JP4333116B2 - Rolling bearing sealing device - Google Patents

Rolling bearing sealing device Download PDF

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Publication number
JP4333116B2
JP4333116B2 JP2002314246A JP2002314246A JP4333116B2 JP 4333116 B2 JP4333116 B2 JP 4333116B2 JP 2002314246 A JP2002314246 A JP 2002314246A JP 2002314246 A JP2002314246 A JP 2002314246A JP 4333116 B2 JP4333116 B2 JP 4333116B2
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Japan
Prior art keywords
ring member
lip
outer ring
rolling bearing
sealing device
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Expired - Fee Related
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JP2002314246A
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Japanese (ja)
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JP2004150484A (en
Inventor
喜重 武田
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JTEKT Corp
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JTEKT Corp
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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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3436—Pressing means
    • F16J15/3456—Pressing means without external means for pressing the ring against the face, e.g. slip-ring with a resilient lip
    • 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
    • F16C19/187—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 with all four raceways integrated on parts other than race rings, e.g. fourth generation hubs
    • 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
    • F16C33/7873—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 single sealing ring of generally L-shaped cross-section
    • F16C33/7876—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 single sealing ring of generally L-shaped cross-section with sealing lips
    • 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
    • F16C19/186—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 with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • 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
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Of Bearings (AREA)
  • Rolling Contact Bearings (AREA)
  • Sealing With Elastic Sealing Lips (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明は、例えば、車軸用転がり軸受装置に用いられる密封装置に関する。
【０００２】
【従来の技術】
従来の車軸用転がり軸受装置に用いられる密封装置には、円筒面に接触するラジアルリップ、径方向に沿う環状面に接触するアキシャルリップ、ラジアルリップ、アキシャルリップの中間に配置されて湾曲面に接触する中間リップとを備えたものがある（例えば、特許文献１参照）。
【０００３】
以下、図４および図５に基づいて、従来の車軸用転がり軸受装置に用いられる密封装置について説明する。図４は、車軸用転がり軸受装置の全体構成を示す断面図、図５は密封装置の拡大断面図である。
【０００４】
車軸用転がり軸受装置１００は、車体側に非回転に支持される外輪部材１０１と、この外輪部材１０１に２列の玉１０２，１０３を介して軸心回りに回転自在に支持される内輪部材１０４と、外輪部材１０１と内輪部材１０４との間の環状空間１０５内の潤滑剤が外部に漏れるのを防止するとともに、泥水等が環状空間１０５内に侵入するのを防止するための密封装置１０６とを備えている。
【０００５】
内輪部材１０４は、車両アウタ側の外周部に、径方向外向きに突出して形成されたハブフランジ１０７を有する。内輪部材１０４は、一方列の玉１０２の内輪軌道面に連続する肩部１０８に円筒面１０９を有し、ハブフランジ１０７の側面１１０と円筒面１０９とは、湾曲面１１１を介して連続している。
【０００６】
図５に示すように、密封装置１０６は、外輪部材１０１の車両アウタ側内周面に嵌着される芯金１１２と、この芯金１１２に一体的に形成される弾性シール部材１１３とから構成される。
【０００７】
この弾性シール部材１１３は、芯金１１２に固着される本体部１１４と、この本体部１１４に一体に形成されてハブフランジ１０７の側面１１０に接触するサイドリップ（アキシャルリップ）１１５と、肩部の円筒面に接触する主リップ（ラジアルリップ）１１６と、サイドリップ１１５と主リップ１１６の間に配置されて湾曲面１１１に接触する補助リップ１１７とを備えている。
【０００８】
