JP4269422B2 - Rolling bearing unit for wheels - Google Patents

Rolling bearing unit for wheels Download PDF

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Publication number
JP4269422B2
JP4269422B2 JP23371399A JP23371399A JP4269422B2 JP 4269422 B2 JP4269422 B2 JP 4269422B2 JP 23371399 A JP23371399 A JP 23371399A JP 23371399 A JP23371399 A JP 23371399A JP 4269422 B2 JP4269422 B2 JP 4269422B2
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inner ring
small diameter
fitting
ring member
diameter portion
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JP2001059518A5 (en
JP2001059518A (en
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英男 大内
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NSK Ltd
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NSK Ltd
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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
    • F16C43/00—Assembling bearings
    • F16C43/04—Assembling rolling-contact bearings
    • 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
    • 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)
  • Support Of The Bearing (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Description

【０００１】
【発明の属する技術分野】
この発明に係る車輪用転がり軸受ユニットは、ＦＦ車（前置エンジン前輪駆動車）又は４ＷＤ車（四輪駆動車）の前輪等の駆動輪を、懸架装置に対して回転自在に支持する為に利用する。
【０００２】
【従来の技術】
車輪を懸架装置に対して回転自在に支持する為に、外輪と内輪とを転動体を介して回転自在に組み合わせた車輪用転がり軸受ユニットが、各種使用されている。又、操舵輪であると同時に駆動輪でもあるＦＦ車或は４ＷＤ車の前輪を支持する為の車輪用転がり軸受ユニットは、等速ジョイントと組み合わせて、車輪に付与された舵角に拘らず、駆動軸の回転を上記車輪に対して円滑に（等速性を確保して）伝達する必要がある。この様な等速ジョイントと組み合わせて、しかも小型且つ軽量に構成できる車輪用転がり軸受ユニットとして従来から、特開平１１−３７１４６号公報に記載されたものが知られている。
【０００３】
図６は、この公報に記載された従来構造を示している。車両への組み付け状態で、懸架装置に支持した状態で回転しない外輪１は、外周面にこの懸架装置に支持する為の第一の取付フランジ２を、内周面に複列の外輪軌道３、３を、それぞれ有する。上記外輪１の内側には、第一、第二の内輪部材４、５を組み合わせて成るハブ６を配置している。このうち第一の内輪部材４は、外周面の一端寄り（図６の左寄り）部分に車輪を支持する為の第二の取付フランジ７を、同じく他端寄り（図６の右寄り）部分に第一の内輪軌道８を、それぞれ設けた筒状に形成している。又、上記第一の内輪部材４の中間部内周面に、雌スプライン溝９を形成した第一の小径部１０を、同じく他端部（図６の右端部）内周面に、この第一の小径部１０よりも大径の円筒面である第二の小径部１１を、互いに同心に設けている。
【０００４】
これに対して、第二の内輪部材５は、一端部（図６の左端部）を上記第一の内輪部材４をがたつきなく外嵌固定する為の嵌合支持部１２とし、中間部外周面に第二の内輪軌道１３を設け、他端部を等速ジョイント１４の外輪となるハウジング部１５としている。又、上記嵌合支持部１２の一端部には、この嵌合支持部１２よりも小径の雄ねじ部１６を設けている。又、この嵌合支持部１２の中間部外周面には、上記第一の小径部１０に形成した雌スプライン溝９と係合する雄スプライン溝１７を形成した第一の嵌合面部１８を、同じく他端部外周面には、上記第二の小径部１１と嵌合する円筒面とした第二の嵌合面部１９を、互いに同心に設けている。そして、上記嵌合支持部１２に、上記第一の内輪部材４を外嵌すると共に、上記第一の小径部１０の内周面に形成した雌スプライン溝９と上記第一の嵌合面部１８の外周面に形成した雄スプライン溝１７とをスプライン係合させている。この状態で、上記雄ねじ部１６にナット２０を螺合し、更に緊締して、上記第一、第二の内輪部材４、５同士を結合している。又、上記各外輪軌道３、３と上記第一、第二の内輪軌道８、１３との間にそれぞれ複数個ずつ転動体２１、２１を転動自在に設ける事により、上記外輪１の内側に上記ハブ６を、回転自在に支持している。
【０００５】
更に、上記外輪１の両端開口部と上記ハブ６の中間部外周面との間には、ステンレス鋼板等の金属製で略円筒状のカバー２２ａ、２２ｂと、ゴムの如きエラストマー等の弾性材製で円環状のシールリング２３ａ、２３ｂとを設けている。これらカバー２２ａ、２２ｂ及びシールリング２３ａ、２３ｂは、上記複数の転動体２１、２１を設置した部分と外部とを遮断し、この部分に存在するグリースが外部に漏出するのを防止すると共に、この部分に雨水、塵芥等の異物が侵入する事を防止する。又、上記第二の内輪部材５の中間部内側には、この第二の内輪部材５の内側を塞ぐ隔板部２４を設けて、この第二の内輪部材５の剛性を確保すると共に、この第二の内輪部材５の先端（図６の左端）開口からこの第二の内輪部材５の内側に入り込んだ異物が、前記ハウジング部１５の内側に設けた等速ジョイント１４部分にまで達する事を防止している。
【０００６】
又、上記等速ジョイント１４は、上記ハウジング部１５と、内輪２５と、保持器２６と、複数個の玉２７とから成る。このうちの内輪２５は、エンジンによりトランスミッション及びデファレンシャルギヤを介して回転駆動される、図示しない駆動軸の先端部に固定される。この内輪２５の外周面には、それぞれが断面円弧形である複数の内側係合溝２８を、円周方向に亙り等間隔に、それぞれ円周方向に対し直角方向に形成している。又、上記ハウジング部１５の内周面で上記内側係合溝２８と対向する位置には、やはり断面円弧形である複数の外側係合溝２９を、円周方向に対し直角方向に形成している。又、上記保持器２６は、断面円弧状で全体を円環状に形成しており、上記内輪２５の外周面とハウジング部１５の内周面との間に挟持している。この保持器２６の円周方向複数個所で、上記内側、外側両係合溝２８、２９に整合する位置には、それぞれポケット３０を形成し、これら各ポケット３０の内側にそれぞれ上記各玉２７を保持している。これら各玉２７は、それぞれ上記各ポケット３０に保持された状態で、上記内側、外側両係合溝２８、２９に沿い転動自在である。又、上記ハウジング部１５の外周面には、このハウジング部１５の端部開口を塞ぐ筒状のブーツ（図示せず）の一端部を係止する為の係止溝３１を、全周に亙り形成している。
