周面と外輪４の外端部内周面との間に組み込んだ密封装置１４ｂの様に、シール材３ａに設けたシールリップの先端縁を、ハブ２０（又は内輪８）の外周面に直接摺接させる構造に、本発明を適用する事もできる。更には、ハブを外輪側に設けた（外輪回転型の）ハブユニットで本発明を実施する事もできる。
【００２４】
【発明の効果】
本発明は、以上に述べた通り構成され作用するので、優れたシール性及び耐久性を有し、しかも回転トルクが小さい密封装置を実現できる。この為、雨水、泥、塵等の各種異物が転がり軸受やハブユニットの内部空間に入り込む事を防止して、この転がり軸受やハブユニットの耐久性の向上を図れると共に、燃費性能や加速性能を中心とする、車両の走行性能の向上を図れる。
【図面の簡単な説明】
【図１】本発明の実施の形態の第１例を示す部分断面図。
【図２】スリンガを固定した内輪が芯金を固定した外輪に対し偏心した状態で、（Ａ）は芯金とスリンガとが近づいた部分を、（Ｂ）は芯金とスリンガとが遠ざかった部分を示す、図１と同様の図。
【図３】本発明の実施の形態の第２例を示す部分断面図。
【図４】同第３例を示す部分断面図。
【図５】本発明の密封装置を組み込んだハブユニットを示す断面図。
【図６】従来構造の密封装置を、転がり軸受に組み込んだ状態で示す半部断面図。
【図７】同密封装置のみを取り出して示す部分拡大断面図。
【図８】同密封装置で、スリンガを固定した内輪が芯金を固定した外輪に対し偏心した状態で、（Ａ）は芯金とスリンガとが近づいた部分を、（Ｂ）は芯金とスリンガとが遠ざかった部分を示す、図７と同様の図。
【符号の説明】
１　　芯金
２　　スリンガ
３、３ａ　シール材
４　　外輪
５　　外径側円筒部
６　　転がり軸受
７　　内側円輪部
８　　内輪
９　　内径側円筒部
１０　　外側円輪部
１１　　外側シールリップ
１２、１２ａ　中間シールリップ
１３、１３ａ、１３ｂ　内側シールリップ
１４、１４ａ、１４ｂ　密封装置
１５　　内輪軌道
１６　　外輪軌道
１７　　転動体
１８　　肉厚部
１９　　括れ部
２０　　ハブ
２１　　ナックル
２２　　固定側フランジ
２３　　回転側フランジ[0001]
TECHNICAL FIELD OF THE INVENTION
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a sealing device, a rolling bearing, and a hub unit, and more particularly to an improvement in a rolling bearing and a hub unit sealing device to be incorporated in a rotation support portion such as a vehicle wheel support device.
[0002]
[Prior art]
Rolling bearings such as ball bearings, cylindrical roller bearings, and tapered roller bearings are incorporated in the rotation support portions of various types of mechanical devices. A sealing device is incorporated in such a rolling bearing to prevent the grease sealed inside the rolling bearing from leaking to the outside and to prevent various foreign substances such as rainwater, mud, and dust existing outside from rolling bearings. Prevents getting inside. 6 and 7 show a conventional structure of a sealing device mounted on an end opening of a rolling bearing for such a purpose.