これらリップのうち補助リップ１１７は、本体部１１４側の基部１１７ａにおける径方向の厚みが最も厚く、先端接触部１１７ｂは径方向外向きに傾斜するとともに、厚みは基部１１７ａから次第に薄くなるように形成されている。この構成により、内輪部材１０４を外輪部材１０１に組込んだ際に、先端接触部１１７ｂが湾曲面１１１に接触し、環状空間１０５を密封するものである。
【０００９】
【特許文献１】
特開平１１−２１０７７０号（第３頁，第１図，第２図）
【００１０】
【発明が解決しようとする課題】
上記従来の密封装置１０６において、補助リップ１１７は、サイドリップ１１５と主リップ１１６の間に配置されて湾曲面１１１に接触するものでるため、径方向および軸方向双方の位置管理が必要となる。
【００１１】
加えて、補助リップ１１７は、本体部１１４側の基部１１７ａの厚みに比べて先端接触部１１７ｂの厚みは薄く形成されている。このため、湾曲面１１１に接触する際、場合によっては図５の仮想線に示すように、補助リップ１１７の先端接触部１１７ｂが基部１１７ａとの境界部分で湾曲して、湾曲面１１１に必要以上の大きな面積をもって面当たりし、適切なシール性能が得られないことが考えられる。
【００１２】
【課題を解決するための手段】
本発明における転がり軸受の密封装置は、外輪部材と、この外輪部材に転動体を介して配置される内輪部材との間に配置されて前記外輪部材と内輪部材との間の環状空間を密封するために、前記内輪部材に形成された円筒面とこの円筒面から軸方向に離隔した位置で径方向に突出する環状面とを連続する湾曲面に弾性的に接触するシールリップが、前記外輪部材の内周面側に取付けられる環状の本体部に一体的に形成され、このシールリップは、前記本体部側の基部と、前記内輪部材の湾曲面に接触する接触部と、前記基部と前記接触部との間の中間部とを含み、前記基部から前記接触部に向けて拡径する形状に形成されるとともに、前記中間部から前記接触部に向けて径方向の厚みが薄くなる形状に形成されており、前記中間部の径方向の厚みに比べて前記基部の径方向の厚みが薄く形成されている。
【００１３】
上記構成のように、中間部の径方向の厚みに比べて基部の径方向の厚みを薄く形成したことによれば、シールリップの接触部が湾曲面に接触する際に、湾曲面との接触に伴なう圧力がシールリップに働くと、本体部側の、剛性の低い基部に前記圧力が集中し易くなり、このためシールリップは、基部を中心に折曲がるように弾性変形する。このため、接触部が湾曲面に必要以上に大きな面積で面当たりすることでシール性能を低下させてしまうといった状態を回避できる。
【００１４】
特に湾曲面は、軸方向と径方向の面圧管理が必要となり、このため適度な面圧をもって接触部を湾曲面に接触させることは難しかったが、本発明では、シールリップが湾曲面に接触する際の圧力が、剛性の低い接触部に集中し易くなって、接触部が湾曲面に必要以上に大きな面積で面当たりするのを防止できるため、多少の組付け誤差があったとしても、面圧の管理が容易となる。
【００１５】
また、本発明の密封装置は、前記内輪部材の円筒面に接触するラジアルリップおよび環状面に接触するアキシャルリップを有している。
【００１６】
この構成によれば、３個のシールリップによって環状空間を確実に密封することができる。
【００１７】
本発明の密封装置が用いられる転がり軸受は、主として内輪回転型の転がり軸受である。そして本発明の密封装置は、転がり軸受の内輪部材に、円筒面と、この円筒面から軸方向に離隔した位置で径方向に突出する環状面、および円筒面と環状面とを連続する湾曲面を有する転がり軸受であれば、適用可能である。
【００１８】
【発明の実施の形態】
以下、本発明の第１の実施形態に係る密封装置を、車軸用転がり軸受装置に付設した場合を例に、図面に基づいて説明する。
【００１９】
図１は駆動側に設けられる車軸用転がり軸受装置の全体構成を示す断面図、図２はシール装置の拡大半断面図である
まず、車軸用転がり軸受装置１の全体構成を説明すると、これは、車体側に非回転に組込まれる外輪部材２と、この外輪部材２に、冠形保持器３ａ，４ａによって円周方向等配位置にそれぞれ保持された２列の玉（転動体の一例）３，４を介して軸心５回りに回転自在に支持される内輪部材６とを備えている。
【００２０】
外輪部材２の外周面途中には、径方向外向きに突出する支持フランジ７が形成され、この支持フランジ７が、車体側に組込まれた図示しないナックルに結合されることで、外輪部材２が車体に非回転（軸心５回りに非回転）に支持される。外輪部材２の内周面に、軸方向に離隔して両列の玉３，４の外輪軌道面２ａ，２ｂが形成されている。
【００２１】
内輪部材６は、外周面に一方列（車両アウタ側）の玉３の内輪軌道面８ａが形成された筒状のハブホイール８と、このハブホイール８の中心穴にスプライン８ｂを介して挿通する中空断面状の軸部９を一体形成した不図示の等速ジョイントの椀形外輪部材１０とから構成されている。この椀形外輪部材１０の外周面に、他方列の玉４の内輪軌道面１０ａが形成されている。
【００２２】
椀形外輪部材１０の軸部９の車両アウタ側端部は、径方向外向きに拡径されるようハブホイール８の車両アウタ側端面に対してかしめられ、玉３，４に対して所定量の予圧が付与されている。
【００２３】
ハブホイール８は、その外周面途中に、ブレーキディスク１１およびタイヤホイール１２を重ねて取付けるための、径方向外向きに突出形成したハブフランジ１３が形成されている。なお前記等速ジョイントは、不図示の駆動軸の回転を車輪（ブレーキディスク１１およびタイヤホイール１２）に伝達するものである。
【００２４】
外輪部材２と内輪部材６の間の環状空間１４を、その車両インナ側および車両アウタ側でそれぞれ密封するための密封装置１５，１６が設けられている。これら密封装置１５，１６は、環状空間１４内の潤滑剤が外部に漏れるのを防止するとともに、泥水等が環状空間１４内に侵入するのを防止する機能を有する。
【００２５】
車両インナ側の密封装置１５は、外輪部材２の車両インナ側内周面に嵌着された芯金１７と、この芯金１７に一体的に形成されて、椀形外輪部材１０の外周曲面に３箇所で接触するリップ部１８ａ，１８ｂ，１８ｃを有する弾性シール体１９とを有する。芯金１７の外周部は軸方向（車両インナ側）に延長されて延長部２０が形成されている。
【００２６】
椀形外輪部材１０の外周面に断面コ字形の環体２１が嵌着され、この環体２１が延長部２０を囲繞することで、環体２１と延長部２０との間でラビリンス隙間、すなわちシール用隙間が形成されている。リップ部１８ａ，１８ｂは椀形外輪部材１０の斜面に接触するものであり、リップ部１８ｃは、椀形外輪部材１０の、ほぼ円筒面とみなすことができる緩やかな曲面に接触するものである。なお、これらリップ部１８ａ，１８ｂ，１８ｃは、それぞれ椀形外輪部材１０の回転によって、椀形外輪部材１０の外周面に接触した状態で摺動するものである。
【００２７】
次に、車両アウタ側の密封装置１６の構成を説明する。図２に示すように、この密封装置１６は、外輪部材２の車両アウタ側内周面に装着される芯金２５を有する。この芯金２５は、外輪部材２の内周面に嵌着する筒状の嵌着部２６と、この嵌着部２６の車両アウタ側端部から径方向内方に向けて延長された環状の取付け部２７とから構成されている。この取付け部２７は、嵌着部２６側の第一環状部２８と、この第一環状部２８の内径側端部から段付部２９を介して一体的に形成される第二環状部３０とから構成される。