【０００７】
上述の様に構成する車輪用転がり軸受ユニットを車両に組み付ける際には、第一の取付フランジ２により外輪１を懸架装置に支持し、第二の取付フランジ７により駆動輪でもある前輪を第一の内輪部材４に固定する。又、エンジンによりトランスミッションを介して回転駆動される、図示しない駆動軸の先端部を、等速ジョイントを構成する内輪２５の内側にスプライン係合させる。自動車の走行時には、上記内輪２５の回転を、複数の玉２７を介してハブ６に伝達し、上記前輪を回転駆動する。
【０００８】
【発明が解決しようとする課題】
図６に示した従来の車輪用転がり軸受ユニットの場合、第一の内輪部材４を第二の内輪部材５の嵌合支持部１２に外嵌固定してハブ６を構成している。この為、ハブ６内に、第一の小径部１０と第一の嵌合面部１８とのスプライン係合部と、第二の小径部１１と第二の嵌合面部１９との嵌合部とが存在する。ところで、車輪用転がり軸受ユニットの軸に相当するこのハブ６には、自動車への組み付け状態では、このハブ６を折り曲げようとする方向のモーメントが、第二の取り付けフランジ７等から加わる荷重により発生する。これに対して、上記両嵌合部で上記モ−メントに対する曲げ剛性を高くする事が、上記ハブ６の曲がりを抑え、車輪用転がり軸受ユニットを組み付けた自動車の走行安定性の向上に繋がる。特に、上記第二の小径部１１と第二の嵌合面部１９との嵌合を締め代を持った嵌め合いにすると共に、この第二の小径部１１と第二の嵌合面部１９との嵌合部の軸方向長さを長くする事が、上記曲げ剛性を向上させる面からは好ましい。
【０００９】
ところが、ただ単に上記第二の小径部１１と第二の嵌合面部１９との嵌合を締め代を持った嵌め合いにすると共に、この第二の小径部１１と第二の嵌合面部１９との嵌合部の軸方向長さを長くしただけでは、上記第一、第二の内輪部材４、５同士の組み合わせ時に問題が生じる。即ち、この様な場合には、これら両内輪部材４、５同士を組み合わせるべく、このうちの第一の内輪部材４に第二の内輪部材５の嵌合支持部１２を挿入すると、上記第一の小径部１０の内周面に形成した雌スプライン溝９と上記第一の嵌合面部１８の外周面に形成した雄スプライン溝１７とが係合し始めるのに先立って、上記第二の小径部１１と上記第二の嵌合面部１９とが、締め代を持って嵌合し始める。この様に上記第二の小径部１１と上記第二の嵌合面部１９とが先に嵌合し始めると、その後に、上記両スプライン溝９、１７同士をスプライン係合をさせる為に円周方向の位相を合わせるべく、上記第一の内輪部材４と第二の内輪部材５とを相対回転させる事が難しくなる。この様な不都合を防止する為には、上記第二の小径部１１と上記第二の嵌合面部１９とが嵌合し始めるのに先立って、上記両スプライン溝９、１７同士の円周方向に亙る位相を合致させてから、この位相を合わせたままの状態で、上記第二の内輪部材５を上記第一の内輪部材４に対し真っ直ぐ捻らずに挿入して、上記両スプライン溝９、１７同士を係合させる事が好ましい。
本発明の車輪用転がり軸受ユニットは、上述の様な事情に鑑みて、車輪用転がり軸受ユニットの曲げ剛性を高める事ができ、しかも組立作業が容易な構造を実現すべく発明したものである。
【００１０】
【課題を解決するための手段】
本発明の車輪用転がり軸受ユニットは、前述した従来の車輪用転がり軸受ユニットと同様に、外周面に懸架装置に支持する為の第一の取付フランジを、内周面に複列の外輪軌道を、それぞれ有する外輪と、外周面の一端寄り部分に車輪を支持する為の第二の取付フランジを、同じく他端寄り部分に第一の内輪軌道を、それぞれ設けた筒状の第一の内輪部材と、一端部をこの第一の内輪部材をがたつきなく外嵌固定する為の嵌合支持部とし、中間部外周面に第二の内輪軌道を設け、他端部を等速ジョイントの外輪となるハウジング部とした第二の内輪部材と、上記各外輪軌道と上記各内輪軌道との間にそれぞれ複数個ずつ転動自在に設けられた転動体とを備える。このうち、上記第一の内輪部材の中間部内周面に雌スプライン溝を形成した第一の小径部を、同じく他端部内周面にこの第一の小径部よりも大径の円筒面である第二の小径部を、互いに同心に設けている。又、上記嵌合支持部の外周面は、上記第一の小径部に形成した雌スプライン溝と係合する雄スプライン溝を形成した第一の嵌合面部と、上記第二の小径部と嵌合する円筒面とした第二の嵌合面部とを、互いに同心に設けている。
特に、本発明の車輪用転がり軸受ユニットに於いては、上記第二の小径部と上記第二の嵌合面部との嵌合を、締め代を持った嵌め合いとしている。そして、上記雄スプライン溝を形成した上記第一の嵌合面部の軸方向長さよりも、上記円筒面とした上記第二の嵌合面部並びに上記第二の小径部の軸方向長さを大きくする事により、上記第一、第二の内輪部材同士の組み合わせ時に、上記両スプライン溝同士がスプライン係合し始めるのに先立って上記第二の小径部と上記第二の嵌合面部とが嵌合し始める様にしている。更に、上記第二の小径部と上記第二の嵌合面部とが嵌合し始めるのに先立って上記両スプライン溝同士の円周方向に亙る位相を合わせる為の位置決め用の凹部又は凸部を、上記第二の内輪部材の外周面の一部で上記雄スプライン部からは外れた部分又は軸方向端面部分に設けている。
【００１１】
【作用】
上述の様に構成する本発明の車輪用転がり軸受ユニットの場合には、雄スプライン溝を形成した第一の嵌合面部の軸方向長さよりも、円筒面とした第二の嵌合面部並びに第二の小径部の軸方向長さを大きくする事により、第一、第二の内輪部材同士の組み合わせ時に、第一の小径部の内周面に形成した雌スプライン溝と上記第一の嵌合面部の外周面に形成した上記雄スプライン溝とが係合し始めるのに先立って、第二の小径部と第二の嵌合面部とが、締め代を持った嵌め合いで嵌合し始める。この為、この第二の小径部と第二の嵌合面部との嵌合部の軸方向長さを長くする事ができ、従来構造の場合よりも曲げ剛性を高くして、走行時に加わる大きなモーメント荷重に拘わらず、車輪用転がり軸受ユニット変形を抑え、自動車の走行安定性の向上等を図れる。更に、組立時には、上記第二の小径部と第二の嵌合面部とが嵌合し始めるのに先立って、上記第二の内輪部材に設けた位置決め用の凹部又は凸部により上記両スプライン溝の位相を合わせてから、この位相を合わせた状態のまま、上記第二の内輪部材を上記第一の内輪部材に対し真っ直ぐ捻らずに挿入して、上記両スプライン溝同士を係合させる。従って、上記第一、第二の内輪部材同士を組み合わせる作業が面倒にならず、曲げ剛性が高い構造であるにも拘らず、製造コストが嵩む事はない。
しかも、上記位置決め用の凹部又は凸部を、上記第二の内輪部材の外周面又は軸方向端面の一部に設けている為、例えば位置決め用の凹部を等速ジョイントの軌道面である外径側係合溝とし、この外径側係合溝に押し込み治具を係合させる場合に比べ、この軌道面に傷を付けて等速ジョイントの耐久性能を著しく低下させる事も防止できる。
【００１２】
【発明の実施の形態】
図１〜３は、本発明の実施の形態の第１例を示している。尚、本例の特徴は、組立作業を面倒にする事なく、車輪用転がり軸受ユニットの曲げ剛性を高めるべく、第一の内輪部材４ａと第二の内輪部材５ａとの構造を工夫した点にある。その他の部分の構造及び作用は、前述の図６に示した従来構造とほぼ同様であるから、同等部分には同一符号を付して重複する説明を省略若しくは簡略にし、以下、本発明の特徴部分並びに上記従来構造と異なる部分を中心に説明する。