[0003]
The conventional sealing devices 14 and 14 shown in FIGS. 6 and 7 include a metal core 1 as a holding member, a slinger 2, and a sealing material 3. Among these, the core metal 1 includes an outer diameter side cylindrical portion 5 that can be fitted and fixed on the inner peripheral surface of the end portion of the outer ring 4, and an axial inner edge of the outer diameter side cylindrical portion 5 (the axial center of the rolling bearing 6). An inner ring portion 7 that is bent inward in the diametrical direction from a left edge (a left edge in FIG. 7) is formed in an annular shape with an L-shaped cross section. The slinger 2 includes an inner cylindrical portion 9 that can be externally fitted and fixed to the outer peripheral surface of the end of the inner ring 8, and an outer edge in the axial direction of the inner cylindrical portion 9 (an edge near the axial opening of the rolling bearing 6). 7 has an outer annular portion 10 bent radially outward from the right edge of FIG. 7), and has an annular shape with an L-shaped cross section. The sealing member 3 is made of an elastic material such as an elastomer such as rubber, and has three outer, middle and inner sealing lips 11 to 13, and a base end thereof is fixedly connected to the cored bar 1. are doing. Then, the distal end edge of the outermost seal lip 11 located on the outermost side is slid in contact with the inner side surface of the outer annular portion 10 constituting the slinger 2, and each corresponds to the radial seal lip described in the claims. The tip edges of the intermediate seal lip 12 and the inner seal lip 13 which are the remaining two seal lips are slidably contacted with the outer peripheral surface of the inner cylindrical portion 9 constituting the slinger 2.
[0004]
In the case of the conventional structure shown in FIGS. 6 and 7 described above, the inner seal lip 13 is inclined in a direction toward the axially outer side of the rolling bearing 6 toward the leading edge. In addition, the thickness of the intermediate seal lip 12 located at the middle of the seal lips 11 to 13 is set to be substantially the same from the base end to the middle, and the thickness is sharply increased (thickened) near the tip. are doing. Similarly to the inner seal lip 13, the intermediate seal lip 12 is inclined in the direction toward the outside in the axial direction of the rolling bearing 6 toward the leading edge. The total length of the inner seal lip 13 is smaller (shorter) than the total length of the intermediate seal lip 12.
[0005]
The sealing device 14 as described above is used by being incorporated into the end of the rolling bearing 6. In the case of the rolling bearing 6 shown in FIG. 5, inner ring raceways 15, 15 are formed on the outer peripheral surfaces of the pair of inner rings 8, 8, and the inner peripheral surfaces of the outer ring 4 provided around these inner rings 8, 1 are formed on the inner peripheral surface. A pair of outer raceways 16, 16 are formed. A plurality of rolling elements 17, 17 are rotatably incorporated between the outer raceways 16, 16 and the inner raceways 15, 15, respectively.
[0006]
In the case of the conventional structure as described above, the leading edge of the seal lip 11 to 13 provided on each seal member 3 is brought into sliding contact with the slinger 2, thereby closing the end opening of the rolling bearing 6 (FIG. 6). . The grease sealed in the rolling bearing 6 is prevented from leaking to the outside, and at the same time, various foreign substances such as rainwater, mud, and dust existing outside are prevented from entering the inside of the rolling bearing.
[0007]
[Problems to be solved by the invention]
In the case of the conventional structure shown in FIGS. 6 and 7 described above, it is desired to improve the following points. That is, for example, when the above-described conventional structure is used for a rolling bearing 6 incorporated in a support device for an automobile wheel, when the automobile turns sharply, the inner ring 8 fitted with the slinger 2 and the cored bar 1 are attached. There is a possibility that the inner ring 4 and the inner ring 4 are relatively inclined (the center axes of the two members 8 and 4 become inconsistent). In this way, when the inner and outer wheels 8 and 4 are relatively inclined, the slinger 2 and the core bar 1 partially approach each other, and the seal lips 11 to 13 are partially excessively compressed. You. Further, even if the inner race 8 is eccentric with respect to the outer race 4 for some reason, there is a possibility that each of the seal lips 11 to 13 is excessively compressed in part. When the seal lips 11 to 13 are partially excessively compressed in this way, the so-called tension force, which is the force with which the leading edges of the seal lips 11 to 13 are pressed against the slinger 2, increases. For this reason, the leading edges of the seal lips 11 to 13 are easily worn, and the sealing performance at the sliding contact portion between the leading edges of the seal lips 11 to 13 and the slinger 2 is deteriorated. Further, in this case, the rotational torque of the rolling bearing 6 increases, and the amount of heat generated due to friction at the sliding contact portion increases.