【００２８】
また、この密封装置１６は、芯金２５に取付けられる合成ゴム製の弾性シール体３１を有する。この弾性シール体３１は、芯金２５の取付け部２７に一体的に形成される環状の本体部３２と、この本体部３２の別々の箇所に一体的に形成される３個のシールリップから形成されている。
【００２９】
すなわちこのシールリップは、ハブフランジ１３における車両インナ側の径方向側面（軸心５に対して垂直方向に沿う面）３５に接触するサイドリップ（「アキシャルリップ」とも呼ぶ）３６と、ハブホイール８において一方列の内輪軌道面８ｂに連続する肩部３７の円筒面（軸心５に平行な円筒面）３８に接触する主リップ（「ラジアルリップ」とも呼ぶ）３９と、サイドリップ３６と主リップ３９の間に配置される補助リップ４０とを備えている。
【００３０】
サイドリップ３６、主リップ３９および補助リップ４０は、それぞれ所定の径方向の厚みを有して円筒状（円錐台状）に形成されている。なお、これらサイドリップ３６、主リップ３９および補助リップ４０は、ハブホイール８の回転によって、ハブホイール８の周面に接触して摺動するものである。
【００３１】
サイドリップ３６は、弾性シール体３１の径方向中間部位に形成され、弾性シール体３１側の基部３６ａと、径方向側面３５に接触する接触部３６ｂとを備える。主リップ３９は、弾性シール体３１の径方向内方部位に形成され、弾性シール体３１側の基部３９ａと、円筒面３８に接触する接触部３９ｂとを備える。
【００３２】
サイドリップ３６における基部３６ａと接触部３６ｂとの径方向の厚みを比較した場合、基部３６ａの厚みの方が接触部３６ｂの厚みよりも大きい値に形成されている。これにより、基部３６ａの剛性に比べて接触部３６ｂの剛性の方が低い。
【００３３】
主リップ３９における基部３９ａと接触部３９ｂとの径方向の厚みを比較した場合、基部３９ａの厚みの方が接触部３９ｂの厚みより大きい値に形成されされている。これにより、基部３９ａの剛性に比べて接触部３９ｂの剛性の方が低い。
【００３４】
次に、補助リップ４０の構成を詳細に説明する。この補助リップ４０は、弾性シール体３１上のサイドリップ３６と主リップ３９との間に配置して形成される。また補助リップ４０は、径方向側面３５および円筒面３８を連続する円弧状の湾曲面４１に接触する接触部４３を有する。また補助リップ４０は、本体部３２の径方向内方部位に、基部４４が一体的に形成される。接触部４３と基部４４との間には中間部４５を有する。
【００３５】
未だ外輪部材２とハブホイール８との間に密封装置１６を組込んでいない状態、あるいは外輪部材２にハブホイール８を組込んでいない状態、すなわち補助リップ４０に弾性応力が働いていないときには、補助リップ４０は仮想線（図２参照）の状態を保持している。この状態で、基部４４の径方向厚みｔ１、中間部４５の径方向厚みｔ３、接触部４３の径方向厚みｔ２は、ｔ２＜ｔ１＜ｔ３の関係を満足している。すなわちこの関係により、各部の剛性は、接触部４３＜基部４４＜中間部４５の関係を満たしている。
【００３６】
上記構成において、密封装置１６は、車軸用転がり軸受装置１を組立てるにあたり、両列の玉３，４を組込んだ後に外輪部材２の車両アウタ側内周面に芯金２５の嵌着部２６を嵌込むようにして装着する。勿論この状態においては、密封装置１６のサイドリップ３６、主リップ３９、および補助リップ４０は無負荷の状態であって、弾性応力が発生しておらず、図２の仮想線で示すように、それぞれ変形前の状態にある。
【００３７】
次に、外輪部材２に軸方向（車両アウタ側）からハブホイール８を所定位置まで挿入するように装着すると、ハブホイール８の円筒面３８に主リップ３９の接触部３９ｂが接触し、ハブホイール８の湾曲面４１に補助リップ４０の接触部４３が接触し、ハブフランジ１３の径方向側面３５にサイドリップ３６の接触部３６ｂが接触する。
【００３８】
主リップ３９では、円筒面３８すなわち径方向での接触状態の管理が必要であり、サイドリップ３６では径方向側面３５すなわち軸方向での接触状態の管理が必要である。しかし、主リップ３９およびサイドリップ３６では、上記のように径方向あるいは軸方向どちらか一方向の管理が主となるので、その接触状態の管理は比較的容易である。
【００３９】
ところで、上述したように、主リップ３９における基部３９ａと接触部３９ｂとでは、基部３９ａの厚みの方が接触部３９ｂの厚みより大きい値に形成されされていることから、基部３９ａの剛性に比べて接触部３９ｂの剛性の方が低くなっている。このため、ハブホイール８を外輪部材２に軸方向から所定位置まで挿入した場合、主リップ３９は、基部３９ａを起点として全体が軸心５に向けて湾曲するように撓んで、接触部３９ｂの先端部が適度な面圧（緊縛力）をもって円筒面３８に接触する。
【００４０】
また、上述したように、サイドリップ３６における基部３６ａと接触部３６ｂとでは、基部３６ａの厚みの方が接触部３６ｂの厚みよりも大きい値に形成されていることから、基部３６ａの剛性に比べて接触部３６ｂの剛性の方が低くなっている。このため、ハブホイール８を外輪部材２に軸方向から所定位置まで挿入し、椀形外輪部材１０の軸部９の車両アウタ側端部を、ハブホイール８の車両アウタ側端面に対してかしめた場合、サイドリップ３６は、基部３６ａを起点として全体が径方向に沿う方向に湾曲するように撓んで、接触部３６ｂの先端部が適度な面圧をもって、径方向側面３５に適度な面圧でもって接触する。
【００４１】
ところで補助リップ４０は、湾曲面４１に接触するものであるため、径方向ならびに軸方向双方の接触状態の管理が必要であり、その接触状態の管理は一般に難しい。すなわち、図４で示した従来の補助リップ１１７では、基部１１７ａの径方向の厚みが最も厚く、接触部１１７ｂの厚みは基部１１７ａから次第に薄くなるように形成されて、接触部１１７ｂ側の剛性が基部１１７ａ側の剛性に比べて低い。このため、内輪部材１０４を外輪部材１０１に組込んだ際に、補助リップ１１７全体が大きく湾曲して接触部１１７ｂの径方向側面１１０に接触する。
【００４２】
しかし、本発明の実施形態における補助リップ４０は、基部４４の厚みｔ１が、中間部４５の厚みｔ２に比べて薄く、剛性が低い。さらに補助リップ４０において、基部４４は径方向側面３５からは中間部４５、接触部４３よりも遠い位置にある。加えて、補助リップ４０は、基部４４から接触部４３に向けて全体として拡径するような形状に形成されている。
【００４３】
このため、ハブホイール８を外輪部材２に軸方向から所定位置まで挿入して、椀形外輪部材１０の軸部９の車両アウタ側端部を、ハブホイール８の車両アウタ側端面に対してかしめた場合、補助リップ４０は、基部４４を中心（支点）として直線的に拡径するよう弾性変形することになる。このため、接触部４３の先端部が必要以上に大きな面積でもって湾曲面４１に接触することなく、接触部４３の先端隅部近傍が適度な面圧（面積）をもって湾曲面４に接触する。
【００４４】
このように、補助リップ４０が基部４４を中心として直線的に拡径するよう弾性変形することによれば、補助リップ４０が湾曲面４１に接触する際の面圧が定圧的になるので、面圧の管理が容易となり、製品（車軸用転がり軸受装置１）ごとのシール性能のばらつきを抑えることができる。