【００１３】
本発明の車輪用転がり軸受ユニットのハブ６ａを構成する円筒状の第一の内輪部材４ａの中間部内周面に、雌スプライン溝９ａを形成した第一の小径部１０ａを、同じく他端部（図１、３の右端部）内周面に、この第一の小径部１０ａよりも大径の円筒面である第二の小径部１１ａを、互いに同心に設けている。一方、第一の内輪部材４ａと共にハブ６ａを構成する第二の内輪部材５ａの一端部（図１、３の左端部）は、上記第一の内輪部材４ａをがたつきなく外嵌固定する為の嵌合支持部１２ａとし、他端部を等速ジョイント１４の外輪となるハウジング部１５としている。上記嵌合支持部１２ａの中間部外周面には、上記第一の小径部１０ａに形成した雌スプライン溝９ａと係合する雄スプライン溝１７ａを形成した第一の嵌合面部１８ａを、他端部外周面には、上記第二の小径部１１ａと嵌合する円筒面とした第二の嵌合面部１９ａを、互いに同心に設けている。又、上記第二の小径部１１ａと第二の嵌合面部１９ａとの嵌合を、締め代を持った嵌め合い（締り嵌め）としている。更に、上記ハウジング部１５の軸方向他端面（図１、３の右端面）の円周方向の１個所位置には、請求項に記載した位置決め用の凹部又は凸部に相当し、後述する押し込み治具の一部と係合する、断面Ｖ字状の係合溝３２を形成している。
【００１４】
更に、本例の場合には、上記雌スプライン溝９ａと上記雄スプライン溝１７ａとの係合部の、軸方向に亙る長さＬ0 よりも、上記第二の小径部１１ａと上記第二の嵌合面部１９ａとの嵌合部の、軸方向に亙る長さＬ1 を大きく（Ｌ0 ＜Ｌ1 ）している。この様に、嵌合部の長さＬ1 を大きくする分、上記第一、第二の内輪部材４ａ、５ａにより構成するハブ６ａの曲げ剛性を大きくできる。但し、これら第一、第二の内輪部材４ａ、５ａ同士を組み合わせる際には、上記雌スプライン溝９ａと上記雄スプライン溝１７ａとが係合し始めるのに先立って、上記第二の小径部１１ａと上記第二の嵌合面部１９ａとが嵌合し始める。
【００１５】
上述の様に構成する第一、第二の内輪部材４ａ、５ａ同士を組み合わせて、上記ハブ６ａとする作業は、次の様にして行なう。先ず、上記第二の内輪部材５ａの嵌合支持部１２ａを上記第一の内輪部材４ａに押し込む為の図示しない押し込み治具の一部に設けた係合突部に、上記第二の内輪部材５ａの係合溝３２を係合させる。この状態で、上記第二の内輪部材５ａの雄スプライン溝１７ａと、上記第一の内輪部材４ａの雌スプライン溝９ａとの、円周方向に亙る位相が合致する様に、前もって上記押し込み治具の設定をしておく。尚、上記雌スプライン９ａの位置は、上記第一の内輪部材４ａの第二の取り付けフランジ７に形成した車輪を支持する為の図示しないスタッドを固定する取付孔３３等を基準にして決める。即ち、押し込み作業時に上記第一の内輪部材４ａを支える受具の一部に設けた位置決め突部を上記取付孔３３にがたつきなく嵌合させて、この受具に対する上記第一の内輪部材４ａの位置決めを図る。勿論、この受具と上記押し込み治具との位置は、互いに規制している。そして、上記両スプライン溝９ａ、１７ａ同士の円周方向の位相を合わせた状態で、上記押し込み治具により上記第二の内輪部材５ａの嵌合支持部１２ａを上記第一の内輪部材４ａに、真っ直ぐ捻らずに押し込む。この押し込み作業により、図３に示す様に、上記両スプライン溝９ａ、１７ａ同士が係合し始めるのに先立って、上記第二の小径部１１ａと上記第二の嵌合面部１９ａとが、締め代を持って（締り嵌めで）嵌合し始める。この状態から更に押し込み作業を続け、上記第二の内輪部材５ａを上記第一の内輪部材４ａ内に、真っ直ぐ捻らず圧入すると、上記両スプライン溝９ａ、１７ａ同士が係合し始める。この際、両スプライン溝９ａ、１７ａ同士の円周方向に亙る位相は合致したままの状態なので、そのまま押し込み作業を続ける事ができる。そして、上記第二の内輪部材５ａの一端部に設けた雄ねじ部１６を前記第一の小径部１０ａよりも突出させた後、図１に示す様に、この雄ねじ部１６にナット２０を螺合し、更に緊締する事により、上記第一、第二の内輪部材４ａ、５ａ同士を結合する。同時に、外輪１の内周面に設けた複列の外輪軌道３、３と上記第一、第二の内輪部材４ａ、５ａの外周面に設けた第一、第二の内輪軌道８、１３との間にそれぞれ複数個ずつ転動自在に設けた、各転動体２１、２１に、適切な予圧を付与する。尚、上記ナット２０は、上記第一の内輪部材４ａの一端部（図１、３の左端部）内周面に形成した、大径部３７の内径側に位置する。
【００１６】
上述の様に構成する本例の車輪用転がり軸受ユニットにより、車輪を懸架装置に対して回転自在に支持する作用は、前述した従来の車輪用転がり軸受ユニットの場合と同様である。特に、本例の場合には、上記第一、第二の内輪部材４ａ、５ａ同士の組み合わせ時に、上記両スプライン溝９ａ、１７ａ同士が係合し始めるのに先立って第二の小径部１１ａと第二の嵌合面部１９ａとが、締め代を持って嵌合し始める。従って、この第二の小径部１１ａと第二の嵌合面部１９ａとの嵌合部の軸方向長さを長くして、モ−メント荷重に対する曲げ剛性を高める事ができる。この結果、走行時に加わる大きなモーメント荷重に拘らず、ハブ６ａの変形を抑えて、車輪用転がり軸受ユニットを組み付けた自動車の走行安定性の向上等を図れる。更には、上記第二の小径部１１ａと第二の嵌合面部１９ａとが嵌合し始めるのに先立って、上記係合溝３２と上記押し込み治具とを係合させると共に、前記取付孔３３と受具とを係合させる事により上記両スプライン溝９ａ、１７ａ同士の位相を合致させる事ができる。従って、ハブ６ａの組立作業時には、これら両スプライン溝９ａ、１７ａの位相を合致させた状態のまま、第二の内輪部材５ａを真っ直ぐ捻らずに押し込むだけで、上記両スプライン溝９ａ、１７ａ同士を係合させる事ができる。従って、曲げ剛性が大きな構造にできるだけでなく、上記ハブ６ａの組立作業を容易にできて、曲げ剛性が高く優れた性能を有する車輪用転がり軸受ユニットを低コストで実現できる。尚、図示の例では上記係合溝３２を第二の内輪部材５ａの軸方向他端面に形成したが、第二の内輪部材５ａの軸方向一端面（図１、３の左端面）に形成しても良い。
【００１７】
尚、上述の説明では、押し込み治具と係合溝３２とを係合させて組立作業を行なうとしたが、押し込み治具には係合突起を設けずに、予め係合溝３２と係合する他の治具により、上記第二の内輪部材５ａの円周方向の位相を合わせておき、それから押し込み作業を行なう事も可能である。又、上記第二の内輪部材５ａのハウジング部１５の内周面に形成した、等速ジョイント１４を構成する為の外側係合溝２９を位置決め用の凹部とする事も、理論的には可能である。但し、押し込み治具を玉２７の軌道面となる上記外側係合溝２９と係合させると、軌道面に傷を付けて等速ジョイントの耐久性能を著しく低下させる恐れがあるので、上記外側係合溝２９を組立時の位置決め用の凹部とするのは好ましくない。従って、上記第二の内輪部材５ａの外周面又は軸方向端面の一部に、上記位置決め用の凹部又は凸部を設けた方が良い。又、上述の説明では、前記第一の内輪部材４ａの外周面の第二の取付フランジ７に形成した取付孔３３と受具とを係合させて、上記第一の内輪部材４ａの回転方向に関する位相合わせを行なうとした。一方、上記第二の取付フランジ７には、軽量化の為の孔が円周上に複数個、等ピッチで形成されている事がある。この様な孔が存在する場合には、この孔と上記受具とを係合させる事もでき、この場合には、上記取付孔３３の内周面を傷付ける恐れがなくなる。
【００１８】