[0008]
When the inner and outer wheels 8 and 4 are relatively inclined with each other or the inner ring 8 is eccentric with respect to the outer ring 4, the peripheral surfaces of the two wheels 8 and 4 form a part of the slinger 2 and the cored bar 1. And away from each other at the radially opposite side. For this reason, the tightening force of the seal lips 11 to 13 existing on the opposite side is reduced, and rainwater or the like easily enters the inside of the sealing device 14.
[0009]
In particular, of the plurality of seal lips 11 to 13, the entire length of the inner seal lip 13 located inside is small (short), and moreover, the inner seal lip 13 with respect to a virtual plane orthogonal to the center axis of the cored bar 1. Has a small inclination angle α (FIG. 7). Therefore, the amount of deformation of the base end of the inner seal lip 13 with respect to the radial force applied from the slinger 2 to the distal end edge of the inner seal lip 13 is small. Therefore, when the inner and outer wheels 8 and 4 are relatively inclined with each other, or when the inner ring 8 is eccentric with respect to the outer ring 4, the leading edge of the inner seal lip 13 causes the outer peripheral surface of the slinger 2 to move. Difficult to follow. For example, when the inner ring 8 to which the slinger 2 is fixed is eccentric with respect to the outer ring 4 to which the core bar 1 is fixed, as shown in FIG. The edge is strongly pressed against the outer peripheral surface of the slinger 2, and the tension becomes excessive. At the same time, as shown in FIG. 8 (B), the distal end edge is separated from the outer peripheral surface of the slinger 2 or the tension force is too small at a part radially opposite to a part in the circumferential direction of the inner seal lip 13. . For this reason, the sealing performance is deteriorated, and the rotational torque and the calorific value of the rolling bearing 6 tend to increase. In FIG. 8, the portion indicated by the two-dot chain line shows the sliding contact between the middle and inner seal lips 12 and 13 and the slinger 2 when the center axes of the cored bar 1 and the slinger 2 coincide with each other. Is represented.
[0010]
On the other hand, if the overall length of the inner seal lip 13 is made sufficiently large (long) and the inclination angle α of the inner seal lip 13 with respect to an imaginary plane orthogonal to the center axis of the metal core 1 is made sufficiently large, Such inconveniences can be prevented. However, in this case, the inner seal lip 13 and the intermediate seal lip 12 provided adjacent to the inner seal lip 13 easily interfere with each other, and good performance of both the seal lips 13 and 12 is secured. It becomes difficult to do.
The present invention has been made in view of such circumstances, and does not impair the performance of one radial seal lip of the two radial seal lips. The present invention has been made to improve the follow-up performance, to ensure sufficient sealing performance, and to suppress an increase in rotational torque and heat generation.
[0011]
[Means for Solving the Problems]
Among the sealing device, the rolling bearing, and the hub unit of the present invention, the sealing device according to claim 1 includes a plurality of sealing devices between an inner raceway provided on the outer peripheral surface of the inner race and an outer raceway provided on the inner peripheral surface of the outer race. A rolling element is provided to be incorporated in a rolling bearing which enables relative rotation between the inner ring and the outer ring, and blocks a gap between an outer peripheral surface of the inner ring and an inner peripheral surface of the outer ring. To this end, the sealing device of the present invention includes a holding member, a sealing material, and two radial sealing lips, similarly to the conventional structure shown in FIGS. The holding member is fixed to one of the outer peripheral surface of the inner race and the inner peripheral surface of the outer race. The seal member is made of an elastic material, and a part of the seal member is fixedly connected to the holding member. Further, each of the radial seal lips is provided on a part of the sealing material, and a front edge thereof is provided on the other of the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring, or The other member is slid or in close proximity to the peripheral surface of the member supported by the other member.
