JP2003042173A

JP2003042173A - Roller bearing unit for supporting wheel

Info

Publication number: JP2003042173A
Application number: JP2002148895A
Authority: JP
Inventors: Yoshihisa Onuki; 善久大貫; Hironari Miyazaki; 裕也宮崎
Original assignee: NSK Ltd
Current assignee: NSK Ltd
Priority date: 2002-05-23
Filing date: 2002-05-23
Publication date: 2003-02-13
Anticipated expiration: 2016-09-25
Also published as: JP3815376B2

Abstract

PROBLEM TO BE SOLVED: To make it hard to damage the inner ring 3 or a caulking widening section for fixing the inner ring 3 to a shaft member 2 by caulking and widening the cylindrical part 21 of the shaft member 2. SOLUTION: A slope face 19 is formed on the end inner peripheral face of the inner ring 3, and the cylindrical part 21 is caulked and widened toward the slope face 19, and that makes it possible to reduce the deformation of the cylindrical part 21, hardly damages the caulking widening part and reduces the deformation of the inner ring 3.

Description

【発明の詳細な説明】【０００１】【発明の属する技術分野】この発明に係る車輪支持用転
がり軸受ユニットは、自動車の車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】自動車の車輪は、車輪支持用転がり軸受
ユニットにより懸架装置に支持する。この様な場合に使
用する車輪支持用転がり軸受ユニットとして、従来から
例えば、特開昭６３−１０６４２６号公報、同６３−１
８４５０１号公報、同６２−２１４８８９号公報、特開
平３−３１００１号公報、米国特許第４５３７２７０号
明細書、同４９５８９４４号明細書、同５２２６７３８
号明細書、同５４９０７３２号明細書等に記載されたも
のが知られている。又、図８は、従来から広く実施され
ている車輪支持用転がり軸受ユニットの１例を示してい
る。この車輪支持用転がり軸受ユニット１は、シャフト
部材２と、内輪３と、外輪４と、複数個の転動体５、５
とを備える。このうちのシャフト部材２の外周面の外端
部（外とは、自動車への組み付け状態で幅方向外寄りと
なる側を言い、各図の左側となる。反対に幅方向中央寄
りとなる側を内と言い、各図の右側となる。）で上記外
輪４から突出した部分には、車輪を支持する為の第二の
フランジ６を形成している。又、このシャフト部材２の
中間部には第一の内輪軌道７を、同じく内端部には外径
寸法が小さくなった段部８を、それぞれ形成している。【０００３】そして、この段部８に、その外周面に第二
の内輪軌道９を形成した上記内輪３を外嵌している。上
記シャフト部材２の内端部には雄ねじ部１０を形成し、
この雄ねじ部１０の先端部を、上記内輪３の内端面より
も内方に突出させている。そして、この雄ねじ部１０に
螺合したナット１１と上記段部８の段差面１２との間で
上記内輪３を挟持する事により、この内輪３を上記シャ
フト部材２の所定位置に結合固定している。上記雄ねじ
部１０の先端部外周面には係止凹部１７を形成してい
る。そして、上記ナット１１を所定のトルクで緊締した
後、このナット１１の一部で上記係止凹部１７に整合す
る部分を直径方向内方にかしめ付ける事により、このナ
ット１１の緩み止めを図っている。尚、上記シャフト部
材２に１対の内輪を外嵌し、これら１対の内輪の外周面
に、第一、第二の内輪軌道７、９を設ける構造も、従来
から知られている。【０００４】又、上記外輪４の内周面には、上記第一の
内輪軌道７と対向する第一の外輪軌道１３及び上記第二
の内輪軌道９に対向する第二の外輪軌道１４を形成して
いる。そして、これら第一、第二の内輪軌道７、９と第
一、第二の外輪軌道１３、１４との間に上記転動体５、
５を、それぞれ複数個ずつ設けている。これら各転動体
５、５の設置空間の外端開口はシールリング２２によ
り、内端開口は蓋体２９により、それぞれ塞いでいる。
尚、図示の例では、転動体５、５として玉を使用してい
るが、重量の嵩む自動車用の車輪支持用転がり軸受ユニ
ットの場合には、これら転動体としてテーパころを使用
する場合もある。【０００５】上述の様な車輪支持用転がり軸受ユニット
１を自動車に組み付けるには、上記外輪４を、その外周
面の一部に形成した第一のフランジ１５により懸架装置
に固定し、上記第二のフランジ６に車輪を固定する。こ
の結果、この車輪が懸架装置に対して回転自在に支持さ
れる。【０００６】又、前記米国特許第５２２６７３８号明細
書には、図９に示す様な構造の車輪支持用転がり軸受ユ
ニット１が記載されている。この従来構造の第２例の場
合には、シャフト部材２の内端部に形成した円筒部の一
部で内輪３の内端面よりも内方に突出した部分を直径方
向外方に折り曲げる事により、かしめ部１６を形成して
いる。そして、このかしめ部１６と段部８の段差面１２
との間で、上記内輪３を挟持している。【０００７】【発明が解決しようとする課題】図８に示した従来構造
の第１例の場合には、雄ねじ部１０の先端部に係止凹部
１７を形成する作業、及びナット１１の一部を直径方向
内方にかしめ付ける作業が必要になる。この為、車輪支
持用転がり軸受ユニット１の部品製造作業及び組立作業
が面倒になり、コストが嵩む。【０００８】又、図９に示した第２例の構造の場合、シ
ャフト部材２に対して内輪３を結合固定する為のかしめ
部１６の形成時に、このかしめ部１６が隣接する内輪３
の内周面に、直径方向外方に向いた力が加わる。この
為、この内輪３の直径が僅かとは言え変化する。そし
て、この変化量が大きくなると、この内輪３に亀裂等の
損傷が発生する可能性が生じるだけでなく、転動体５、
５に付与した予圧を適正値に維持する作業が面倒にな
り、上記内輪３を含む車輪支持用転がり軸受ユニット１
の耐久性を確保する事が難しくなる可能性がある。特
に、上記シャフト部材２に対して上記内輪３が回転する
事を防止すべく、上記かしめ部１６のかしめ強度を十分
に確保しようとした場合には、上記変形量が大きくなり
易く、上記内輪３の耐久性確保が難しくなる。【０００９】この様な事情に鑑みて特願平８−３６８０
０号には、内輪の端面とかしめ部との間にスペーサリン
グを設け、かしめ部の形成作業に伴う、直径方向外方に
向いた力をこのスペーサリングにより受ける構造が開示
されている。この先発明に係る構造によれば、かしめ部
の形成作業に伴って発生する、直径方向外方に向いた力
の大部分を上記スペーサリングが受ける。従って、上記
内輪にはこの直径方向外方に向いた力が殆ど伝わらず、
この内輪の損傷防止を図れる。但し、この様なスペーサ
リングを設けた構造の場合でも、上記かしめ部自体、円
筒部からの加工量が多く、かしめ作業に伴う変形に基づ
いて亀裂等が発生し易く、耐久性の確保が難しい。【００１０】本発明の車輪支持用転がり軸受ユニット
は、この様な事情に鑑みて、内輪の内径がこの内輪の固
定作業に基づいて変化しない様にし、且つかしめ部に亀