【００４５】
加えて、接触部４３の先端部が適度な面圧をもって湾曲面４１の所定位置に接触することで、内輪部材６の回転トルクを必要以上に高くしてしまうこともない。
【００４６】
図３に基づいて、第２の実施形態を説明する。上記実施形態では駆動輪側に用いる車軸用転がり軸受装置１を例にシール装置１６の説明したが、本発明のシール装置１６は、従動輪側に用いられる車軸用転がり軸受装置５０にも適用可能である。
【００４７】
同図に示す車軸用転がり軸受装置５０は、車体側に非回転に支持される外輪部材５１と、この外輪部材５１の内周面に形成された外輪軌道面５１ａ，５１ｂそれぞれに複数個の玉５２，５３を介して軸心５４回りに回転自在に支持された内輪部材５５と、外輪部材５１の車両インナ側に嵌着される保護キャップ５６とを備えている。
【００４８】
内輪部材５５は、ハブ軸５７と、このハブ軸５７の車両インナ側の環状凹部５８に嵌着する筒状部材５９とから構成される。ハブ軸５７は、外周面途中に一方列の玉５２の内輪軌道面５７ａが形成され、筒状部材５９の外周面に他方列の玉５３の内輪軌道面５９ａが形成されている。
【００４９】
内輪軌道面５７ａに連続するハブ軸５７の肩部６０に円筒面６１が形成されている。この円筒面６１よりも車両アウタ側の外周面に、ハブフランジ６２が形成されている。このハブフランジ６２の車両インナ側の径方向側面６３と前記円筒面６１とは、湾曲面６４で連続している。また、ハブ軸５７の車両インナ側端部にねじ部６５が形成され、このねじ部６５にナット部材６６が螺着されて筒状部材５９に圧接されることで、所定の予圧が付与されている。
【００５０】
密封装置１６の構成は上記第１の実施形態と同様であり、シールリップは、ハブフランジ６２における車両インナ側の径方向側面６３に接触するサイドリップ３６と、肩部６０の円筒面６１に接触する主リップ３９と、サイドリップ３６と主リップ３９の間に配置される補助リップ４０とを備えている。サイドリップ３６、主リップ３９および補助リップ４０の構成は、上記実施形態と同様である。また芯金２５の構成も上記実施形態と同様であり、これは、外輪部材５１の車両アウタ側内周面に嵌着される。
【００５１】
上記のような構成の車軸用転がり軸受装置５０の密封装置１６においても、上記実施形態と同様に、補助リップ４０が湾曲面６４に接触する際の面圧の管理が容易となり、製品（車軸用転がり軸受装置５０）ごとのシール性能のばらつきを抑えることができる。
【００５２】
上記各実施形態では、径方向および軸方向の面圧管理を要する補助リップ４０の形状を工夫して、シール性能のばらつきを抑えるようにした。しかし、本発明はこれに限定されるものではなく、場合によっては、主リップ３９およびサイドリップ３６も補助リップ４０と同様の形状に形成してもよい。この場合は、さらに確実にシール性能のばらつきを抑えることができる。
【００５３】
【発明の効果】
以上の説明から明らかな通り、本発明の密封装置によれば、径方向と軸方向双方の接触面圧を管理しなければならない場合であっても、その管理を容易に行い得る。
【図面の簡単な説明】
【図１】 本発明の実施形態を示す車軸用転がり軸受装置の全体構成を示す断面図である。
【図２】 同じく車軸用転がり軸受装置に用いられる密封装置の拡大断面図である。
【図３】 他の実施形態を示す車軸用転がり軸受装置の半断面図である。
【図４】 従来の車軸用転がり軸受装置の全体構成を示す断面図である。
【図５】 同じく車軸用転がり軸受装置に用いられる密封装置の拡大断面図である。
【符号の説明】
１ 車軸用転がり軸受装置
２ 外輪部材
６ 内輪部材
８ ハブホイール
９ 軸部
１０ 椀形外輪部材
１３ ハブフランジ
１４ 環状空間
１５，１６ 密封装置
２５ 芯金
２７ 取付け部
２８ 第一環状部
２９ 段付部
３０ 第二環状部
３１ 弾性シール体
３２ 本体部
３５ 径方向側面
３６ サイドリップ
３８ 円筒面
３９ 主リップ
４０ 補助リップ
４１ 湾曲面
４３ 接触部
４４ 基部
４５ 中間部[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a sealing device used in, for example, a rolling bearing device for an axle.
[0002]
[Prior art]
The sealing device used in the conventional rolling bearing device for an axle is arranged between the radial lip that contacts the cylindrical surface, the axial lip that contacts the annular surface along the radial direction, the radial lip, and the axial lip, and contacts the curved surface. There is a thing provided with the intermediate lip which performs (for example, refer to patent documents 1).
[0003]
Hereinafter, based on FIG. 4 and FIG. 5, the sealing device used for the conventional rolling bearing device for axles is demonstrated. 4 is a cross-sectional view showing the overall configuration of the rolling bearing device for an axle, and FIG. 5 is an enlarged cross-sectional view of the sealing device.
[0004]
An axle rolling bearing device 100 includes an outer ring member 101 that is non-rotatably supported on the vehicle body side, and an inner ring member 104 that is supported by the outer ring member 101 via two rows of balls 102 and 103 so as to be rotatable about an axis. And a sealing device 106 for preventing the lubricant in the annular space 105 between the outer ring member 101 and the inner ring member 104 from leaking to the outside and preventing muddy water or the like from entering the annular space 105. It has.