[0012]
In particular, in the sealing device according to claim 1, one of the two radial seal lips is provided with a thick portion provided at a portion closer to a distal end and a portion provided near a proximal end. And a constricted portion having a thickness smaller than the maximum thickness of the thick portion. The other radial seal lip of the two radial seal lips is provided on the peripheral surface of the constricted portion in a state protruding in a direction away from the one peripheral surface. The distal end edge of the other radial seal lip and the distal end edge of the thick portion are supported by a peripheral surface provided on the other of the outer peripheral surface of the inner race and the inner peripheral surface of the outer race or the other. In sliding contact or close proximity to the peripheral surface of the provided member.
[0013]
Further, a rolling bearing according to a second aspect incorporates at least one sealing device according to the first aspect.
A hub unit according to a third aspect of the present invention is a hub for fixing an inner ring or an outer ring to a wheel, and incorporates at least one sealing device according to the first aspect.
[0014]
[Action]
According to the sealing device, the rolling bearing, and the hub unit of the present invention configured as described above, the other radial sealing lip of the two radial sealing lips provided on the sealing member has a mating peripheral surface. It is possible to improve the followability to the movement. For this reason, the change in the tension force of the other radial seal lip can be suppressed. Moreover, in order to improve the followability, it is not necessary to increase the total length of the other seal lip or to increase the inclination angle of the other seal lip with respect to a virtual plane perpendicular to the center axis of the holding member. . Therefore, it is possible to prevent the two radial seal lips from interfering with each other. As a result, without deteriorating the performance of one of the two radial seal lips, the wear of the leading edge of the other radial seal lip can be suppressed, and good sealing performance can be obtained. In addition, it is possible to suppress an increase in the rotational torque and the amount of generated heat.
[0015]
BEST MODE FOR CARRYING OUT THE INVENTION
1 and 2 show a first example of an embodiment of the present invention. The sealing device 14a according to the present invention includes a metal core 1, which is a holding member, a slinger 2, and a sealing material 3a. The core metal 1 is integrally formed by subjecting a metal plate such as a low carbon steel plate to a punching process such as a press process and a plastic process. Such a cored bar 1 has an outer diameter side cylindrical portion 5 that can be fitted and fixed on the inner peripheral surface of an outer end portion of an outer ring 4 (see FIG. 6) constituting a rolling bearing 6, and a shaft of the outer diameter side cylindrical portion 5. An inner ring portion 7 which is bent inward in the diametric direction from the inner edge in the direction (the left edge in FIGS. 1 and 2) has a substantially L-shaped cross section and is entirely annular.
[0016]
In addition, the slinger 2 is integrally formed by punching such as press working and plastic working on a metal plate having excellent corrosion resistance such as a stainless steel plate. Such a slinger 2 includes an inner cylindrical portion 9 that can be fitted and fixed to the outer peripheral surface of an inner ring 8 (see FIG. 6) that constitutes the rolling bearing 6, and an axially outer portion of the inner cylindrical portion 9. An outer ring portion 10 that is bent outward in the diametric direction from an end edge (right end edge in FIGS. 1 and 2) has a substantially L-shaped cross section and is entirely annular.
[0017]
The sealing material 3a is made of an elastic material such as an elastomer such as rubber, and has three sealing lips 11, 12a, and 13a on the outer side, the middle, and the inner side. The connection is fixed. Further, the intermediate seal lip 12a, which corresponds to one radial seal lip described in the claims, has a thick portion 18 provided at a portion near the front end and a thick portion 18 provided at a portion near the base end. A constricted portion 19 having a thickness smaller than the maximum thickness. In addition, the thickness of the thick portion 18 is sharply increased (thickened) near a portion continuous with the constricted portion 19 and is reduced near the leading edge. The inner seal lip 13a, which corresponds to the other radial seal lip described in the claims, is provided at a middle portion of the inner peripheral surface of the constricted portion 19 in a state of protruding radially inward. The total length of the inner seal lip 13a is smaller (shorter) than the total length of the intermediate seal lip 12a. The outer seal lip 11 is inclined radially outward toward the leading edge. Then, the leading edge of the outer seal lip 11 is slid in contact with the inner side surface (the left side surface in FIGS. 1 and 2) of the outer annular portion 10 constituting the slinger 2, and the remaining two seal lips, the intermediate seal, are provided. The leading edge of the lip 12a and the inner seal lip 13a are slid in contact with the outer peripheral surface of the inner cylindrical portion 9 constituting the slinger 2 at a position separated in the axial direction.