裂等の損傷が発生しにくくすると共に、シャフト部材に
対し内輪を固定するナットの緩み止めを図る為の係止凹
部の形成作業やナットのかしめ付け作業を省略する事に
より、コスト低減を図る事を目的に発明したものであ
る。【００１１】【課題を解決するための手段】本発明の車輪支持用転が
り軸受ユニットは何れも、従来の、或は先発明の車輪支
持用転がり軸受ユニットと同様に、外周面に第一のフラ
ンジを、内周面に複列の内輪軌道を、それぞれ設けた外
輪と、端部外周面に第二のフランジを設けたシャフト部
材と、外周面に内輪軌道を有し上記シャフト部材に外嵌
した、少なくとも１個の内輪と、この内輪を含んで上記
シャフト部材と共に回転する部分の外周面に設けた第
一、第二の内輪軌道と上記複列の外輪軌道との間に、そ
れぞれ複数個ずつ設けた転動体とを備える。そして、上
記シャフトの端部に形成した円筒部の一部で上記内輪よ
りも突出した部分を直径方向外方にかしめ広げ、このか
しめ広げた部分により上記内輪を直接又はスペーサリン
グを介して抑え付ける事により、上記内輪を上記シャフ
トに固定している。特に、本発明の車輪支持用転がり軸
受ユニットに於いては、上記内輪若しくはこの内輪より
も上記シャフトの先端寄りに外嵌したスペーサリングの
開口周縁部で上記円筒部をかしめ広げた部分の外周面が
押し付けられる部分を、開口端に向かう程内径が大きく
なる、円錐凹面状の傾斜面としている。【００１２】更に好ましくは、次の〜の構成要件
を、それぞれ単独で、或は〜のうちから選択される
複数の構成要件を、上記必須要件に組み合わせて実施す
る。上記円筒部を構成すべく、上記シャフト部材の端部
に形成する円形の凹部の先端の、このシャフトの軸方向
に関する位置は、上記第二の内輪軌道に当接する転動体
の中心の上記シャフト部材の軸方向に関する位置より
も、上記シャフト部材の端部側に位置する。上記第二の内輪軌道に当接する転動体の中心と、上
記内輪の端面若しくはこの内輪の肩部の端面との、上記
シャフト部材の軸方向に関する距離は、上記転動体の外
径の０．７５倍以上である。上記内輪の端部で上記傾斜面を形成した部分の外径
を、この内輪の肩部の外径よりも小さくする。上記シャフト部材の先端部で上記内輪の嵌合部、若
しくは内輪及びスペーサリングの嵌合部よりも突出した
部分の外径を、この嵌合部の外径よりも小さくし、上記
シャフト部材の端部に形成した円筒部のうちの外径の小
さくなった部分を、直径方向外方にかしめ広げる。上記シャフト部材の先端部外周面の一部で、上記傾
斜面の小径側端部に対向する部分に凹溝を、上記外周面
の全周に亙って形成し、上記シャフト部材の端部に形成
した円筒部のうちの凹溝よりも先端寄り部分を、直径方
向外方にかしめ広げる。転動体から内輪に加わる荷重の作用線の延長位置
を、上記傾斜面よりもシャフト部材の軸方向中央寄り
で、このシャフト部材の外径が変化しない部分に存在さ
せる。【００１３】【作用】上述の様に構成される本発明の車輪支持用転が
り軸受ユニットにより、懸架装置に対して車輪を回転自
在に支持する作用は、従来の車輪支持用転がり軸受ユニ
ットと同様である。特に、本発明の車輪支持用転がり軸
受ユニットの場合には、シャフト部材の端部に形成した
円筒部をかしめ広げた部分の外周面が押し付けられる部
分を、開口端に向かう程内径が大きくなる、円錐凹面状
の傾斜面としている為、このかしめ部分の変形量が少な
くて済む。この為、このかしめ部分に発生する歪みを小
さく抑えて、このかしめ部に割れ等の損傷が発生するの
を抑える事ができる。又、上記変形量を少なく抑える
為、このかしめ部を形成する事に基づき、上記円筒部の
周囲に存在する部材にその直径方向外方に加わる力を低
減できる。この結果、スペーサリングを用いた場合は勿
論、スペーサリングを用いない場合でも、内輪にその直
径方向外方に加わる力を低減して、この内輪の損傷防止
を図れる。【００１４】【発明の実施の形態】図１〜２は、前記の構成要件
を組み込んだ、本発明の実施の形態の第１例を示してい
る。尚、本発明の特徴は、シャフト部材２に対して内輪
３を固定する部分の構造にある。その他の部分の構造及
び作用に就いては、前述の図８に示した従来構造と同様
であるから、重複する説明を省略若しくは簡略にし、以
下、本発明の特徴部分を中心に説明する。【００１５】シャフト部材２の内端部に形成した段部８
の中間部内端寄り部分で、この段部８に外嵌した内輪３
の内端部内周面に、内端開口に向かう程内径が大きくな
る、円錐凹面状の傾斜面１９を形成している。この傾斜
面１９が上記シャフト部材２の中心軸に対し傾斜してい
る傾斜角度θは、２０〜６０度程度とする。又、上記シ
ャフト部材２の内端面には円形の凹部２０を形成する事
により、このシャフト部材２の内端部に円筒部２１を形
成している。本例の場合にこの円筒部２１は、上記シャ
フト部材２の内端部で、ほぼ上記内輪３の肩部２３の内
側部分に存在する。【００１６】上述の様な傾斜面１９を形成した内輪３
を、上記シャフト部材２の内端部に設けた円筒部２１を
かしめ広げる事によりこのシャフト部材２に固定し、本
発明の車輪支持用転がり軸受ユニットとする際には、前
記図９に示した従来構造の場合に比べて、かしめ部分の
変形量が少なくて済む。即ち、上記従来構造の場合には
かしめ部１６を形成する為、シャフト部材２の内端部に
形成した円筒部を直径方向外方に向け、９０度折り曲げ
るのに対して、本発明の車輪支持用転がり軸受ユニット
を構成すべく、上記円筒部２１をかしめ広げる際には、
この円筒部２１を上記傾斜角度θ（＝２０〜６０度）だ
け変形させれば良い。この為、このかしめ部分に発生す
る歪みを小さく抑えて、このかしめ部に割れ等の損傷が
発生するのを抑える事ができる。又、上記変形量を少な
く抑える為、このかしめ部を形成する事に基づき、上記
円筒部２１の周囲に存在する部材である上記内輪３に、
この内輪３の直径方向外方に加わる力を低減できて、こ
の内輪３の損傷防止を図れる。【００１７】尚、上記円筒部２１を直径方向外方にかし
め広げる作業は、鍛造加工、或は揺動プレス加工により
行なう。何れの加工法を採用する場合でも、図２に示す
様に、上記円筒部２１の内径側にプレス型２５を押し込
み、上記円筒部２１を直径方向外方にかしめ広げる。特
に、かしめ作業に揺動プレス加工を採用すれば、成形時
の荷重を小さくして、軸受内部への影響をなくし、成形
後の予圧管理を適正にできると言った利点がある。又、
上記円筒部２１の奥端縁（この円筒部２１の内径が変化
しない部分の奥端）と上記内輪３の端面２４との距離Ｌ
は、車輪支持用転がり軸受ユニットの大きさ等の応じて
設計的に定めるが、一般的な乗用車用の車輪支持用転が
り軸受ユニットの場合で、５〜１５mm程度とするのが好
ましい。【００１８】又、上記円筒部２１を構成すべく、上記シ
ャフト部材２の端部に形成する円形の凹部２０の先端位
置は、複列に配置した転動体５、５のうち、内側の列を
構成する転動体５の中心よりも内側に位置させている。
即ち、図１に点Ｘで示した、上記凹部２０の先端の、上
記シャフト部材２の軸方向に関する位置は、第二の内輪
軌道である、上記内輪３の外周面に設けた第二の内輪軌
道９に当接する転動体５の中心の、上記シャフト部材２
の軸方向に関する位置よりも、上記シャフト部材２の内
端部側に位置させている。従って、車輪支持用転がり軸
受ユニットを構成するシャフト部材２と外輪４との間に
ラジアル荷重が加わり、上記転動体５から上記第二の内
輪軌道９にラジアル荷重が加わった場合でも、上記シャ
フト部材２の一部でこのラジアル荷重を受ける部分が充
実体である為、このシャフト部材２の耐久性を十分に確
保できる。【００１９】更に、上記第二の内輪軌道９に当接する転
動体５の中心と、上記内輪３の端面２４との、上記シャ
フト部材２の軸方向に関する距離Ｍを、上記各転動体
５、５の外径Ｄの０．７５倍以上（Ｍ≧０．７５Ｄ）と
している。この様に、転動体５の中心と端面２４との距
離Ｍを確保している為、上記内輪３の肩部２３や第二の
内輪軌道９部分の寸法精度や形状精度が悪化する事を防
止して、車輪支持用転がり軸受ユニットの機能を確保で