次に、図４〜５は、本発明の実施の形態の第２例を示している。本例の車輪用転がり軸受ユニットのハブ６ｂを構成する第二の内輪部材５ｂの一端部（図４の左端部）は、上記第一の内輪部材４ｂをがたつきなく外嵌固定する為の嵌合支持部１２ｂとし、他端部を等速ジョイント１４の外輪となるハウジング部１５としている。上記嵌合支持部１２ｂの外周面は、一端寄り部分（図４の左寄り部分）に、その先端（図４の左端）まで雄スプライン溝１７ｂを形成した第一の嵌合面部１８ｂを、他端部（図４の右端部）に、円筒面とした第二の嵌合面部１９ｂを、互いに同心に設けている。又、上記ハウジング部１５の他端部外周面の円周方向の１個所位置には、請求項に記載した位置決め用の凹部又は凸部に相当し、後述する押し込み治具に設けた係合突部と係合する、断面Ｖ字状の凹溝３４を形成している。
【００１９】
上述の様に構成する第一、第二の内輪部材４ｂ、５ｂ同士を組み合わせる作業は、次の様にして行なう。先ず、上記第二の内輪部材５ｂの嵌合支持部１２ｂを上記第一の内輪部材４ｂに押し込む為の図示しない押し込み治具に設けた係合突部と、上記第二の内輪部材５ｂの凹溝３４とを係合させる。この状態で、上記第二の内輪部材５ｂの雄スプライン溝１７ｂが、上記第一の内輪部材４ｂの雌スプライン溝９ｂと円周方向に亙る位相が合致する様に、前もって上記押し込み治具及び次述する受具の設定をしておく。尚、上記雌スプライン９ｂの円周方向に亙る位相は、上記第一の内輪部材４ｂの第二の取り付けフランジ７に形成した、車輪を支持する為の図示しないスタッドを固定する取付孔３３に、押し込み作業の際、上記第一の内輪部材４ｂを支える受具に設けた突部をがたつきなく嵌合させる事により、規制する。そして、上記両スプライン溝９ｂ、１７ｂ同士の円周方向に亙る位相を合致させた状態で、上記押し込み治具により上記第二の内輪部材５ｂの嵌合支持部１２ｂを上記第一の内輪部材４ｂに、真っ直ぐ捻らずに押し込む。この押し込み作業により、上記両スプライン溝９ｂ、１７ｂ同士が係合し始めるのに先立って、上記第二の小径部１１ｂと上記第二の嵌合面部１９ｂとが、締め代を持って嵌合し始める。尚、この押し込み作業の際には、上記第一の嵌合面部１８ｂは、先端までストレート形状である。更に押し込み作業を続け、上記第二の内輪部材５ｂを上記第一の内輪部材４ｂ内に、真っ直ぐ捻らずに押し込むと、上記両スプライン溝９ｂ、１７ｂ同士が係合し始める。この際、両スプライン溝９ｂ、１７ｂ同士の円周方向に亙る位相は合致した状態のままなので、そのまま押し込み作業を続ける事ができる。そして、この第一の内輪部材４ｂの軸方向他端面（図４の右端面）を、上記第二の内輪部材５ｂの中間部外周面に設けた段部３５に突き当てた状態で、上記第一の嵌合面部１８ｂの先端部を直径方向外方に塑性変形させてかしめ部３６を形成する。この状態で上記第一の内輪部材４ｂは、上記段部３５と上記かしめ部３６とにより、軸方向両側から狭持されて、上記第二の内輪部材５ｂに対し固定される。尚、上記第一の内輪部材４ｂをこの段部３５に突き当てた状態で各転動体２１、２１に適正な予圧が付与される様に、上記段部３５等の位置を規制している。
【００２０】
上述の様に構成する本例の車輪用転がり軸受ユニットの場合には、前述した第１例に比べて、ナット２０（図１参照）を使わない分、部品点数の削減による重量並びにコストの低減を図る事ができる。尚、本例を実施するに当たり、必ずしもかしめ部３６となる嵌合支持部１２ｂの先端まで上記雄スプライン溝１７ｂを形成する必要はないが、図示の例の様に、この嵌合支持部１２ｂの先端までスプライン加工をする方が、スプライン加工を途中までとする場合よりもコストがかからない。その他の構造及び作用は、前述した第１例の場合と同様である。
【００２１】
【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、製作費の上昇を抑えつつ、車輪用転がり軸受ユニットの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】図１のＡ矢視図。
【図３】組立工程を示す部分断面図。
【図４】本発明の実施の形態の第２例を示す部分断面図。
【図５】図４のＢ矢視図。
【図６】従来構造の１例を示す部分断面図。
【符号の説明】
１ 外輪
２ 取付フランジ
３ 外輪軌道
４、４ａ、４ｂ 第一の内輪部材
５、５ａ、５ｂ 第二の内輪部材
６、６ａ、６ｂ ハブ
７ 第二の取付フランジ
８ 第一の内輪軌道
９、９ａ、９ｂ 雌スプライン溝
１０、１０ａ、１０ｂ 第一の小径部
１１、１１ａ、１１ｂ 第二の小径部
１２、１２ａ、１２ｂ 嵌合支持部
１３ 第二の内輪軌道
１４ 等速ジョイント
１５ ハウジング部
１６ 雄ねじ部
１７、１７ａ、１７ｂ 雄スプライン溝
１８、１８ａ、１８ｂ 第一の嵌合面部
１９、１９ａ、１９ｂ 第二の嵌合面部
２０ ナット
２１ 転動体
２２ａ、２２ｂ カバー
２３ａ、２３ｂ シールリング
２４ 隔板部
２５ 内輪
２６ 保持器
２７ 玉
２８ 内側係合溝
２９ 外側係合溝
３０ ポケット
３１ 係止溝
３２ 係合溝
３３ 取付孔
３４ 凹溝
３５ 段部
３６ かしめ部
３７ 大径部[0001]
BACKGROUND OF THE INVENTION
The wheel rolling bearing unit according to the present invention is configured to rotatably support a drive wheel such as a front wheel of an FF vehicle (front engine front wheel drive vehicle) or a 4WD vehicle (four wheel drive vehicle) with respect to a suspension device. Use.
[0002]
[Prior art]
In order to rotatably support a wheel with respect to a suspension device, various types of wheel rolling bearing units are used in which an outer ring and an inner ring are rotatably combined via rolling elements. In addition, the wheel rolling bearing unit for supporting the front wheel of the FF vehicle or 4WD vehicle which is the steering wheel as well as the driving wheel is combined with the constant velocity joint, regardless of the steering angle given to the wheel. It is necessary to transmit the rotation of the drive shaft to the wheel smoothly (with a constant speed). 2. Description of the Related Art Conventionally, a rolling bearing unit for a wheel that can be configured in a small size and light weight in combination with such a constant velocity joint is disclosed in Japanese Patent Application Laid-Open No. 11-37146.