[0018]
According to the sealing device, the rolling bearing and the hub unit of the present invention configured as described above, the diameter of the three sealing lips 11, 12a, and 13a can be reduced without deteriorating the performance of the intermediate sealing lip 12a located at the middle. The followability of the innermost inner seal lip 13a with respect to the movement of the peripheral surface of the mating member facing in the direction can be improved, and the sealing performance can be sufficiently ensured. That is, in the case of the present invention, the inner seal lip 13a is provided on the inner peripheral surface of the constricted portion 19 having a reduced thickness at a part of the intermediate seal lip 12a so as to protrude radially inward. I have. Further, the intermediate seal lip 12a can have a large overall length and a large inclination angle with respect to an imaginary plane orthogonal to the central axis of the metal core 1. Therefore, the amount of deformation of the base end portion of the intermediate seal lip 12a with respect to the radial force applied from the outer peripheral surface of the inner cylindrical portion 9 constituting the slinger 2 can be increased. Further, the rigidity of the intermediate seal lip 12a can be reduced at the constricted portion 19. Therefore, the amount of displacement of the leading edge of the inner seal lip 13a with respect to the radial force applied to the inner seal lip 13a from the outer peripheral surface of the inner cylindrical portion 9 can be sufficiently increased. As a result, when the inner ring 8 is tilted or eccentric with respect to the outer ring 4 during use, if the cored bar 1 and the outer peripheral surface of the slinger 2 are partially approached or separated, the inner seal 8 The leading edge of the lip 13a can favorably follow the movement of the outer peripheral surface of the slinger 2. For example, when the inner ring 8 to which the slinger 2 is fixed is eccentric with respect to the outer ring 4 to which the core bar 1 is fixed, as shown in FIG. 2A, a part of the inner seal lip 13a in the circumferential direction is provided. Thus, the leading edge of the inner seal lip 13a tends to be strongly pressed against the outer peripheral surface of the inner cylindrical portion 9. On the other hand, in the case of the present invention, the inner seal lip 12a is connected to the base end of the inner seal lip 13a and the constricted portion 19 is displaced to the outer diameter side. The base end of the seal lip 13a is also displaced to the outer diameter side. For this reason, it is possible to prevent the tightening force between the leading edge of the inner seal lip 13a and the outer peripheral surface of the slinger 2 from becoming excessive. Further, when the inner ring 8 is eccentric with respect to the outer ring 4 as described above, as shown in FIG. The leading edge of the seal lip 13a tends to separate from the outer peripheral surface of the inner cylindrical portion 9. On the other hand, in the case of the present invention, since the constricted portion 19 connecting the base end of the inner seal lip 13a with the intermediate seal lip 12a is displaced toward the inner diameter side, the tightening force becomes too small, The distal end edge can be prevented from separating from the outer peripheral surface of the inner diameter side cylindrical portion 9. 2 is a sliding contact between the middle and inner seal lips 12a and 13a and the slinger 2 when the center axes of the cored bar 1 and the slinger 2 are coincident with each other. Indicates the state.
[0019]
As described above, in the case of the present invention, since the leading edge of the inner seal lip 13a satisfactorily follows the movement of the outer peripheral surface of the slinger 2, it is possible to suppress a change in the tightening force of the inner seal lip 13a. it can. Further, it is not necessary to increase the total length of the inner seal lip 13a or increase the inclination angle α '(FIG. 1) of the inner seal lip 13a with respect to a virtual plane orthogonal to the center axis of the cored bar 1. Therefore, interference between the inner seal lip 13a and the intermediate seal lip 12a can be prevented. As a result, without deteriorating the performance of the intermediate seal lip 12a, it is possible to obtain good sealing performance by suppressing the abrasion of the leading edge of the inner seal lip 13a, and to suppress an increase in rotational torque and heat generation. Can do things.