きる。即ち、これら各部分の寸法精度や形状精度を良好
に確保できるので、車輪支持用転がり軸受ユニットの運
転時に振動等が発生するのを防止すると共に、転動体５
の転動面や第二の内輪軌道９の転がり疲れ寿命等を確保
できる。尚、図示の例では、第一の内輪軌道７をシャフ
ト部材２の中間部外周面に直接形成しているが、この第
一の内輪軌道７は、シャフト部材２と別体の内輪に形成
し、この内輪をこのシャフト部材２に外嵌固定しても良
い。【００２０】次に、図３は、前記の構成要件を組
み込んだ、本発明の実施の形態の第２例を示している。
本例の場合には、シャフト部材２の内端部で、このシャ
フト部材２に外嵌した内輪３の端面２４よりも内方に突
出した部分に、スペーサリング１８を外嵌している。こ
のスペーサリング１８の内半部内周面には、内端開口に
向かう程内径が大きくなる、円錐凹面状の傾斜面１９を
形成している。そして、上記シャフト部材２の内端部で
上記スペーサリング１８の内側に存在する円筒部２１を
直径方向外方にかしめ広げる事により、上記スペーサリ
ング１８を上記内輪３の端面２４に向け抑え付けて、こ
の内輪３を上記シャフト部材２に結合固定している。
又、第二の内輪軌道９と第二の外輪軌道１４との間に設
けた転動体５から内輪３に加わる荷重の作用線（接触角
を表す鎖線αと一致する）の延長位置は、上記傾斜面１
９よりも段部８の軸方向中央寄りで、外径が変化しない
部分に存在する。【００２１】本例の場合、この様なスペーサリング１８
を設ける事により、上記円筒部２１をかしめ広げる際の
かしめ強度を十分に大きくした場合でも、上記内輪３が
直径方向に弾性変形する事を確実に防止できる。即ち、
本例の場合には、上記円筒部２１をかしめ広げる際に加
わる、直径方向外方に向いた力は、シャフト部材２に外
嵌したスペーサリング１８が受ける。従って、上記円筒
部２１をかしめ広げる作業に伴って、上記内輪３の直径
が変化する事が、前述した第１例の場合よりも少なくな
る（殆ど変化しなくなる）。尚、仮にスペーサリング１
８の寸法精度、及び形状精度が悪化しても、車輪支持用
転がり軸受ユニットの性能には何らの悪影響も及ぼさな
い。又、本例の場合には、上記荷重の作用線の延長位置
を規制している為、この荷重が上記円筒部２１をかしめ
広げた部分に作用する事を防止して、かしめ固定部分の
耐久性を確保できる。スペーサリング１８を設けた点、
並びに作用線の延長位置を規制した点以外の構成及び作
用は、前述した第１例の場合と同様である。【００２２】次に、図４は、前記の構成要件を
組み込んだ、本発明の実施の形態の第３例を示してい
る。本例の場合には、シャフト部材２の内端部に外嵌し
た内輪３ａの内端部で傾斜面１９を形成した部分の外径
を、この内輪３ａの肩部２３の外径よりも小さくして、
内輪円筒部２６としている。この様な本例の場合、上記
シャフト部材２の内端部に形成した円筒部２１を、上記
傾斜面１９に向けて直径方向外方にかしめ広げ、上記内
輪３をシャフト部材２に固定する際には、上記内輪円筒
部２６が、かしめ広げに伴う応力の大部分を受ける。従
って、肩部２３に比較して薄肉の内輪円筒部２６の変形
量は多くなるが、上記内輪３ａの肩部２３及び第二の内
輪軌道９の変形量を小さくできる。この結果、車輪支持
用転がり軸受ユニットの回転精度を十分良好な状態に維
持できる。尚、本例の場合には、上記第二の内輪軌道９
に当接する転動体５の中心と、上記内輪３ａの肩部２３
の端面２４ａとの、上記シャフト部材２の軸方向に関す
る距離Ｍを、上記各転動体５、５の外径Ｄの０．７５倍
以上（Ｍ≧０．７５Ｄ）としている。又、本例の場合
も、荷重の作用線の延長位置を規制して、かしめ固定部
分の耐久性確保を図っている。その他の構成及び作用
は、前述した第１例の場合と同様である。【００２３】次に、図５は、前記の構成要件を組み
込んだ、本発明の実施の形態の第４例を示している。上
述した第１〜３例の場合には、外輪４を回転しない静止
輪とし、シャフト部材２を回転させる構造であったのに
対して、本例の場合には、シャフト部材２を懸架装置に
支持して回転させず、外輪４を車輪と共に回転する回転
輪としている。回転側と静止側とが逆になった以外の構
成及び作用は、前述した第１例の場合と同様である。【００２４】次に、図６は、前記の構成要件を組
み込んだ、本発明の実施の形態の第５例を示している。
本例の場合、シャフト部材２の内端部で内輪３の嵌合部
よりも突出した部分の外径を、この嵌合部の外径よりも
小さくしている。即ち、上記シャフト部材２の内端部に
形成した円筒部２１の基端部外周面で、この内輪３の内
端開口部に形成した傾斜面１９よりも少しだけ第二の内
輪軌道９に寄った部分に、０．０２〜１mm程度の僅かな
段差Ｈを有する段差部２７を形成している。そして、上
記円筒部２１のうちの外径の小さくなった部分を、直径
方向外方にかしめ広げ、上記傾斜面１９を抑え付ける様
にしている。この様に円筒部２１を直径方向外方にかし
め広げる際には、上記段差部２７がかしめ広げ作業に伴
って折れ曲がる部分の起点となる。この為、かしめ広げ
作業に伴って上記円筒部２１に無理な力が加わりにくく
なって、かしめ広げ部分に亀裂等の損傷が発生しにくく
なる。その他の構成及び作用は、前述した第１例の場合
と同様である。尚、本例の構造を上述した第４例に適用
する場合には、軸方向に関する内外方向が逆になる。【００２５】次に、図７は、前記の構成要件を組
み込んだ、本発明の実施の形態の第６例を示している。
本例の場合、シャフト部材２の内端部外周面の一部で、
内輪３の内端部に形成した傾斜面１９の小径側端部に対
向する部分に、０．１〜２mm程度の深さＫを有する凹溝
２８を、上記外周面の全周に亙って形成している。そし
て、上記シャフト部材２の内端部に形成した円筒部２１
のうちの上記凹溝２８よりも内端寄り部分を、直径方向
外方にかしめ広げ、上記傾斜面１９を抑え付ける様にし
ている。この様に円筒部２１を直径方向外方にかしめ広
げる際には、上記凹溝２８がかしめ広げ作業に伴って折
れ曲がる部分の起点となる。この為、かしめ広げ作業に
伴って上記円筒部２１に無理な力が加わりにくくなっ
て、かしめ広げ部分に亀裂等の損傷が発生しにくくな
る。その他の構成及び作用は、前述した第１例の場合と
同様である。尚、本例の構造を上述した第４例に適用す
る場合にも、軸方向に関する内外方向が逆になる。【００２６】【発明の効果】本発明の車輪支持用転がり軸受ユニット
は、以上に述べた通り構成され作用するので、内輪の直
径が変化する事を防止して、この内輪及びこの内輪を固
定する為のかしめ広げ部分が、上記内輪の固定作業に基
づいて損傷する可能性を低くできる。又、予圧を適正値
に維持でき、しかも部品点数、部品加工、組立工数の減
少により、コスト低減を図れる。Description: BACKGROUND OF THE INVENTION A rolling bearing unit for supporting a wheel according to the present invention is used to rotatably support a wheel of an automobile with respect to a suspension device. 2. Description of the Related Art Wheels of a motor vehicle are supported by a suspension device by means of wheel-supporting rolling bearing units. Conventionally, as a rolling bearing unit for supporting a wheel used in such a case, for example, JP-A-63-106426 and JP-A-63-1
Nos. 84501, 62-214889, JP-A-3-31001, U.S. Pat. Nos. 4,537,270, 4,958,944, and 5,267,738.