[0005]
The inner ring member 104 has a hub flange 107 formed on the outer peripheral portion on the vehicle outer side so as to protrude outward in the radial direction. The inner ring member 104 has a cylindrical surface 109 on a shoulder 108 that is continuous with the inner ring raceway surface of the balls 102 in one row, and the side surface 110 and the cylindrical surface 109 of the hub flange 107 are continuously connected via a curved surface 111. Yes.
[0006]
As shown in FIG. 5, the sealing device 106 includes a cored bar 112 that is fitted to the vehicle outer side inner peripheral surface of the outer ring member 101, and an elastic seal member 113 that is integrally formed with the cored bar 112. Is done.
[0007]
The elastic seal member 113 includes a main body 114 fixed to the metal core 112, a side lip (axial lip) 115 that is integrally formed with the main body 114 and contacts the side surface 110 of the hub flange 107, and a shoulder lip. A main lip (radial lip) 116 that contacts the cylindrical surface and an auxiliary lip 117 that is disposed between the side lip 115 and the main lip 116 and contacts the curved surface 111 are provided.
[0008]
Of these lips, the auxiliary lip 117 has the largest thickness in the radial direction at the base portion 117a on the main body 114 side, the tip contact portion 117b is inclined outward in the radial direction, and the thickness gradually decreases from the base portion 117a. Has been. With this configuration, when the inner ring member 104 is assembled into the outer ring member 101, the tip contact portion 117 b comes into contact with the curved surface 111 and seals the annular space 105.
[0009]
[Patent Document 1]
Japanese Patent Application Laid-Open No. 11-210770 (page 3, FIGS. 1 and 2)
[0010]
[Problems to be solved by the invention]
In the above-described conventional sealing device 106, the auxiliary lip 117 is disposed between the side lip 115 and the main lip 116 and contacts the curved surface 111. Therefore, position management in both the radial direction and the axial direction is required.
[0011]
In addition, the auxiliary lip 117 is formed such that the tip contact portion 117b is thinner than the base portion 117a on the main body 114 side. For this reason, when contacting the curved surface 111, the tip contact portion 117b of the auxiliary lip 117 is curved at the boundary portion with the base portion 117a as shown by the phantom line in FIG. It is conceivable that the surface contact with a large area of cannot be obtained and appropriate sealing performance cannot be obtained.
[0012]
[Means for Solving the Problems]
The sealing device for a rolling bearing according to the present invention is disposed between an outer ring member and an inner ring member disposed on the outer ring member via a rolling element, and seals an annular space between the outer ring member and the inner ring member. Therefore, a seal lip that elastically contacts a curved surface between a cylindrical surface formed on the inner ring member and an annular surface protruding in a radial direction at a position spaced apart from the cylindrical surface in the axial direction includes the outer ring member. The seal lip is formed integrally with an annular main body portion attached to the inner peripheral surface side of the main body portion, a base portion on the main body portion side, a contact portion that contacts the curved surface of the inner ring member, and the base portion and the contact portion. An intermediate portion between the intermediate portion and the contact portion, and a shape that increases in diameter from the base portion toward the contact portion, and a shape in which a radial thickness decreases from the intermediate portion toward the contact portion. It is, in the radial direction of the intermediate portion Radial thickness of the base than the body is formed thin.
[0013]
According to the configuration in which the radial thickness of the base portion is made thinner than the radial thickness of the intermediate portion as in the above configuration, when the contact portion of the seal lip contacts the curved surface, contact with the curved surface is achieved. When the pressure accompanying the pressure acts on the seal lip, the pressure tends to concentrate on the base portion having low rigidity on the main body side, and the seal lip is elastically deformed so as to bend around the base portion. For this reason, it is possible to avoid a state in which the sealing performance is deteriorated due to the contact portion contacting the curved surface with an area larger than necessary.
[0014]
Especially for curved surfaces, it is necessary to manage the surface pressure in the axial direction and the radial direction. For this reason, it was difficult to bring the contact portion into contact with the curved surface with an appropriate surface pressure. However, in the present invention, the seal lip contacts the curved surface. Since the pressure at the time of making it easy to concentrate on the contact part with low rigidity and preventing the contact part from hitting the curved surface with an area larger than necessary, even if there is some assembly error, It becomes easy to manage the surface pressure.
[0015]
The sealing device of the present invention has a radial lip that contacts the cylindrical surface of the inner ring member and an axial lip that contacts the annular surface.
[0016]
According to this configuration, the annular space can be reliably sealed by the three seal lips.
[0017]
The rolling bearing in which the sealing device of the present invention is used is mainly an inner ring rotating type rolling bearing. The sealing device of the present invention includes a cylindrical surface, an annular surface projecting in a radial direction at a position axially spaced from the cylindrical surface, and a curved surface in which the cylindrical surface and the annular surface are continuous. If it is a rolling bearing which has, it is applicable.
[0018]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, the case where the sealing device according to the first embodiment of the present invention is attached to a rolling bearing device for an axle will be described with reference to the drawings.
[0019]
FIG. 1 is a sectional view showing an overall configuration of an axle rolling bearing device provided on the drive side, and FIG. 2 is an enlarged half sectional view of a seal device. First, an overall configuration of an axle rolling bearing device 1 will be described. The outer ring member 2 that is incorporated non-rotatingly on the vehicle body side, and two rows of balls (an example of a rolling element) 3 held on the outer ring member 2 at the circumferentially equidistant positions by the crown-shaped cages 3a and 4a , 4 and an inner ring member 6 that is rotatably supported around an axis 5.
[0020]
A support flange 7 that protrudes radially outward is formed in the middle of the outer peripheral surface of the outer ring member 2, and this support flange 7 is coupled to a knuckle (not shown) incorporated on the vehicle body side, so that the outer ring member 2 is It is supported by the vehicle body in a non-rotating manner (non-rotating around the axis 5). Outer ring raceway surfaces 2 a and 2 b of the balls 3 and 4 in both rows are formed on the inner peripheral surface of the outer ring member 2 so as to be separated from each other in the axial direction.