[0020]
In the case of this example, the three seal lips 11, 12a, and 13a, including the inner seal lip 13a, are all inclined in the outward direction with respect to the flow direction of the fluid toward the respective leading edges. ing. Therefore, the grease sealed in the rolling bearing 6 is appropriately supplied to the sliding contact portion between the leading edge of each of the seal lips 11, 12a, 13a and the slinger 2. Therefore, the lubricating state of each of the sliding contact portions should be maintained well, the rotational torque of the rolling bearing 6 should be kept low, and the sliding contact portions should be covered with grease to improve the sealing performance of each of the sliding contact portions. Can be.
[0021]
Next, FIG. 3 shows a second example of the embodiment of the present invention. In the case of this example, unlike the case of the first example described above, the inner seal lip 13a is a non-contact seal. That is, in the case of the present example, the leading edge of the inner seal lip 13a is closely opposed to the outer peripheral surface of the inner diameter side cylindrical portion 9 constituting the slinger 2 via a minute gap having a thickness dimension d. . In the case of such a present example, the rotational torque can be made smaller than in the case of the first example described above. Also, in the conventional structure shown in FIG. 7 described above, when the inner seal lip 13 is a non-contact seal similarly to this example, the center axis of the slinger 2 is inclined with respect to the center axis of the cored bar 5 during use. In consideration of the possibility that the two members 2 and 5 may be eccentric, the thickness of the gap between the leading edge of the inner seal lip 13 and the outer peripheral surface of the inner cylindrical portion 9 is increased. Must be set. When the thickness of the gap is set to be large as described above, it is difficult to ensure good sealing performance. On the other hand, in the case of the present example, the leading edge of the inner seal lip 13a satisfactorily follows the movement of the outer peripheral surface of the slinger 2. For this reason, even if the thickness dimension d of the minute gap is set small, it is possible to prevent the inner seal lip 13a from coming into contact with the slinger 2, and it is possible to secure good sealing performance while reducing the rotational torque.
Other configurations and operations are the same as those in the first example described above, and therefore, the same reference numerals are given to the same parts, and duplicate description will be omitted.
[0022]
Next, FIG. 4 shows a third example of the embodiment of the present invention. In the case of the present example, unlike the case of the above-described first example, the inner seal lip 13b is moved in the direction toward the inner side in the axial direction (left side in FIG. 4) of the rolling bearing 6 (see FIG. 6) toward the leading edge. Tilted. In the case of such a present example, the grease sealed inside the rolling bearing 6 makes the sliding between the leading edge of the intermediate seal lip 12a and the outer seal lip 11 and the slinger 2 different from the case of the first example described above. It becomes difficult to be supplied to the contact portion. However, in the case of this example, while preventing the interference between the thick portion 18 of the intermediate seal lip 12a and the inner seal lip 13b, the total length of the inner seal lip 13b is increased, and the center axis of the cored bar 1 is increased. Can be increased with respect to an imaginary plane orthogonal to.
Other configurations and operations are the same as those of the first example shown in FIGS. 1 and 2 described above, and therefore, the same reference numerals are given to the same parts, and duplicate description will be omitted.