[0003]
FIG. 6 shows a conventional structure described in this publication. The outer ring 1 that does not rotate in a state of being mounted on a vehicle while being supported by a suspension device has a first mounting flange 2 for supporting the suspension device on the outer peripheral surface, and a double row outer ring track 3 on the inner peripheral surface. 3 respectively. A hub 6 formed by combining the first and second inner ring members 4 and 5 is disposed inside the outer ring 1. Of these, the first inner ring member 4 is provided with a second mounting flange 7 for supporting the wheel on one end (to the left in FIG. 6) of the outer peripheral surface, and on the other end (to the right in FIG. 6). One inner ring raceway 8 is formed in a cylindrical shape provided. Further, a first small diameter portion 10 having a female spline groove 9 formed on the inner peripheral surface of the intermediate portion of the first inner ring member 4 is formed on the inner peripheral surface of the other end portion (the right end portion in FIG. 6). The second small-diameter portions 11, which are cylindrical surfaces having a larger diameter than the small-diameter portion 10, are provided concentrically with each other.
[0004]
On the other hand, the second inner ring member 5 has one end portion (left end portion in FIG. 6) as a fitting support portion 12 for externally fixing and fixing the first inner ring member 4 without rattling. A second inner ring raceway 13 is provided on the outer peripheral surface, and the other end part is a housing part 15 that becomes an outer ring of the constant velocity joint 14. Further, a male screw portion 16 having a smaller diameter than the fitting support portion 12 is provided at one end portion of the fitting support portion 12. Further, on the outer peripheral surface of the intermediate portion of the fitting support portion 12, a first fitting surface portion 18 in which a male spline groove 17 that engages with the female spline groove 9 formed in the first small diameter portion 10 is formed. Similarly, on the outer peripheral surface of the other end portion, a second fitting surface portion 19 that is a cylindrical surface that fits the second small diameter portion 11 is provided concentrically with each other. Then, the first inner ring member 4 is fitted on the fitting support portion 12, and the female spline groove 9 formed on the inner peripheral surface of the first small diameter portion 10 and the first fitting surface portion 18. A male spline groove 17 formed on the outer peripheral surface of the outer peripheral surface is spline engaged. In this state, the nut 20 is screwed into the male screw portion 16 and further tightened to join the first and second inner ring members 4 and 5 together. Also, a plurality of rolling elements 21 and 21 are provided between the outer ring raceways 3 and 3 and the first and second inner ring raceways 8 and 13, respectively, so that they can roll inside. The hub 6 is rotatably supported.
[0005]
Further, between the opening portions at both ends of the outer ring 1 and the outer peripheral surface of the intermediate portion of the hub 6, a substantially cylindrical cover 22a, 22b made of a metal such as a stainless steel plate, and an elastic material such as an elastomer such as rubber. Are provided with annular seal rings 23a and 23b. The covers 22a and 22b and the seal rings 23a and 23b block the portion where the plurality of rolling elements 21 and 21 are installed from the outside, and prevent the grease existing in the portion from leaking outside. Prevents foreign matter such as rainwater and dust from entering the area. Further, a partition plate portion 24 for closing the inner side of the second inner ring member 5 is provided inside the intermediate portion of the second inner ring member 5 to ensure the rigidity of the second inner ring member 5. The foreign matter that has entered the inside of the second inner ring member 5 from the opening (left end in FIG. 6) of the second inner ring member 5 reaches the constant velocity joint 14 provided inside the housing portion 15. It is preventing.
[0006]
The constant velocity joint 14 includes the housing portion 15, an inner ring 25, a cage 26, and a plurality of balls 27. Of these, the inner ring 25 is fixed to the tip of a drive shaft (not shown) that is rotationally driven by the engine via a transmission and a differential gear. On the outer peripheral surface of the inner ring 25, a plurality of inner engagement grooves 28 each having an arcuate cross section are formed at equal intervals in the circumferential direction and perpendicular to the circumferential direction. Further, a plurality of outer engagement grooves 29 having an arcuate cross section are formed in a direction perpendicular to the circumferential direction at a position facing the inner engagement groove 28 on the inner peripheral surface of the housing portion 15. ing. The cage 26 has an arc shape in cross section and is formed in an annular shape as a whole, and is held between the outer peripheral surface of the inner ring 25 and the inner peripheral surface of the housing portion 15. A plurality of pockets 30 are formed at positions corresponding to the inner and outer engaging grooves 28 and 29 at a plurality of locations in the circumferential direction of the cage 26, and the balls 27 are respectively placed inside the pockets 30. keeping. These balls 27 can roll along the inner and outer engaging grooves 28 and 29 while being held in the respective pockets 30. Further, a locking groove 31 for locking one end portion of a cylindrical boot (not shown) that closes the end opening of the housing portion 15 is provided on the entire outer circumference of the housing portion 15. Forming.
[0007]
When the rolling bearing unit for a wheel configured as described above is assembled to a vehicle, the outer ring 1 is supported on the suspension device by the first mounting flange 2 and the front wheel which is also the driving wheel is first supported by the second mounting flange 7. The inner ring member 4 is fixed. Further, the tip of a drive shaft (not shown) that is rotationally driven by the engine via the transmission is spline-engaged with the inner side of the inner ring 25 constituting the constant velocity joint. When the automobile travels, the rotation of the inner ring 25 is transmitted to the hub 6 via a plurality of balls 27, and the front wheel is rotationally driven.
[0008]
[Problems to be solved by the invention]
In the case of the conventional rolling bearing unit for wheels shown in FIG. 6, the first inner ring member 4 is externally fitted and fixed to the fitting support portion 12 of the second inner ring member 5 to constitute the hub 6. For this reason, in the hub 6, a spline engagement portion between the first small diameter portion 10 and the first fitting surface portion 18, and a fitting portion between the second small diameter portion 11 and the second fitting surface portion 19. Exists. By the way, in the hub 6 corresponding to the shaft of the rolling bearing unit for the wheel, a moment in a direction in which the hub 6 is bent is generated by a load applied from the second mounting flange 7 or the like when assembled to the automobile. To do. On the other hand, increasing the bending rigidity with respect to the moment at both the fitting portions suppresses the bending of the hub 6 and leads to an improvement in the running stability of the automobile assembled with the wheel rolling bearing unit. In particular, the fitting between the second small diameter portion 11 and the second fitting surface portion 19 is a fitting with a tightening margin, and the second small diameter portion 11 and the second fitting surface portion 19 In order to improve the bending rigidity, it is preferable to lengthen the axial length of the fitting portion.
[0009]
However, the fitting of the second small diameter portion 11 and the second fitting surface portion 19 is simply made with a tight fit, and the second small diameter portion 11 and the second fitting surface portion 19 are also fitted. If only the axial length of the fitting portion is increased, a problem occurs when the first and second inner ring members 4 and 5 are combined. In other words, in such a case, when the fitting support portion 12 of the second inner ring member 5 is inserted into the first inner ring member 4 in order to combine both the inner ring members 4 and 5, the first Prior to the engagement of the female spline groove 9 formed on the inner peripheral surface of the small-diameter portion 10 and the male spline groove 17 formed on the outer peripheral surface of the first fitting surface portion 18, the second small-diameter portion 10 The part 11 and the second fitting surface part 19 start to be fitted with a tightening margin. As described above, when the second small diameter portion 11 and the second fitting surface portion 19 start to be fitted first, the spline grooves 9 and 17 are then circumferentially connected to each other for spline engagement. It becomes difficult to relatively rotate the first inner ring member 4 and the second inner ring member 5 in order to match the phase of the direction. In order to prevent such inconvenience, the circumferential direction between the spline grooves 9 and 17 is set before the second small diameter portion 11 and the second fitting surface portion 19 start to be fitted. The second inner ring member 5 is inserted into the first inner ring member 4 without being twisted in a state in which the phases are matched, and both the spline grooves 9, It is preferable to engage 17 with each other.