[0021]
The inner ring member 6 is inserted through a cylindrical hub wheel 8 in which the inner ring raceway surface 8a of the balls 3 in one row (vehicle outer side) is formed on the outer peripheral surface, and a center hole of the hub wheel 8 through a spline 8b. It is composed of a saddle-shaped outer ring member 10 of a constant velocity joint (not shown) in which a shaft section 9 having a hollow cross section is integrally formed. The inner ring raceway surface 10 a of the balls 4 in the other row is formed on the outer peripheral surface of the saddle-shaped outer ring member 10.
[0022]
The vehicle outer side end portion of the shaft portion 9 of the bowl-shaped outer ring member 10 is caulked against the vehicle outer side end surface of the hub wheel 8 so as to expand radially outward, and a predetermined amount with respect to the balls 3 and 4. The preload is given.
[0023]
The hub wheel 8 is formed with a hub flange 13 projecting outward in the radial direction for attaching the brake disk 11 and the tire wheel 12 in an overlapping manner on the outer peripheral surface thereof. The constant velocity joint transmits rotation of a drive shaft (not shown) to the wheels (brake disc 11 and tire wheel 12).
[0024]
Sealing devices 15 and 16 are provided for sealing the annular space 14 between the outer ring member 2 and the inner ring member 6 on the vehicle inner side and the vehicle outer side, respectively. These sealing devices 15 and 16 have functions of preventing the lubricant in the annular space 14 from leaking to the outside and preventing muddy water and the like from entering the annular space 14.
[0025]
The sealing device 15 on the vehicle inner side is formed on the outer peripheral curved surface of the saddle-shaped outer ring member 10 by being integrally formed with the core metal 17 fitted to the inner peripheral surface of the outer side of the outer ring member 2 and the core metal 17. And an elastic seal body 19 having lip portions 18a, 18b, and 18c that are in contact at three locations. An outer peripheral portion of the cored bar 17 is extended in the axial direction (vehicle inner side) to form an extended portion 20.
[0026]
An annular body 21 having a U-shaped cross section is fitted on the outer peripheral surface of the saddle-shaped outer ring member 10, and the annular body 21 surrounds the extension portion 20, whereby a labyrinth gap between the annular body 21 and the extension portion 20, that is, A sealing gap is formed. The lip portions 18a and 18b are in contact with the inclined surface of the saddle-shaped outer ring member 10, and the lip portion 18c is in contact with a gentle curved surface of the saddle-shaped outer ring member 10 that can be regarded as a substantially cylindrical surface. The lip portions 18a, 18b, and 18c slide in contact with the outer peripheral surface of the bowl-shaped outer ring member 10 by the rotation of the bowl-shaped outer ring member 10, respectively.
[0027]
Next, the configuration of the vehicle outer side sealing device 16 will be described. As shown in FIG. 2, the sealing device 16 includes a cored bar 25 that is attached to the vehicle outer side inner peripheral surface of the outer ring member 2. The metal core 25 includes a cylindrical fitting portion 26 that is fitted to the inner peripheral surface of the outer ring member 2, and an annular shape that extends radially inward from the vehicle outer side end portion of the fitting portion 26. The mounting part 27 is comprised. The attachment portion 27 includes a first annular portion 28 on the fitting portion 26 side, and a second annular portion 30 formed integrally from the inner diameter side end portion of the first annular portion 28 via a stepped portion 29. Consists of
[0028]
The sealing device 16 includes an elastic seal body 31 made of synthetic rubber that is attached to the core metal 25. The elastic seal body 31 is formed of an annular main body portion 32 formed integrally with the attachment portion 27 of the core metal 25 and three seal lips formed integrally at different portions of the main body portion 32. Has been.
[0029]
That is, the seal lip includes a side lip (also referred to as an “axial lip”) 36 that contacts a radial side surface (a surface along a direction perpendicular to the axis 5) 35 of the hub flange 13 on the vehicle inner side, and the hub wheel 8. , A main lip (also referred to as a “radial lip”) 39 that contacts a cylindrical surface (cylindrical surface parallel to the axis 5) 38 of the shoulder 37 that is continuous with the inner ring raceway surface 8b in one row, a side lip 36, and a main lip 39 and an auxiliary lip 40 disposed between the two.
[0030]
Each of the side lip 36, the main lip 39, and the auxiliary lip 40 has a predetermined radial thickness and is formed in a cylindrical shape (conical frustum shape). The side lip 36, the main lip 39, and the auxiliary lip 40 slide in contact with the peripheral surface of the hub wheel 8 by the rotation of the hub wheel 8.
[0031]
The side lip 36 is formed at a radially intermediate portion of the elastic seal body 31 and includes a base portion 36 a on the elastic seal body 31 side and a contact portion 36 b that contacts the radial side surface 35. The main lip 39 is formed at a radially inner portion of the elastic seal body 31 and includes a base portion 39 a on the elastic seal body 31 side and a contact portion 39 b that contacts the cylindrical surface 38.
[0032]
When the radial thicknesses of the base portion 36a and the contact portion 36b in the side lip 36 are compared, the thickness of the base portion 36a is formed to be larger than the thickness of the contact portion 36b. Thereby, the rigidity of the contact part 36b is lower than the rigidity of the base part 36a.
[0033]
When the radial thicknesses of the base portion 39a and the contact portion 39b in the main lip 39 are compared, the thickness of the base portion 39a is formed to be larger than the thickness of the contact portion 39b. Thereby, the rigidity of the contact part 39b is lower than the rigidity of the base part 39a.
[0034]
Next, the configuration of the auxiliary lip 40 will be described in detail. The auxiliary lip 40 is formed between the side lip 36 and the main lip 39 on the elastic seal body 31. The auxiliary lip 40 has a contact portion 43 that contacts an arcuate curved surface 41 that continues the radial side surface 35 and the cylindrical surface 38. The auxiliary lip 40 is integrally formed with a base portion 44 at a radially inward portion of the main body portion 32. An intermediate portion 45 is provided between the contact portion 43 and the base portion 44.
[0035]
When the sealing device 16 is not yet assembled between the outer ring member 2 and the hub wheel 8, or when the hub wheel 8 is not incorporated into the outer ring member 2, that is, when the elastic stress is not acting on the auxiliary lip 40, The auxiliary lip 40 holds the state of the phantom line (see FIG. 2). In this state, the radial thickness t1 of the base portion 44, the radial thickness t3 of the intermediate portion 45, and the radial thickness t2 of the contact portion 43 satisfy the relationship of t2 <t1 <t3. That is, due to this relationship, the rigidity of each portion satisfies the relationship of contact portion 43 <base portion 44 <intermediate portion 45.