And Japanese Patent No. 5490732 are known. FIG. 8 shows an example of a widely used rolling bearing unit for supporting a wheel. The wheel supporting rolling bearing unit 1 includes a shaft member 2, an inner ring 3, an outer ring 4, and a plurality of rolling elements 5, 5
And Of these, the outer end portion of the outer peripheral surface of the shaft member 2 (outside refers to a side that is shifted outward in the width direction when assembled to an automobile, and is the left side in each drawing. Conversely, a side that is shifted toward the center in the width direction Is referred to as the inner side, which is on the right side of each drawing.) In the portion protruding from the outer ring 4, a second flange 6 for supporting the wheel is formed. Further, a first inner raceway 7 is formed at an intermediate portion of the shaft member 2, and a step 8 having a smaller outer diameter is formed at an inner end of the shaft member 2. The inner ring 3 having a second inner ring raceway 9 formed on the outer peripheral surface of the step portion 8 is externally fitted. A male screw portion 10 is formed at the inner end of the shaft member 2,
The distal end portion of the male screw portion 10 projects inward from the inner end surface of the inner ring 3. The inner ring 3 is held between a nut 11 screwed to the male screw portion 10 and the stepped surface 12 of the step portion 8, so that the inner ring 3 is connected and fixed to a predetermined position of the shaft member 2. I have. A locking recess 17 is formed on the outer peripheral surface of the distal end of the male screw portion 10. Then, after tightening the nut 11 with a predetermined torque, a portion of the nut 11 that is aligned with the locking concave portion 17 is crimped inward in the diametrical direction to prevent the nut 11 from loosening. I have. A structure in which a pair of inner races are externally fitted to the shaft member 2 and first and second inner raceways 7 and 9 are provided on the outer peripheral surfaces of the pair of inner races is conventionally known. A first outer raceway 13 facing the first inner raceway 7 and a second outer raceway 14 facing the second inner raceway 9 are formed on the inner peripheral surface of the outer race 4. are doing. And between the first and second inner raceways 7, 9 and the first and second outer raceways 13, 14, the rolling elements 5,
5 are provided in plurality. An outer end opening of the installation space of each of the rolling elements 5 and 5 is closed by a seal ring 22, and an inner end opening is closed by a lid 29.
Although balls are used as the rolling elements 5 and 5 in the illustrated example, tapered rollers may be used as these rolling elements in the case of a heavy-weight rolling bearing unit for an automobile wheel. . In order to assemble the above-described wheel supporting rolling bearing unit 1 into an automobile, the outer ring 4 is fixed to a suspension device by a first flange 15 formed on a part of the outer peripheral surface thereof, and The wheel is fixed to the flange 6 of. As a result, the wheel is rotatably supported by the suspension. [0006] The above-mentioned US Pat. No. 5,227,738 discloses a rolling bearing unit 1 for supporting wheels having a structure as shown in FIG. In the case of the second example of this conventional structure, a part of the cylindrical portion formed at the inner end of the shaft member 2 and protruding inward from the inner end surface of the inner race 3 is bent outward in the diameter direction. , A swaging portion 16 is formed. Then, the caulked portion 16 and the step surface 12 of the step portion 8 are formed.
, The inner ring 3 is sandwiched. [0008] In the case of the first example of the conventional structure shown in FIG. 8, the operation of forming the locking concave portion 17 at the tip of the male screw portion 10 and a part of the nut 11 are performed. It is necessary to caulk the inward in the diameter direction. For this reason, the parts manufacturing operation and the assembling operation of the wheel supporting rolling bearing unit 1 are troublesome, and the cost is increased. In the case of the structure of the second example shown in FIG. 9, when the caulked portion 16 for connecting and fixing the inner ring 3 to the shaft member 2 is formed, the caulked portion 16 is adjacent to the inner ring 3.
A force directed diametrically outward is applied to the inner peripheral surface of the. For this reason, the diameter of the inner ring 3 changes, albeit slightly. When the amount of change becomes large, not only the possibility that damage such as a crack occurs in the inner ring 3 occurs, but also the rolling elements 5,
The operation of maintaining the preload applied to the wheel 5 at an appropriate value becomes troublesome, and the rolling bearing unit 1 for supporting the wheel including the inner ring 3 is provided.
It may be difficult to ensure the durability of the. In particular, when the caulking strength of the caulking portion 16 is sufficiently ensured in order to prevent the inner ring 3 from rotating with respect to the shaft member 2, the deformation amount is likely to increase, and the inner ring 3 It is difficult to ensure the durability of the tire. [0009] In view of such circumstances, Japanese Patent Application No. Hei 8-3680.