The wheel rolling bearing unit of the present invention has been invented to realize a structure that can increase the bending rigidity of the wheel rolling bearing unit and can be easily assembled in view of the above-described circumstances.
[0010]
[Means for Solving the Problems]
  The wheel rolling bearing unit of the present invention has a first mounting flange for supporting the suspension device on the outer circumferential surface and a double row outer ring raceway on the inner circumferential surface, as in the conventional wheel rolling bearing unit described above. A cylindrical first inner ring member provided with a respective outer ring, a second mounting flange for supporting the wheel on one end portion of the outer peripheral surface, and a first inner ring raceway on the other end portion. And one end portion as a fitting support portion for externally fixing the first inner ring member without rattling, a second inner ring raceway is provided on the outer peripheral surface of the intermediate portion, and the other end portion is an outer ring of the constant velocity joint. A second inner ring member serving as a housing portion, and a plurality of rolling elements provided in a freely rotatable manner between each outer ring raceway and each inner ring raceway. Among these, the first small-diameter portion in which the female spline groove is formed on the inner peripheral surface of the first inner ring member is a cylindrical surface having a diameter larger than that of the first small-diameter portion on the inner peripheral surface of the other end portion. The second small diameter portions are provided concentrically with each other. Further, the outer peripheral surface of the fitting support portion is fitted with a first fitting surface portion having a male spline groove that engages with the female spline groove formed in the first small diameter portion, and the second small diameter portion. A second fitting surface portion that is a cylindrical surface to be joined is provided concentrically with each other.
  In particular, in the wheel rolling bearing unit of the present invention, the fitting between the second small diameter portion and the second fitting surface portion is a fitting with a tightening margin. AndBy increasing the axial length of the second fitting surface portion and the second small diameter portion as the cylindrical surface, rather than the axial length of the first fitting surface portion in which the male spline groove is formed. ,When the first and second inner ring members are combined with each other, the second small diameter portion and the second fitting surface portion start to be engaged before the spline grooves start to engage with each other. I have to. Further, prior to the second small diameter portion and the second fitting surface portion starting to be fitted, a positioning concave portion or convex portion for aligning the phases of the spline grooves in the circumferential direction is provided. , A part of the outer peripheral surface of the second inner ring member that is separated from the male spline partOr axial end face partProvided.
[0011]
[Action]
  In the case of the rolling bearing unit for wheels of the present invention configured as described above,By increasing the axial length of the second fitting surface portion as a cylindrical surface and the second small diameter portion, rather than the axial length of the first fitting surface portion forming the male spline groove,A female spline groove formed on the inner peripheral surface of the first small diameter portion when the first and second inner ring members are combined;the aboveFormed on the outer peripheral surface of the first mating surfacethe abovePrior to the engagement with the male spline groove, the second small diameter portion and the second fitting surface portion begin to be fitted with a tight fit.. For this reasonIncreasing the axial length of the fitting portion between the second small diameter portion and the second fitting surface portionCanBending rigidity is made higher than in the case of the conventional structure, and deformation of the rolling bearing unit for the wheel can be suppressed regardless of a large moment load applied during traveling, and the traveling stability of the automobile can be improved. Further, at the time of assembly, both the spline grooves are formed by the positioning recesses or projections provided in the second inner ring member before the second small diameter portion and the second fitting surface portion start to be fitted. After the phase is adjusted, the second inner ring member is inserted into the first inner ring member without being twisted in a state where the phases are adjusted, and the two spline grooves are engaged with each other. Therefore, the operation of combining the first and second inner ring members is not troublesome, and the manufacturing cost does not increase despite the high bending rigidity.
  Moreover, since the positioning concave portion or convex portion is provided on a part of the outer peripheral surface or the axial end surface of the second inner ring member, for example, the positioning concave portion is an outer diameter that is the raceway surface of the constant velocity joint. It is possible to prevent the endurance performance of the constant velocity joint from being significantly deteriorated by scratching the raceway surface as compared with the case where the side engaging groove is used and the pushing jig is engaged with the outer diameter side engaging groove.
[0012]
DETAILED DESCRIPTION OF THE INVENTION
1 to 3 show a first example of an embodiment of the present invention. The feature of this example is that the structure of the first inner ring member 4a and the second inner ring member 5a is devised in order to increase the bending rigidity of the rolling bearing unit for the wheel without making the assembly work cumbersome. is there. Since the structure and operation of the other parts are almost the same as those of the conventional structure shown in FIG. 6 described above, the same parts are denoted by the same reference numerals and redundant description is omitted or simplified. The description will focus on the part and the part different from the conventional structure.
[0013]
  The first small-diameter portion 10a having a female spline groove 9a formed on the inner peripheral surface of the intermediate portion of the cylindrical first inner ring member 4a constituting the hub 6a of the wheel rolling bearing unit of the present invention is also connected to the other end ( The second small-diameter portion 11a, which is a cylindrical surface having a diameter larger than that of the first small-diameter portion 10a, is provided concentrically on the inner peripheral surface of the right end portion in FIGS. On the other hand, one end portion (the left end portion in FIGS. 1 and 3) of the second inner ring member 5a constituting the hub 6a together with the first inner ring member 4a externally fixes the first inner ring member 4a without rattling. Therefore, the other end portion is a housing portion 15 serving as an outer ring of the constant velocity joint 14. On the outer peripheral surface of the intermediate portion of the fitting support portion 12a, a first fitting surface portion 18a in which a male spline groove 17a that engages with the female spline groove 9a formed in the first small diameter portion 10a is formed at the other end. A second fitting surface portion 19a, which is a cylindrical surface that fits with the second small diameter portion 11a, is provided concentrically on the outer peripheral surface of the portion. Further, the fitting between the second small diameter portion 11a and the second fitting surface portion 19a is a fitting (tightening fitting) with a tightening margin. Further, the housing portion 15Axial directionOne position in the circumferential direction of the other end surface (the right end surface in FIGS. 1 and 3) corresponds to the positioning concave portion or convex portion described in the claims, and engages with a part of the pushing jig described later. The engaging groove 32 having a V-shaped cross section is formed.
[0014]
Further, in the case of this example, the length L in the axial direction of the engaging portion between the female spline groove 9a and the male spline groove 17a.0 Rather than the length L in the axial direction of the fitting portion between the second small diameter portion 11a and the second fitting surface portion 19a.1 (L0 <L1 )is doing. In this way, the length L of the fitting part1 Therefore, the bending rigidity of the hub 6a constituted by the first and second inner ring members 4a and 5a can be increased. However, when the first and second inner ring members 4a and 5a are combined, the second small-diameter portion 11a before the female spline groove 9a and the male spline groove 17a start to engage with each other. And the second fitting surface portion 19a start to be fitted.