[0036]
In the above configuration, the sealing device 16, when assembling the axle rolling bearing device 1, incorporates both rows of balls 3 and 4, and then inserts the fitting portion 26 of the core metal 25 on the vehicle outer side inner peripheral surface of the outer ring member 2. Fit it so that it fits. Of course, in this state, the side lip 36, the main lip 39, and the auxiliary lip 40 of the sealing device 16 are in an unloaded state and no elastic stress is generated, and as shown by a virtual line in FIG. Each is in a state before deformation.
[0037]
Next, when the hub wheel 8 is mounted to the outer ring member 2 so as to be inserted from the axial direction (vehicle outer side) to a predetermined position, the contact portion 39b of the main lip 39 comes into contact with the cylindrical surface 38 of the hub wheel 8, and the hub wheel 8, the contact portion 43 of the auxiliary lip 40 contacts the curved surface 41, and the contact portion 36 b of the side lip 36 contacts the radial side surface 35 of the hub flange 13.
[0038]
The main lip 39 requires management of the cylindrical surface 38, that is, the contact state in the radial direction, and the side lip 36 requires management of the radial side surface 35, that is, the contact state in the axial direction. However, since the main lip 39 and the side lip 36 are mainly managed in one of the radial direction and the axial direction as described above, the management of the contact state is relatively easy.
[0039]
Incidentally, as described above, the base 39a and the contact portion 39b of the main lip 39 are formed such that the thickness of the base portion 39a is larger than the thickness of the contact portion 39b. Thus, the rigidity of the contact portion 39b is lower. For this reason, when the hub wheel 8 is inserted into the outer ring member 2 from the axial direction to a predetermined position, the main lip 39 is bent so that the entire main lip 39 is curved toward the shaft center 5 starting from the base portion 39a. The tip portion contacts the cylindrical surface 38 with an appropriate surface pressure (binding force).
[0040]
Further, as described above, the base portion 36a and the contact portion 36b of the side lip 36 are formed such that the thickness of the base portion 36a is larger than the thickness of the contact portion 36b. Thus, the rigidity of the contact portion 36b is lower. Therefore, the hub wheel 8 is inserted into the outer ring member 2 from the axial direction to a predetermined position, and the vehicle outer side end portion of the shaft portion 9 of the saddle-shaped outer ring member 10 is caulked against the vehicle outer side end surface of the hub wheel 8. In this case, the side lip 36 bends so that the whole of the side lip 36 is curved in the radial direction with the base portion 36a as a starting point, and the distal end portion of the contact portion 36b has an appropriate surface pressure and an appropriate surface pressure on the radial side surface 35. Contact with it.
[0041]
Incidentally, since the auxiliary lip 40 is in contact with the curved surface 41, it is necessary to manage the contact state in both the radial direction and the axial direction, and it is generally difficult to manage the contact state. That is, in the conventional auxiliary lip 117 shown in FIG. 4, the base portion 117a has the largest thickness in the radial direction, and the contact portion 117b has a thickness that gradually decreases from the base portion 117a. Lower than the rigidity on the base 117a side. For this reason, when the inner ring member 104 is assembled into the outer ring member 101, the entire auxiliary lip 117 is greatly curved and contacts the radial side surface 110 of the contact portion 117b.
[0042]
However, in the auxiliary lip 40 in the embodiment of the present invention, the thickness t1 of the base portion 44 is thinner than the thickness t2 of the intermediate portion 45, and the rigidity is low. Further, in the auxiliary lip 40, the base portion 44 is located farther from the radial side surface 35 than the intermediate portion 45 and the contact portion 43. In addition, the auxiliary lip 40 is formed in a shape that expands as a whole from the base portion 44 toward the contact portion 43.
[0043]
Therefore, the hub wheel 8 is inserted into the outer ring member 2 from the axial direction to a predetermined position, and the vehicle outer side end portion of the shaft portion 9 of the saddle-shaped outer ring member 10 is caulked against the vehicle outer side end surface of the hub wheel 8. In this case, the auxiliary lip 40 is elastically deformed so as to linearly expand its diameter with the base portion 44 as the center (fulcrum). For this reason, the tip end portion of the contact portion 43 has an area larger than necessary and does not contact the curved surface 41, and the vicinity of the tip corner portion of the contact portion 43 contacts the curved surface 4 with an appropriate surface pressure (area).
[0044]
As described above, when the auxiliary lip 40 is elastically deformed so as to linearly increase in diameter around the base portion 44, the surface pressure when the auxiliary lip 40 contacts the curved surface 41 becomes constant. The pressure can be easily managed, and variations in the sealing performance for each product (roller bearing device for axle 1) can be suppressed.
[0045]
In addition, since the tip of the contact portion 43 contacts the predetermined position of the curved surface 41 with an appropriate surface pressure, the rotational torque of the inner ring member 6 is not increased more than necessary.
[0046]
A second embodiment will be described with reference to FIG. In the above embodiment, the seal device 16 has been described by taking the axle rolling bearing device 1 used on the drive wheel side as an example, but the seal device 16 of the present invention can also be applied to the axle rolling bearing device 50 used on the driven wheel side. It is.
[0047]
An axle rolling bearing device 50 shown in FIG. 1 includes an outer ring member 51 that is non-rotatably supported on the vehicle body side, and a plurality of balls on each of outer ring raceway surfaces 51 a and 51 b formed on the inner peripheral surface of the outer ring member 51. An inner ring member 55 that is rotatably supported around the shaft center 54 via 52 and 53 and a protective cap 56 that is fitted to the vehicle inner side of the outer ring member 51 are provided.
[0048]
The inner ring member 55 includes a hub shaft 57 and a cylindrical member 59 that fits into the annular recess 58 on the vehicle inner side of the hub shaft 57. In the hub shaft 57, an inner ring raceway surface 57 a of one row of balls 52 is formed in the middle of the outer circumferential surface, and an inner ring raceway surface 59 a of the other row of balls 53 is formed on the outer circumferential surface of the cylindrical member 59.