No. 0 discloses a structure in which a spacer ring is provided between an end face of an inner race and a caulked portion, and a force directed outward in a diametrical direction accompanying the forming operation of the caulked portion is received by the spacer ring. According to the structure according to the preceding invention, the spacer ring receives most of the diametrically outward force generated during the formation of the caulked portion. Therefore, the diametrically outward force is hardly transmitted to the inner ring,
The inner ring can be prevented from being damaged. However, even in the case of such a structure provided with the spacer ring, the caulking portion itself, the amount of processing from the cylindrical portion is large, cracks and the like are easily generated based on deformation due to the caulking work, and it is difficult to ensure durability. . In view of such circumstances, the rolling bearing unit for supporting a wheel according to the present invention prevents the inner diameter of the inner ring from changing due to the fixing work of the inner ring, and causes damage such as cracks to the swaged portion. It was invented for the purpose of reducing costs by eliminating the work of forming the locking recess and the work of caulking the nut to prevent loosening of the nut that fixes the inner ring to the shaft member and to prevent the nut from becoming loose. is there. [0011] Each of the rolling bearing units for supporting a wheel according to the present invention has a first flange on the outer peripheral surface, similarly to the rolling bearing unit for supporting a wheel of the prior art or the prior invention. A double row inner ring raceway on the inner peripheral surface, an outer ring provided respectively, a shaft member provided with a second flange on the end outer peripheral surface, and an outer ring surface having an inner raceway on the outer peripheral surface are externally fitted to the shaft member. A plurality of at least one inner ring and a plurality of inner rings between first and second inner ring raceways provided on the outer peripheral surface of a portion including the inner ring and rotating with the shaft member, and the double row outer ring raceway. Provided rolling elements. Then, a portion of the cylindrical portion formed at the end of the shaft, which protrudes from the inner ring, is swaged diametrically outward, and the swaged portion suppresses the inner ring directly or via a spacer ring. Thus, the inner ring is fixed to the shaft. In particular, in the wheel bearing rolling bearing unit of the present invention, the outer peripheral surface of a portion where the cylindrical portion is swaged and widened at the opening peripheral edge of the inner ring or a spacer ring externally fitted closer to the tip of the shaft than the inner ring. Is pressed as a conical concave inclined surface whose inner diameter increases toward the opening end. [0012] More preferably, the following constituent requirements are individually implemented, or a plurality of constituent requirements selected from the following are combined with the above essential requirements. The position of the tip of the circular concave portion formed at the end of the shaft member in the axial direction of the shaft to form the cylindrical portion is the center of the rolling member abutting on the second inner raceway. Is located closer to the end of the shaft member than the position in the axial direction. The distance in the axial direction of the shaft member between the center of the rolling element abutting on the second inner ring raceway and the end face of the inner ring or the end face of the shoulder of the inner ring is 0.75 of the outer diameter of the rolling element. More than double. The outer diameter of the portion where the inclined surface is formed at the end of the inner ring is made smaller than the outer diameter of the shoulder of the inner ring. An outer diameter of a fitting portion of the inner ring or a portion protruding from a fitting portion of the inner ring and the spacer ring at a tip portion of the shaft member is made smaller than an outer diameter of the fitting portion, and an end of the shaft member is formed. A portion having a smaller outer diameter of the cylindrical portion formed in the portion is swaged outward in the diameter direction. A groove is formed in a part of the outer peripheral surface of the distal end portion of the shaft member facing the small diameter side end portion of the inclined surface over the entire periphery of the outer peripheral surface, and is formed at the end of the shaft member. The portion of the formed cylindrical portion closer to the tip than the concave groove is swaged outward in the diameter direction. The extended position of the line of action of the load applied to the inner race from the rolling element is located closer to the axial center of the shaft member than the inclined surface and at a portion where the outer diameter of the shaft member does not change. The function of the wheel supporting rolling bearing unit of the present invention configured as described above to rotatably support the wheel with respect to the suspension is the same as that of the conventional wheel supporting rolling bearing unit. is there. In particular, in the case of the wheel bearing rolling bearing unit of the present invention, the portion against which the outer peripheral surface of the portion formed by caulking the cylindrical portion formed at the end of the shaft member is pressed, the inner diameter increases toward the open end, Since the inclined surface has a conical concave shape, the amount of deformation of the swaged portion can be reduced. For this reason, it is possible to suppress distortion generated in the swaged portion to be small, and to suppress occurrence of damage such as a crack in the swaged portion. Further, in order to suppress the deformation amount, the force applied to the members existing around the cylindrical portion in the radial direction can be reduced based on the formation of the caulked portion. As a result, not only when the spacer ring is used but also when the spacer ring is not used, the force applied to the inner ring in the diametrically outward direction can be reduced, and the inner ring can be prevented from being damaged. FIGS. 1 and 2 show a first embodiment of the present invention incorporating the above-mentioned components. The feature of the present invention lies in the structure of a portion for fixing the inner race 3 to the shaft member 2. The structure and operation of the other parts are the same as those of the conventional structure shown in FIG. 8 described above. Therefore, the overlapping description will be omitted or simplified, and the following description will focus on the features of the present invention. Step 8 formed at the inner end of shaft member 2
The inner ring 3 externally fitted to the step 8 at a portion near the inner end of the middle
A conical concave inclined surface 19 whose inner diameter increases toward the inner end opening is formed on the inner peripheral surface of the inner end. The inclination angle θ at which the inclined surface 19 is inclined with respect to the center axis of the shaft member 2 is set to be about 20 to 60 degrees. Further, by forming a circular concave portion 20 on the inner end surface of the shaft member 2, a cylindrical portion 21 is formed on the inner end portion of the shaft member 2. In the case of the present example, the cylindrical portion 21 is present at the inner end of the shaft member 2 and substantially inside the shoulder portion 23 of the inner ring 3. The inner ring 3 having the above-described inclined surface 19 is formed.
Is fixed to the shaft member 2 by caulking and expanding the cylindrical portion 21 provided at the inner end of the shaft member 2 to obtain the wheel supporting rolling bearing unit of the present invention, as shown in FIG. The amount of deformation of the swaged portion is smaller than in the case of the conventional structure. That is, in the case of the conventional structure, the cylindrical portion formed at the inner end of the shaft member 2 is diametrically outwardly bent at 90 degrees in order to form the caulked portion 16, whereas the wheel support according to the present invention is formed. When swaging the cylindrical portion 21 to form a rolling bearing unit for use,
What is necessary is just to deform | transform this cylindrical part 21 only by the said inclination angle (theta) (= 20-60 degrees). For this reason, it is possible to suppress distortion generated in the swaged portion to be small, and to suppress occurrence of damage such as a crack in the swaged portion. Further, in order to suppress the deformation amount, the inner ring 3 which is a member existing around the cylindrical portion 21 is formed based on the formation of the caulked portion.
The force applied to the inner ring 3 outward in the diameter direction can be reduced, and the inner ring 3 can be prevented from being damaged. The operation of caulking and expanding the cylindrical portion 21 outward in the diameter direction is performed by forging or oscillating pressing. Regardless of which processing method is employed, as shown in FIG. 2, a press die 25 is pushed into the inner diameter side of the cylindrical portion 21 and the cylindrical portion 21 is swaged outward in the diameter direction. In particular, if the swing press working is employed for the caulking operation, there is an advantage that the load at the time of molding can be reduced, the influence on the inside of the bearing can be eliminated, and the preload management after the molding can be properly performed. or,
Distance L between the back end edge of the cylindrical portion 21 (the back end of the portion where the inner diameter of the cylindrical portion 21 does not change) and the end surface 24 of the inner ring 3
Is determined in design according to the size of the rolling bearing unit for supporting the wheel, etc., but it is preferably about 5 to 15 mm in the case of a rolling bearing unit for supporting a wheel for a general passenger car. In order to form the cylindrical portion 21, the tip position of the circular concave portion 20 formed at the end of the shaft member 2 corresponds to the inner row of the rolling elements 5, 5 arranged in multiple rows. It is positioned inside the center of the rolling element 5 that constitutes it.
That is, the position of the tip of the concave portion 20 in the axial direction of the shaft member 2 indicated by the point X in FIG. 1 is the second inner race provided on the outer peripheral surface of the inner race 3 as the second inner raceway. The shaft member 2 at the center of the rolling element 5 in contact with the track 9
Is located closer to the inner end of the shaft member 2 than the position in the axial direction. Therefore, even when a radial load is applied between the shaft member 2 and the outer ring 4 that constitute the wheel supporting rolling bearing unit, and a radial load is applied from the rolling element 5 to the second inner raceway 9, the shaft member Since a portion of the shaft member 2 that receives the radial load is a solid body, the durability of the shaft member 2 can be sufficiently ensured. Further, the distance M in the axial direction of the shaft member 2 between the center of the rolling element 5 abutting on the second inner ring raceway 9 and the end surface 24 of the inner ring 3 is determined by each of the rolling elements 5, 5 0.75 times or more (M ≧ 0.75D) of the outer diameter D of In this way, since the distance M between the center of the rolling element 5 and the end face 24 is ensured, the dimensional accuracy and the shape accuracy of the shoulder 23 of the inner ring 3 and the second inner ring raceway 9 are prevented from deteriorating. Thus, the function of the wheel supporting rolling bearing unit can be secured. That is, since the dimensional accuracy and the shape accuracy of each of these parts can be ensured well, vibration and the like are prevented from being generated during the operation of the wheel supporting rolling bearing unit, and the rolling elements 5
And the rolling fatigue life of the second inner raceway 9 can be ensured. In the illustrated example, the first inner raceway 7 is formed directly on the outer peripheral surface of the intermediate portion of the shaft member 2. However, the first inner raceway 7 is formed on an inner race separate from the shaft member 2. Alternatively, the inner ring may be externally fitted and fixed to the shaft member 2. Next, FIG. 3 shows a second example of the embodiment of the present invention incorporating the above-mentioned components.