[0023]
Note that the sealing device of the present invention and the rolling bearing incorporating the same can be implemented regardless of whether the inner ring 8 or the outer ring 4 constituting the rolling bearing 6 rotates during use. Further, the present invention can also be implemented with a structure in which the slinger 2 is internally fitted and fixed to the outer ring 4 and the core 1 having the sealing material 3a coupled to the inner ring 8 is externally fitted and fixed. In this case, the leading edge of the inner seal lip provided on the outer peripheral surface of the intermediate seal lip constituting the seal member 3 a so as to protrude radially outward is slidably in contact with the inner peripheral surface of the slinger 2. Further, the sealing device of the present invention and a rolling bearing incorporating the same have an inner ring 8 which is externally fitted and fixed to an outer peripheral surface of a hub for supporting a wheel, and an outer ring 4 which is a knuckle constituting a suspension system of an automobile. It can also be used by being incorporated in a hub unit that can be freely fitted and fixed in the support hole. In this case, a fixed flange for fixing to the end surface of the knuckle may be formed on the outer peripheral surface of the outer race 4. Further, as shown in FIG. 5, an inner ring 8 having an inner ring raceway 15 on the outer peripheral surface is externally fitted and fixed to the inner peripheral portion (right end portion in FIG. 5) of the hub 20, and the outer peripheral portion of the intermediate portion of the hub 20 is fixed. The sealing device 14a of the present invention can also be incorporated in a hub unit in which another inner ring raceway 15 is formed at a portion deviating from the inner ring 8 in terms of surface. In the case of the hub unit shown in FIG. 5, a fixed-side flange 22 for fixing to the end surface of the knuckle 21 is formed on the outer peripheral surface of the outer ring 4. A rotating flange 23 for fixing wheels is formed on the outer peripheral surface of the hub 21 near the outer end (the part near the left end in FIG. 5).
In the hub unit shown in the figure, the tip of a sealing lip provided on the sealing material 3a like a sealing device 14b incorporated between the outer peripheral surface of the intermediate portion of the hub 20 and the inner peripheral surface of the outer end of the outer ring 4. The present invention can also be applied to a structure in which the rim slides directly on the outer peripheral surface of the hub 20 (or the inner ring 8). Furthermore, the present invention can also be implemented with a hub unit provided with a hub on the outer ring side (rotating outer ring type).
[0024]
【The invention's effect】
Since the present invention is configured and operates as described above, it is possible to realize a sealing device having excellent sealing properties and durability and small rotating torque. This prevents various foreign substances, such as rainwater, mud, and dust, from entering the interior space of the rolling bearing and hub unit, thereby improving the durability of the rolling bearing and hub unit, and improving fuel efficiency and acceleration performance. It is possible to improve the running performance of the vehicle, mainly at the center.
[Brief description of the drawings]
FIG. 1 is a partial cross-sectional view showing a first example of an embodiment of the present invention.
FIG. 2 (A) shows a portion where the core metal and the slinger approached, and FIG. 2 (B) shows a case where the core metal and the slinger moved away from each other with the inner ring to which the slinger was fixed being eccentric with respect to the outer ring to which the core metal was fixed. The figure similar to FIG. 1 which shows a part.
FIG. 3 is a partial cross-sectional view showing a second example of the embodiment of the present invention.
FIG. 4 is a partial cross-sectional view showing the third example.
FIG. 5 is a sectional view showing a hub unit incorporating the sealing device of the present invention.
FIG. 6 is a half sectional view showing a state in which a sealing device having a conventional structure is incorporated in a rolling bearing.
FIG. 7 is a partially enlarged sectional view showing only the sealing device.