[0015]
The operation of forming the hub 6a by combining the first and second inner ring members 4a and 5a configured as described above is performed as follows. First, the second inner ring member is formed on an engaging projection provided on a part of a pushing jig (not shown) for pushing the fitting support part 12a of the second inner ring member 5a into the first inner ring member 4a. The engaging groove 32 of 5a is engaged. In this state, the pushing jig is used in advance so that the phases in the circumferential direction of the male spline groove 17a of the second inner ring member 5a and the female spline groove 9a of the first inner ring member 4a coincide with each other. Set up. The position of the female spline 9a is determined with reference to a mounting hole 33 for fixing a stud (not shown) for supporting a wheel formed on the second mounting flange 7 of the first inner ring member 4a. That is, the positioning protrusion provided in a part of the holder that supports the first inner ring member 4a during the pushing operation is fitted into the mounting hole 33 without rattling, and the first inner ring member with respect to the holder is fitted. Position 4a. Of course, the positions of the receiver and the pushing jig are regulated with respect to each other. Then, with the circumferential phases of the spline grooves 9a, 17a being matched, the fitting support portion 12a of the second inner ring member 5a is moved to the first inner ring member 4a by the pushing jig. Push it straight without twisting. As shown in FIG. 3, the push-in operation causes the second small diameter portion 11a and the second fitting surface portion 19a to be tightened before the spline grooves 9a and 17a start to engage with each other. Start mating (with an interference fit). When the second inner ring member 5a is pressed into the first inner ring member 4a without being twisted straight, the spline grooves 9a and 17a start to engage with each other. At this time, since the phases extending in the circumferential direction between the spline grooves 9a and 17a remain matched, the pushing operation can be continued as it is. And after making the external thread part 16 provided in the one end part of the said 2nd inner ring member 5a protrude from said 1st small diameter part 10a, as shown in FIG. 1, the nut 20 is screwed together in this external thread part 16 Then, the first and second inner ring members 4a and 5a are joined together by further tightening. At the same time, double-row outer ring raceways 3 and 3 provided on the inner peripheral surface of the outer ring 1 and first and second inner ring raceways 8 and 13 provided on the outer peripheral surfaces of the first and second inner ring members 4a and 5a, Appropriate preload is applied to each of the rolling elements 21, 21 provided in a freely rotatable manner between each of the rolling elements. The nut 20 is positioned on the inner diameter side of the large-diameter portion 37 formed on the inner peripheral surface of one end portion (the left end portion in FIGS. 1 and 3) of the first inner ring member 4a.
[0016]
  The operation of rotatably supporting the wheel with respect to the suspension device by the wheel rolling bearing unit of the present example configured as described above is the same as that of the conventional wheel rolling bearing unit described above. In particular, in the case of this example, when the first and second inner ring members 4a and 5a are combined, the second small diameter portion 11a and the spline grooves 9a and 17a start to engage with each other. The second fitting surface portion 19a starts to be fitted with a tightening margin. Therefore, the axial length of the fitting portion between the second small diameter portion 11a and the second fitting surface portion 19a can be increased to increase the bending rigidity with respect to the moment load. As a result, it is possible to suppress the deformation of the hub 6a regardless of a large moment load applied during traveling, and to improve the traveling stability of the automobile in which the wheel rolling bearing unit is assembled. Furthermore, before the second small diameter portion 11a and the second fitting surface portion 19a start to be engaged, the engaging groove 32 and the pushing jig are engaged, and the mounting hole 33 is engaged. The phases of the two spline grooves 9a and 17a can be matched by engaging the receiving tool with the support. Accordingly, when the hub 6a is assembled, both the spline grooves 9a and 17a can be inserted into each other by simply pushing the second inner ring member 5a straight without twisting while keeping the phases of the spline grooves 9a and 17a in phase. Can be engaged. Therefore, not only can the structure have a large bending rigidity, but the assembly operation of the hub 6a can be facilitated, and a rolling bearing unit for a wheel having a high bending rigidity and excellent performance can be realized at low cost. In the illustrated example, the engagement groove 32 is formed on the second inner ring member 5a.Axial directionAlthough formed on the other end surface, the second inner ring member 5aAxial directionYou may form in one end surface (left end surface of FIG. 1, 3).
[0017]
  In the above description, the pushing jig and the engaging groove 32 are engaged to perform the assembling work. However, the pushing jig is not provided with the engaging protrusion, and is engaged with the engaging groove 32 in advance. It is also possible to adjust the circumferential phase of the second inner ring member 5a with another jig, and then perform the pushing operation. Further, it is theoretically possible to use the outer engaging groove 29 formed on the inner peripheral surface of the housing portion 15 of the second inner ring member 5a as a recess for positioning to constitute the constant velocity joint 14. It is. However, if the pushing jig is engaged with the outer engagement groove 29 that becomes the raceway surface of the ball 27, the raceway surface may be damaged and the durability performance of the constant velocity joint may be significantly reduced. It is not preferable that the groove 29 is a recess for positioning during assembly. Therefore, the outer peripheral surface of the second inner ring member 5aOr axial end faceIt is better to provide the positioning concave portion or convex portion in a part of the portion. In the above description, the mounting hole 33 formed in the second mounting flange 7 on the outer peripheral surface of the first inner ring member 4a is engaged with the receiver, so that the rotational direction of the first inner ring member 4a is engaged. Phasing was performed. On the other hand, in the second mounting flange 7, a plurality of holes for weight reduction may be formed on the circumference at an equal pitch. If such a hole exists, the hole can be engaged with the receiver, and in this case, there is no possibility of damaging the inner peripheral surface of the mounting hole 33.
[0018]
  4 to 5 show a second example of the embodiment of the present invention. Of this exampleRolling bearing unit for wheelsOne end portion (left end portion in FIG. 4) of the second inner ring member 5b constituting the hub 6b is a fitting support portion 12b for externally fixing the first inner ring member 4b without rattling. The end portion is a housing portion 15 that becomes an outer ring of the constant velocity joint 14. The outer peripheral surface of the fitting support portion 12b has a first fitting surface portion 18b in which a male spline groove 17b is formed at a portion closer to one end (leftward portion in FIG. 4) to the tip (left end in FIG. 4), and the other end. A second fitting surface portion 19b having a cylindrical surface is provided concentrically with the portion (the right end portion in FIG. 4). Further, at one position in the circumferential direction of the outer peripheral surface of the other end portion of the housing portion 15, it corresponds to a concave portion or a convex portion for positioning described in the claims, and an engagement protrusion provided on a pushing jig described later. A concave groove 34 having a V-shaped cross section is formed to be engaged with the portion.
[0019]
The operation of combining the first and second inner ring members 4b and 5b configured as described above is performed as follows. First, an engagement protrusion provided on a pushing jig (not shown) for pushing the fitting support portion 12b of the second inner ring member 5b into the first inner ring member 4b, and a recess of the second inner ring member 5b. The groove 34 is engaged. In this state, the push-in jig and the next are connected in advance so that the male spline groove 17b of the second inner ring member 5b is in phase with the female spline groove 9b of the first inner ring member 4b in the circumferential direction. Set the receiving equipment to be described. The phase of the female spline 9b in the circumferential direction is formed in a mounting hole 33 for fixing a stud (not shown) for supporting a wheel, formed in the second mounting flange 7 of the first inner ring member 4b. In the pushing operation, the protrusion is provided by fitting the protrusion provided on the supporter supporting the first inner ring member 4b without rattling. The fitting support portion 12b of the second inner ring member 5b is attached to the first inner ring member 4b by the pushing jig in a state where the phases of the spline grooves 9b and 17b in the circumferential direction are matched. And push it straight without twisting. By this pushing operation, the second small-diameter portion 11b and the second fitting surface portion 19b are fitted with a tight margin before the spline grooves 9b and 17b start to engage with each other. start. In the pushing operation, the first fitting surface portion 18b has a straight shape up to the tip. When the pushing operation is continued and the second inner ring member 5b is pushed into the first inner ring member 4b without being twisted, the spline grooves 9b and 17b start to engage with each other. At this time, since the phases of the spline grooves 9b and 17b extending in the circumferential direction remain matched, the pushing operation can be continued as it is. Then, in the state where the other axial end surface (the right end surface in FIG. 4) of the first inner ring member 4b is abutted against the step 35 provided on the outer peripheral surface of the intermediate portion of the second inner ring member 5b, The crimping portion 36 is formed by plastically deforming the tip end portion of the one fitting surface portion 18b outward in the diameter direction. In this state, the first inner ring member 4b is clamped from both sides in the axial direction by the step portion 35 and the caulking portion 36, and is fixed to the second inner ring member 5b. Note that the position of the stepped portion 35 and the like is regulated so that an appropriate preload is applied to the rolling elements 21 and 21 in a state where the first inner ring member 4b is abutted against the stepped portion 35.