In the case of this example, the spacer ring 18 is externally fitted to a portion of the inner end of the shaft member 2 that protrudes inward from the end surface 24 of the inner race 3 that is externally fitted to the shaft member 2. An inner peripheral surface of the inner half portion of the spacer ring 18 is formed with a conical concave inclined surface 19 whose inner diameter increases toward the inner end opening. Then, the cylindrical portion 21 existing inside the spacer ring 18 at the inner end of the shaft member 2 is radially outwardly swaged and widened, thereby pressing the spacer ring 18 toward the end surface 24 of the inner ring 3. The inner ring 3 is fixedly connected to the shaft member 2.
Further, the extension position of the line of action of load applied to the inner ring 3 from the rolling elements 5 provided between the second inner raceway 9 and the second outer raceway 14 (which coincides with the chain line α representing the contact angle) is as described above. Slope 1
It is located closer to the axial center of the step portion 8 than to the portion 9 where the outer diameter does not change. In the case of this embodiment, such a spacer ring 18
Is provided, the elastic deformation of the inner ring 3 in the diametric direction can be reliably prevented even when the crimping strength when the cylindrical portion 21 is crimped and widened is sufficiently increased. That is,
In the case of the present example, the spacer ring 18 externally fitted to the shaft member 2 receives a force directed outward in the diametrical direction, which is applied when the cylindrical portion 21 is swaged and spread. Therefore, the diameter of the inner ring 3 changes less with the work of caulking and expanding the cylindrical portion 21 than in the case of the first example described above (almost no change). In addition, temporarily, the spacer ring 1
Even if the dimensional accuracy and the shape accuracy of No. 8 deteriorate, the performance of the rolling bearing unit for supporting wheels is not affected at all. Further, in the case of this example, since the extension position of the line of action of the load is regulated, this load is prevented from acting on the portion where the cylindrical portion 21 is swaged and the endurance of the swaged fixed portion is prevented. Nature can be secured. The point that the spacer ring 18 is provided,
The configuration and operation other than the point that the extension position of the action line is restricted are the same as those of the first example described above. Next, FIG. 4 shows a third embodiment of the present invention incorporating the above-mentioned components. In the case of the present example, the outer diameter of a portion where the inclined surface 19 is formed at the inner end of the inner ring 3a fitted to the inner end of the shaft member 2 is smaller than the outer diameter of the shoulder 23 of the inner ring 3a. do it,
The inner ring cylindrical portion 26 is provided. In the case of such a present example, when the cylindrical portion 21 formed at the inner end portion of the shaft member 2 is swaged diametrically outward toward the inclined surface 19 to fix the inner ring 3 to the shaft member 2, , The inner ring cylindrical portion 26 receives most of the stress caused by swaging. Therefore, the deformation of the thin inner ring cylindrical portion 26 is larger than that of the shoulder 23, but the deformation of the shoulder 23 of the inner ring 3a and the second inner raceway 9 can be reduced. As a result, the rotational accuracy of the wheel supporting rolling bearing unit can be maintained in a sufficiently favorable state. In the case of this example, the second inner raceway 9
And the shoulder 23 of the inner race 3a.
The distance M in the axial direction of the shaft member 2 with respect to the end surface 24a is 0.75 times or more (M ≧ 0.75D) the outer diameter D of each of the rolling elements 5 and 5. Also in the case of this example, the extension position of the line of action of the load is regulated to ensure the durability of the caulking fixed portion. Other configurations and operations are the same as those of the first example described above. Next, FIG. 5 shows a fourth embodiment of the present invention incorporating the above-mentioned components. In the case of the first to third examples described above, the outer ring 4 is a stationary wheel that does not rotate, and the shaft member 2 is rotated. On the other hand, in the case of the present example, the shaft member 2 is connected to the suspension device. The outer wheel 4 is a rotating wheel that rotates together with the wheel without being supported and rotated. The configuration and operation other than that the rotation side and the stationary side are reversed are the same as in the case of the above-described first example. Next, FIG. 6 shows a fifth embodiment of the present invention incorporating the above-mentioned components.
In the case of this example, the outer diameter of the portion of the inner end of the shaft member 2 protruding from the fitting portion of the inner race 3 is made smaller than the outer diameter of this fitting portion. That is, the base member outer peripheral surface of the cylindrical portion 21 formed at the inner end of the shaft member 2 is slightly closer to the second inner raceway 9 than the inclined surface 19 formed at the inner end opening of the inner race 3. A step 27 having a slight step H of about 0.02 to 1 mm is formed in the bent portion. Then, a portion of the cylindrical portion 21 having a reduced outer diameter is swaged outward in a diametrical direction to suppress the inclined surface 19. When the cylindrical portion 21 is swaged outward in the diametrical direction in this way, the step portion 27 serves as a starting point of a portion that is bent with the swaging operation. For this reason, an excessive force is less likely to be applied to the cylindrical portion 21 with the swaging operation, and damage such as a crack is less likely to occur at the swaging portion. Other configurations and operations are the same as those of the first example described above. When the structure of this example is applied to the above-described fourth example, the inward and outward directions with respect to the axial direction are reversed. Next, FIG. 7 shows a sixth embodiment of the present invention incorporating the above-mentioned components.
In the case of this example, at a part of the outer peripheral surface of the inner end portion of the shaft member 2,
A groove 28 having a depth K of about 0.1 to 2 mm is formed in a portion of the inclined surface 19 formed at the inner end of the inner ring 3 facing the small-diameter end, over the entire outer peripheral surface. Has formed. A cylindrical portion 21 formed at the inner end of the shaft member 2
The portion closer to the inner end than the concave groove 28 is swaged radially outward to suppress the inclined surface 19. As described above, when the cylindrical portion 21 is swaged outward in the diameter direction, the concave groove 28 serves as a starting point of a portion that is bent in accordance with the swaging operation. For this reason, an excessive force is less likely to be applied to the cylindrical portion 21 with the swaging operation, and damage such as a crack is less likely to occur at the swaging portion. Other configurations and operations are the same as those of the first example described above. When the structure of this example is applied to the above-described fourth example, the inward and outward directions with respect to the axial direction are reversed. The rolling bearing unit for supporting a wheel according to the present invention is constructed and operates as described above, so that the diameter of the inner ring is prevented from changing and the inner ring and the inner ring are fixed. It is possible to reduce the possibility that the caulked portion is damaged due to the fixing operation of the inner ring. Further, the preload can be maintained at an appropriate value, and the cost can be reduced by reducing the number of parts, the number of parts processing, and the number of assembly steps.