8 (A) is a diagram showing a state where the inner ring to which the slinger is fixed is eccentric with respect to the outer ring to which the core metal is fixed, FIG. FIG. 8 is a view similar to FIG. 7, showing a portion where the slinger has moved away.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Core 2 Slinger 3, 3a Sealing material 4 Outer ring 5 Outer diameter side cylindrical part 6 Rolling bearing 7 Inner ring part 8 Inner ring 9 Inner diameter side cylindrical part 10 Outer ring part 11 Outer seal lip 12, 12a Intermediate seal lip 13, 13a, 13b Inner seal lip 14, 14a, 14b Sealing device 15 Inner ring raceway 16 Outer ring raceway 17 Rolling element 18 Thick portion 19 Narrow portion 20 Hub 21 Knuckle 22 Fixed flange 23 Rotation flange

Claims (3)

内輪の外周面に設けた内輪軌道と外輪の内周面に設けた外輪軌道との間に複数の転動体を設けて上記内輪と外輪との相対回転を自在とした転がり軸受に組み込み、これら内輪の外周面と外輪の内周面との間を塞ぐ為、これら内輪の外周面と外輪の内周面とのうちの一方の周面に固定された保持部材と、弾性材により造られてこの保持部材にその一部を結合固定したシール材と、このシール材の一部に設けられて、それぞれの先端縁を、上記内輪の外周面と外輪の内周面とのうちの他方に設けられた周面又はこの他方に支持された部材の周面に摺接又は近接対向させた２本の径方向シールリップとを備えた密封装置に於いて、
これら２本の径方向シールリップのうちの一方の径方向シールリップが、先端寄り部分に設けられた肉厚部と、基端寄り部分に設けられた、この肉厚部の最大厚さよりも厚さが小さくなった括れ部とを備えたものであり、上記２本の径方向シールリップのうちの他方の径方向シールリップが、上記括れ部の周面に、上記一方の周面から離れる方向に突出する状態で設けられたものであり、上記他方の径方向シールリップの先端縁と上記肉厚部の先端縁とを、上記内輪の外周面と外輪の内周面とのうちの他方に設けられた周面又はこの他方に支持された部材の周面に摺接又は近接対向させている事を特徴とする密封装置。A plurality of rolling elements are provided between an inner raceway provided on the outer peripheral surface of the inner race and an outer raceway provided on the inner peripheral surface of the outer race, and these rolling elements are incorporated into a rolling bearing that allows relative rotation between the inner race and the outer race. In order to close the gap between the outer peripheral surface of the outer ring and the inner peripheral surface of the outer ring, a holding member fixed to one of the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring, A sealing member having a part thereof fixedly connected to the holding member, and a tip edge provided on a part of the sealing member, and a leading edge provided on the other of the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring. A sealing device comprising two radial sealing lips that are slidably in contact with or close to the peripheral surface of the member supported by the other or the other.
One of the two radial seal lips has a thicker portion provided near the distal end and a thicker portion provided near the base end than the maximum thickness of the thickened portion. And the other radial seal lip of the two radial seal lips is provided on the peripheral surface of the constricted portion in a direction away from the one peripheral surface. The tip end edge of the other radial seal lip and the tip end edge of the thick portion are provided on the other of the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring. A sealing device, wherein the sealing device is slidably in contact with or close to a peripheral surface provided or a peripheral surface of a member supported by the other. 請求項１に記載した密封装置を少なくとも１個組み込んだ転がり軸受。A rolling bearing incorporating at least one sealing device according to claim 1. 内輪又は外輪が車輪を固定する為のハブであり、請求項１に記載した密封装置を少なくとも１個組み込んだハブユニット。A hub unit, wherein the inner ring or the outer ring is a hub for fixing the wheel, and at least one sealing device according to claim 1 is incorporated therein.
JP2002248756A 2002-08-28 2002-08-28 Sealing device, and rolling bearing and hub unit with the device integrated Pending JP2004084858A (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004016351A1 (en) * 2004-04-02 2005-10-20 Ina Schaeffler Kg Release bearing with a limitation of the sealing lip movement
JP2009138835A (en) * 2007-12-05 2009-06-25 Jtekt Corp Sealing device for bearing

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004016351A1 (en) * 2004-04-02 2005-10-20 Ina Schaeffler Kg Release bearing with a limitation of the sealing lip movement
EP1589242A1 (en) 2004-04-02 2005-10-26 INA-Schaeffler KG Release bearing provided with a sealing lip and a device limiting the amplitude of its movement
EP1589242B1 (en) * 2004-04-02 2012-05-09 Schaeffler Technologies AG & Co. KG Release bearing provided with a sealing lip and a device limiting the amplitude of its movement
JP2009138835A (en) * 2007-12-05 2009-06-25 Jtekt Corp Sealing device for bearing

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