[0049]
A cylindrical surface 61 is formed on the shoulder 60 of the hub shaft 57 that is continuous with the inner ring raceway surface 57a. A hub flange 62 is formed on the outer peripheral surface of the vehicle outer side with respect to the cylindrical surface 61. A radial side surface 63 on the vehicle inner side of the hub flange 62 and the cylindrical surface 61 are continuous with a curved surface 64. Further, a threaded portion 65 is formed at the vehicle inner side end portion of the hub shaft 57, and a nut member 66 is screwed to the threaded portion 65 and pressed against the tubular member 59, whereby a predetermined preload is applied. Yes.
[0050]
The configuration of the sealing device 16 is the same as that of the first embodiment, and the seal lip contacts the side lip 36 that contacts the radial side surface 63 of the hub flange 62 on the vehicle inner side and the cylindrical surface 61 of the shoulder 60. The main lip 39 and the auxiliary lip 40 disposed between the side lip 36 and the main lip 39 are provided. The configurations of the side lip 36, the main lip 39, and the auxiliary lip 40 are the same as those in the above embodiment. Moreover, the structure of the metal core 25 is the same as that of the said embodiment, and this is fitted to the vehicle outer side inner peripheral surface of the outer ring member 51.
[0051]
Also in the sealing device 16 of the axle rolling bearing device 50 having the above-described configuration, the surface pressure when the auxiliary lip 40 comes into contact with the curved surface 64 can be easily managed, and the product (for the axle) can be obtained. It is possible to suppress variations in the sealing performance for each rolling bearing device 50).
[0052]
In each of the above embodiments, the shape of the auxiliary lip 40 that requires radial and axial surface pressure management is devised to suppress variations in sealing performance. However, the present invention is not limited to this, and the main lip 39 and the side lip 36 may be formed in the same shape as the auxiliary lip 40 in some cases. In this case, variation in sealing performance can be suppressed more reliably.
[0053]
【The invention's effect】
As apparent from the above description, according to the sealing device of the present invention, even when the contact surface pressure in both the radial direction and the axial direction must be managed, the management can be easily performed.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing the overall configuration of an axle rolling bearing device according to an embodiment of the present invention.
FIG. 2 is an enlarged cross-sectional view of a sealing device that is also used in a rolling bearing device for an axle.
FIG. 3 is a half cross-sectional view of a rolling bearing device for an axle showing another embodiment.
FIG. 4 is a cross-sectional view showing an overall configuration of a conventional rolling bearing device for an axle.
FIG. 5 is an enlarged cross-sectional view of a sealing device that is also used in a rolling bearing device for an axle.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Rolling bearing apparatus for axles 2 Outer ring member 6 Inner ring member 8 Hub wheel 9 Shaft part 10 Saddle type outer ring member 13 Hub flange 14 Annular space 15, 16 Sealing device 25 Core metal 27 Mounting part 28 First annular part 29 Stepped part 30 Second annular portion 31 Elastic seal body 32 Main body portion 35 Radial side surface 36 Side lip 38 Cylindrical surface 39 Main lip 40 Auxiliary lip 41 Curved surface 43 Contact portion 44 Base 45 Intermediate portion

Claims (2)

外輪部材と、この外輪部材に転動体を介して配置される内輪部材との間に配置されて前記外輪部材と内輪部材との間の環状空間を密封するための転がり軸受の密封装置であって、
前記内輪部材に形成された円筒面とこの円筒面から軸方向に離隔した位置で径方向に突出する環状面とを連続する湾曲面に弾性的に接触するシールリップが、前記外輪部材の内周面側に取付けられる環状の本体部に一体的に形成され、
このシールリップは、前記本体部側の基部と、前記内輪部材の湾曲面に接触する接触部と、前記基部と前記接触部との間の中間部とを含み、前記基部から前記接触部に向けて拡径する形状に形成されるとともに、前記中間部から前記接触部に向けて径方向の厚みが薄くなる形状に形成されており、
前記中間部の径方向の厚みに比べて前記基部の径方向の厚みが薄く形成された、ことを特徴とする転がり軸受の密封装置。A rolling bearing sealing device disposed between an outer ring member and an inner ring member disposed on the outer ring member via a rolling element to seal an annular space between the outer ring member and the inner ring member. ,
A seal lip that elastically contacts a curved surface between a cylindrical surface formed on the inner ring member and an annular surface projecting in a radial direction at a position spaced apart from the cylindrical surface in the axial direction includes an inner circumference of the outer ring member. Formed integrally with an annular body attached to the surface side,
The seal lip includes a base portion on the main body portion side, a contact portion that contacts the curved surface of the inner ring member, and an intermediate portion between the base portion and the contact portion, from the base portion toward the contact portion. Formed in a shape that expands in diameter, and is formed in a shape in which the radial thickness decreases from the intermediate portion toward the contact portion,
The rolling bearing sealing device according to claim 1, wherein a radial thickness of the base portion is thinner than a radial thickness of the intermediate portion . 請求項１記載の転がり軸受の密封装置において、
前記内輪部材の円筒面に接触するラジアルリップおよび環状面に接触するアキシャルリップを有した、ことを特徴とする転がり軸受の密封装置。The rolling bearing sealing device according to claim 1,
A rolling bearing sealing device comprising: a radial lip that contacts a cylindrical surface of the inner ring member; and an axial lip that contacts an annular surface.
JP2002314246A 2002-10-29 2002-10-29 Rolling bearing sealing device Expired - Fee Related JP4333116B2 (en)

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JP5100056B2 (en) * 2006-08-17 2012-12-19 Ｎｔｎ株式会社 Wheel bearing device
JP2008095919A (en) * 2006-10-16 2008-04-24 Nok Corp Sealing device
JP2009115110A (en) * 2007-11-01 2009-05-28 Nok Corp Sealing device
EP3309430B1 (en) * 2015-06-12 2023-11-22 Nok Corporation Sealing device
JP2017145881A (en) * 2016-02-17 2017-08-24 内山工業株式会社 Sealing device
JP7407526B2 (en) * 2019-07-04 2024-01-04 Nok株式会社 sealing device

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