【図面の簡単な説明】【図１】本発明の実施の形態の第１例を示す半部断面
図。【図２】シャフト部材の内端部に形成した円筒部をかし
め広げる状態を示す、要部拡大断面図。【図３】本発明の実施の形態の第２例を示す半部断面
図。【図４】同第３例を示す半部断面図。【図５】同第４例を示す半部断面図。【図６】同第５例を示す要部拡大断面図。【図７】同第６例を示す要部拡大断面図。【図８】従来構造の第１例を示す半部断面図。【図９】同第２例を示す半部断面図。【符号の説明】１車輪支持用転がり軸受ユニット２シャフト部材３、３ａ内輪４外輪５転動体６第二のフランジ７第一の内輪軌道８段部９第二の内輪軌道１０雄ねじ部１１ナット１２段差面１３第一の外輪軌道１４第二の外輪軌道１５第一のフランジ１６かしめ部１７係止凹部１８スぺーサリング１９傾斜面２０凹部２１円筒部２２シールリング２３肩部２４、２４ａ端面２５プレス型２６内輪円筒部２７段差部２８凹溝２９蓋体BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a half sectional view showing a first example of an embodiment of the present invention. FIG. 2 is an enlarged sectional view of a main part, showing a state where a cylindrical portion formed at an inner end of a shaft member is swaged and spread; FIG. 3 is a half sectional view showing a second example of the embodiment of the present invention. FIG. 4 is a half sectional view showing the third example. FIG. 5 is a half sectional view showing the fourth example. FIG. 6 is an enlarged sectional view of a main part showing the fifth example. FIG. 7 is an enlarged sectional view of a main part showing the sixth example. FIG. 8 is a half sectional view showing a first example of a conventional structure. FIG. 9 is a half sectional view showing the second example. DESCRIPTION OF SYMBOLS 1 Wheel supporting rolling bearing unit 2 Shaft member 3, 3 a Inner ring 4 Outer ring 5 Rolling element 6 Second flange 7 First inner ring raceway 8 Step 9 Second inner raceway 10 Male thread 11 Nut 12 Step surface 13 First outer raceway 14 Second outer raceway 15 First flange 16 Caulking portion 17 Locking recess 18 Spacer ring 19 Inclined surface 20 Depression 21 Cylindrical portion 22 Seal ring 23 Shoulder portions 24, 24a End surface 25 Press Mold 26 Inner ring cylindrical part 27 Step part 28 Groove 29 Cover

─────────────────────────────────────────────────────
【手続補正書】【提出日】平成１４年５月２７日（２００２．５．２
７）【手続補正１】【補正対象書類名】明細書【補正対象項目名】全文【補正方法】変更【補正内容】【書類名】明細書【発明の名称】車輪支持用転がり軸受ユニット【特許請求の範囲】【請求項１】外周面に第一のフランジを、内周面に複
列の外輪軌道を、それぞれ設けた外輪と、端部外周面に
第二のフランジを設けたシャフト部材と、外周面に内輪
軌道を有し上記シャフト部材に外嵌した、少なくとも１
個の内輪と、この内輪を含んで上記シャフト部材と共に
回転する部分の外周面に設けた第一、第二の内輪軌道と
上記複列の外輪軌道との間に、それぞれ複数個ずつ設け
た転動体とを備え、上記シャフト部材の端部に形成した
円筒部の一部で上記内輪よりも突出した部分を直径方向
外方にかしめ広げ、このかしめ広げた部分で上記内輪を
抑え付ける事により、上記内輪を上記シャフト部材に固
定する車輪支持用転がり軸受ユニットに於いて、このシ
ャフト部材の端部に段差部を、上記円筒部の基端側の外
径よりも先端側の外径が小さくなる状態で形成し、この
円筒部のうちの外径の小さくなった部分を直径方向外方
にかしめ広げた事を特徴とする車輪支持用転がり軸受ユ
ニット。【請求項２】段差部が、内輪の内端開口部に形成した
傾斜面よりも、円筒部寄りに存在する第二の内輪軌道に
寄った部分に存在する、請求項１に記載した車輪支持用
転がり軸受ユニット。【請求項３】段差部の段差が０．０２〜１mmである、
請求項１〜２の何れかに記載した車輪支持用転がり軸受
ユニット。【発明の詳細な説明】【０００１】【発明の属する技術分野】この発明に係る車輪支持用転
がり軸受ユニットは、自動車の車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】自動車の車輪は、車輪支持用転がり軸受
ユニットにより懸架装置に支持する。この様な場合に使
用する車輪支持用転がり軸受ユニットとして、従来から
例えば、特開昭６３−１０６４２６号公報、同６３−１
８４５０１号公報、同６２−２１４８８９号公報、特開
平３−３１００１号公報、米国特許第４５３７２７０号
明細書、同４９５８９４４号明細書、同５２２６７３８
号明細書、同５４９０７３２号明細書等に記載されたも
のが知られている。又、図８は、従来から広く実施され
ている車輪支持用転がり軸受ユニットの１例を示してい
る。この車輪支持用転がり軸受ユニット１は、シャフト
部材２と、内輪３と、外輪４と、複数個の転動体５、５
とを備える。このうちのシャフト部材２の外周面の外端
部（外とは、自動車への組み付け状態で幅方向外寄りと
なる側を言い、各図の左側となる。反対に幅方向中央寄
りとなる側を内と言い、各図の右側となる。）で上記外
輪４から突出した部分には、車輪を支持する為の第二の
フランジ６を形成している。又、このシャフト部材２の
中間部には第一の内輪軌道７を、同じく内端部には外径
寸法が小さくなった段部８を、それぞれ形成している。【０００３】そして、この段部８に、その外周面に第二
の内輪軌道９を形成した上記内輪３を外嵌している。上
記シャフト部材２の内端部には雄ねじ部１０を形成し、
この雄ねじ部１０の先端部を、上記内輪３の内端面より
も内方に突出させている。そして、この雄ねじ部１０に
螺合したナット１１と上記段部８の段差面１２との間で
上記内輪３を挟持する事により、この内輪３を上記シャ
フト部材２の所定位置に結合固定している。上記雄ねじ
部１０の先端部外周面には係止凹部１７を形成してい
る。そして、上記ナット１１を所定のトルクで緊締した
後、このナット１１の一部で上記係止凹部１７に整合す
る部分を直径方向内方にかしめ付ける事により、このナ
ット１１の緩み止めを図っている。尚、上記シャフト部
材２に１対の内輪を外嵌し、これら１対の内輪の外周面
に、第一、第二の内輪軌道７、９を設ける構造も、従来
から知られている。【０００４】又、上記外輪４の内周面には、上記第一の
内輪軌道７と対向する第一の外輪軌道１３及び上記第二
の内輪軌道９に対向する第二の外輪軌道１４を形成して
いる。そして、これら第一、第二の内輪軌道７、９と第
一、第二の外輪軌道１３、１４との間に上記転動体５、
５を、それぞれ複数個ずつ設けている。これら各転動体
５、５の設置空間の外端開口はシールリング２２によ