[0020]
In the case of the rolling bearing unit for a wheel of this example configured as described above, the weight and cost are reduced by reducing the number of parts because the nut 20 (see FIG. 1) is not used, compared to the first example described above. Can be planned. In carrying out this example, it is not always necessary to form the male spline groove 17b up to the tip of the fitting support portion 12b to be the caulking portion 36. However, as shown in the illustrated example, the fitting support portion 12b Spline processing to the tip is less expensive than spline processing halfway. Other structures and operations are the same as those of the first example described above.
[0021]
【The invention's effect】
Since the present invention is configured and operates as described above, it is possible to improve the performance of the wheel rolling bearing unit while suppressing an increase in manufacturing cost.
[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 is a view taken in the direction of arrow A in FIG.
FIG. 3 is a partial cross-sectional view showing an assembly process.
FIG. 4 is a partial sectional view showing a second example of the embodiment of the present invention.
FIG. 5 is a view taken in the direction of arrow B in FIG.
FIG. 6 is a partial cross-sectional view showing an example of a conventional structure.
[Explanation of symbols]
1 outer ring
2 Mounting flange
3 Outer ring raceway
4, 4a, 4b First inner ring member
5, 5a, 5b Second inner ring member
6, 6a, 6b hub
7 Second mounting flange
8 First inner ring raceway
9, 9a, 9b Female spline groove
10, 10a, 10b First small diameter portion
11, 11a, 11b Second small diameter portion
12, 12a, 12b Fitting support part
13 Second inner ring raceway
14 Constant velocity joint
15 Housing part
16 Male thread
17, 17a, 17b Male spline groove
18, 18a, 18b first fitting surface portion
19, 19a, 19b Second fitting surface portion
20 nuts
21 Rolling elements
22a, 22b cover
23a, 23b Seal ring
24 Separator
25 inner ring
26 Cage
27 balls
28 Inner engagement groove
29 Outer engagement groove
30 pockets
31 Locking groove
32 engaging groove
33 Mounting hole
34 Groove
35 steps
36 Caulking part
37 Large diameter part

Claims (1)

外周面に懸架装置に支持する為の第一の取付フランジを、内周面に複列の外輪軌道を、それぞれ有する外輪と、外周面の一端寄り部分に車輪を支持する為の第二の取付フランジを、同じく他端寄り部分に第一の内輪軌道を、それぞれ設けた筒状の第一の内輪部材と、一端部をこの第一の内輪部材をがたつきなく外嵌固定する為の嵌合支持部とし、中間部外周面に第二の内輪軌道を設け、他端部を等速ジョイントの外輪となるハウジング部とした第二の内輪部材と、上記各外輪軌道と上記各内輪軌道との間にそれぞれ複数個ずつ転動自在に設けられた転動体とを備え、上記第一の内輪部材の中間部内周面に雌スプライン溝を形成した第一の小径部を、同じく他端部内周面にこの第一の小径部よりも大径の円筒面である第二の小径部を、互いに同心に設け、上記嵌合支持部の外周面は、上記第一の小径部に形成した雌スプライン溝と係合する雄スプライン溝を形成した第一の嵌合面部と、上記第二の小径部と嵌合する円筒面とした第二の嵌合面部とを、互いに同心に設けたものである車輪用転がり軸受ユニットに於いて、上記第二の小径部と上記第二の嵌合面部との嵌合を締め代を持った嵌め合いとし、上記雄スプライン溝を形成した上記第一の嵌合面部の軸方向長さよりも、上記円筒面とした上記第二の嵌合面部並びに上記第二の小径部の軸方向長さを大きくする事により、上記第一、第二の内輪部材同士の組み合わせ時に、上記両スプライン溝同士が係合し始めるのに先立って上記第二の小径部と上記第二の嵌合面部とが嵌合し始める様にすると共に、上記第二の小径部と上記第二の嵌合面部とが嵌合し始めるのに先立って上記両スプライン溝同士の円周方向に亙る位相を合わせる為の位置決め用の凹部又は凸部を、上記第二の内輪部材の外周面の一部で上記雄スプライン溝からは外れた部分又は軸方向端面部分に設けた事を特徴とする車輪支持用転がり軸受ユニット。A first mounting flange for supporting the suspension device on the outer peripheral surface, an outer ring having a double row outer ring raceway on the inner peripheral surface, and a second mounting for supporting the wheel on one end of the outer peripheral surface A cylindrical inner ring member provided with a flange, a first inner ring raceway at the other end portion, and a fitting for fixing the first inner ring member to the first inner ring member without rattling. A second inner ring member having a second inner ring raceway on the outer peripheral surface of the intermediate portion and having the other end portion as a housing part serving as an outer ring of the constant velocity joint, the outer ring raceways, and the inner ring raceways. A plurality of rolling elements provided so as to be freely rotatable between the first inner ring member and a first small-diameter portion formed with a female spline groove on the inner peripheral surface of the first inner ring member. A second small diameter portion that is a cylindrical surface having a diameter larger than that of the first small diameter portion And the outer peripheral surface of the fitting support portion includes a first fitting surface portion in which a male spline groove that engages with a female spline groove formed in the first small diameter portion is formed, and the second small diameter portion. In a rolling bearing unit for a wheel which is provided concentrically with a second fitting surface portion which is a cylindrical surface to be fitted, the fitting between the second small diameter portion and the second fitting surface portion is performed. The second fitting surface portion as the cylindrical surface and the second small diameter than the axial length of the first fitting surface portion in which the male spline groove is formed as a fitting with a tightening margin. When the first and second inner ring members are combined with each other, the second small diameter portion and the second small diameter portion and the second small diameter portion are started before the two spline grooves start to engage with each other. And the second small diameter portion and the second small diameter portion and the second small diameter portion. Prior to the start of mating with the mating surface portion, a positioning recess or projection for aligning the circumferential phase of the two spline grooves is a part of the outer peripheral surface of the second inner ring member. A rolling bearing unit for supporting a wheel, wherein the rolling bearing unit is provided at a portion removed from the male spline groove or at an axial end surface portion .
JP23371399A 1999-08-20 1999-08-20 Rolling bearing unit for wheels Expired - Fee Related JP4269422B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP23371399A JP4269422B2 (en) 1999-08-20 1999-08-20 Rolling bearing unit for wheels

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP23371399A JP4269422B2 (en) 1999-08-20 1999-08-20 Rolling bearing unit for wheels

Publications (3)

Publication Number Publication Date
JP2001059518A JP2001059518A (en) 2001-03-06
JP2001059518A5 JP2001059518A5 (en) 2006-09-21
JP4269422B2 true JP4269422B2 (en) 2009-05-27

Family

ID=16959397

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JP4613462B2 (en) * 2001-08-08 2011-01-19 株式会社ジェイテクト Axle bearing device
JP6180723B2 (en) 2012-11-05 2017-08-16 Ntn株式会社 Double row rolling bearing

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