り、内端開口は蓋体２９により、それぞれ塞いでいる。
尚、図示の例では、転動体５、５として玉を使用してい
るが、重量の嵩む自動車用の車輪支持用転がり軸受ユニ
ットの場合には、これら転動体としてテーパころを使用
する場合もある。【０００５】上述の様な車輪支持用転がり軸受ユニット
１を自動車に組み付けるには、上記外輪４を、その外周
面の一部に形成した第一のフランジ１５により懸架装置
に固定し、上記第二のフランジ６に車輪を固定する。こ
の結果、この車輪が懸架装置に対して回転自在に支持さ
れる。【０００６】又、前記米国特許第５２２６７３８号明細
書には、図９に示す様な構造の車輪支持用転がり軸受ユ
ニット１が記載されている。この従来構造の第２例の場
合には、シャフト部材２の内端部に形成した円筒部の一
部で内輪３の内端面よりも内方に突出した部分を直径方
向外方に折り曲げる事により、かしめ部１６を形成して
いる。そして、このかしめ部１６と段部８の段差面１２
との間で、上記内輪３を挟持している。【０００７】【発明が解決しようとする課題】図８に示した従来構造
の第１例の場合には、雄ねじ部１０の先端部に係止凹部
１７を形成する作業、及びナット１１の一部を直径方向
内方にかしめ付ける作業が必要になる。この為、車輪支
持用転がり軸受ユニット１の部品製造作業及び組立作業
が面倒になり、コストが嵩む。【０００８】又、図９に示した第２例の構造の場合、シ
ャフト部材２に対して内輪３を結合固定する為のかしめ
部１６の形成時に、このかしめ部１６が隣接する内輪３
の内周面に、直径方向外方に向いた力が加わる。この
為、この内輪３の直径が僅かとは言え変化する。そし
て、この変化量が大きくなると、この内輪３に亀裂等の
損傷が発生する可能性が生じるだけでなく、転動体５、
５に付与した予圧を適正値に維持する作業が面倒にな
り、上記内輪３を含む車輪支持用転がり軸受ユニット１
の耐久性を確保する事が難しくなる可能性がある。特
に、上記シャフト部材２に対して上記内輪３が回転する
事を防止すべく、上記かしめ部１６のかしめ強度を十分
に確保しようとした場合には、上記変形量が大きくなり
易く、上記内輪３の耐久性確保が難しくなる。【０００９】この様な事情に鑑みて特願平８−３６８０
０号には、内輪の端面とかしめ部との間にスペーサリン
グを設け、かしめ部の形成作業に伴う、直径方向外方に
向いた力をこのスペーサリングにより受ける構造が開示
されている。この先発明に係る構造によれば、かしめ部
の形成作業に伴って発生する、直径方向外方に向いた力
の大部分を上記スペーサリングが受ける。従って、上記
内輪にはこの直径方向外方に向いた力が殆ど伝わらず、
この内輪の損傷防止を図れる。但し、この様なスペーサ
リングを設けた構造の場合でも、上記かしめ部自体、円
筒部からの加工量が多く、かしめ作業に伴う変形に基づ
いて亀裂等が発生し易く、耐久性の確保が難しい。【００１０】本発明の車輪支持用転がり軸受ユニット
は、この様な事情に鑑みて、かしめ部に亀裂等の損傷が
発生しにくくすると共に、シャフト部材に対し内輪を固
定するナットの緩み止めを図る為の係止凹部の形成作業
やナットのかしめ付け作業を省略する事により、コスト
低減を図る事を目的に発明したものである。【００１１】【課題を解決するための手段】本発明の車輪支持用転が
り軸受ユニットは何れも、従来の、或は先発明の車輪支
持用転がり軸受ユニットと同様に、外周面に第一のフラ
ンジを、内周面に複列の外輪軌道を、それぞれ設けた外
輪と、端部外周面に第二のフランジを設けたシャフト部
材と、外周面に内輪軌道を有し上記シャフト部材に外嵌
した、少なくとも１個の内輪と、この内輪を含んで上記
シャフト部材と共に回転する部分の外周面に設けた第
一、第二の内輪軌道と上記複列の外輪軌道との間に、そ
れぞれ複数個ずつ設けた転動体とを備える。そして、上
記シャフト部材の端部に形成した円筒部の一部で上記内
輪よりも突出した部分を直径方向外方にかしめ広げ、こ
のかしめ広げた部分により上記内輪を抑え付ける事によ
り、上記内輪を上記シャフト部材に固定している。特
に、本発明の車輪支持用転がり軸受ユニットに於いて
は、このシャフト部材の端部に段差部を、上記円筒部の
基端側の外径よりも先端側の外径が小さくなる状態で形
成している。そして、この円筒部のうちの外径の小さく
なった部分を直径方向外方にかしめ広げている。尚、好
ましくは、上記内輪の開口周縁部で上記円筒部をかしめ
広げた部分の外周面が押し付けられる部分を、開口端に
向う程径が大きくなる、円錐凹面状の傾斜面とする。【００１２】更に好ましくは、次の〜の構成要件
を、それぞれ単独で、或は〜のうちから選択される
複数の構成要件を、上記必須要件に組み合わせて実施す
る。上記円筒部を構成すべく、上記シャフト部材の端部
に形成する円形の凹部の先端の、このシャフト部材の軸
方向に関する位置は、上記円筒部寄りに存在する第二の
内輪軌道に当接する転動体の中心の上記シャフト部材の
軸方向に関する位置よりも、上記シャフト部材の端部側
に位置する。上記第二の内輪軌道に当接する転動体の中心と、上
記内輪の端面若しくはこの内輪の肩部の端面との、上記
シャフト部材の軸方向に関する距離は、上記転動体の外
径の０．７５倍以上である。上記内輪の端部で上記傾斜面を形成した部分の外径
を、この内輪の肩部の外径よりも小さくする。上記シャフト部材の先端部外周面の一部で、上記傾
斜面の小径側端部に対向する部分に凹溝を、上記外周面
の全周に亙って形成し、上記シャフト部材の端部に形成
した円筒部のうちの凹溝よりも先端寄り部分を、直径方
向外方にかしめ広げる。転動体から内輪に加わる荷重の作用線の延長位置
を、上記傾斜面よりもシャフト部材の軸方向中央寄り
で、このシャフト部材の外径が変化しない部分に存在さ
せる。【００１３】【作用】上述の様に構成される本発明の車輪支持用転が
り軸受ユニットにより、懸架装置に対して車輪を回転自
在に支持する作用は、従来の車輪支持用転がり軸受ユニ
ットと同様である。特に、本発明の車輪支持用転がり軸
受ユニットの場合には、シャフト部材の端部に形成した
円筒部をかしめ広げる部分を、段差部を介して外径が小
さくなった部分としている為、かしめ広げ作業に伴って
円筒部に無理な力が加わりにくくなって、かしめ広げ部
分に亀裂等の損傷が発生しにくくなる。【００１４】【発明の実施の形態】図１〜２は、前記の構成要件
を組み込んだ、本発明を適用可能な構造の第１例を示し
ている。尚、本例の特徴は、シャフト部材２に対して内
輪３を固定する部分の構造にある。その他の部分の構造
及び作用に就いては、前述の図８に示した従来構造と同
様であるから、重複する説明を省略若しくは簡略にし、
以下、本発明の特徴部分を中心に説明する。【００１５】シャフト部材２の内端部に形成した段部８
の中間部内端寄り部分で、この段部８に外嵌した内輪３
の内端部内周面に、内端開口に向かう程内径が大きくな
る、円錐凹面状の傾斜面１９を形成している。この傾斜
面１９が上記シャフト部材２の中心軸に対し傾斜してい
る傾斜角度θは、２０〜６０度程度とする。又、上記シ
ャフト部材２の内端面には円形の凹部２０を形成する事
により、このシャフト部材２の内端部に円筒部２１を形
成している。本例の場合にこの円筒部２１は、上記シャ
フト部材２の内端部で、ほぼ上記内輪３の肩部２３の内
側部分に存在する。【００１６】上述の様な傾斜面１９を形成した内輪３
を、上記シャフト部材２の内端部に設けた円筒部２１を
かしめ広げる事によりこのシャフト部材２に固定し、本
発明を適用可能な構造である、車輪支持用転がり軸受ユ
ニットとする際には、前記図９に示した従来構造の場合
に比べて、かしめ部分の変形量が少なくて済む。即ち、
上記従来構造の場合にはかしめ部１６を形成する為、シ
ャフト部材２の内端部に形成した円筒部を直径方向外方
に向け、９０度折り曲げるのに対して、本発明の車輪支
持用転がり軸受ユニットを構成すべく、上記円筒部２１
をかしめ広げる際には、この円筒部２１を上記傾斜角度
θ（＝２０〜６０度）だけ変形させれば良い。この為、
このかしめ部分に発生する歪みを小さく抑えて、このか
しめ部に割れ等の損傷が発生するのを抑える事ができ
る。又、上記変形量を少なく抑える為、このかしめ部を
形成する事に基づき、上記円筒部２１の周囲に存在する
部材である上記内輪３に、この内輪３の直径方向外方に
加わる力を低減できて、この内輪３の損傷防止を図れ
る。【００１７】尚、上記円筒部２１を直径方向外方にかし
め広げる作業は、鍛造加工、或は揺動プレス加工により
行なう。何れの加工法を採用する場合でも、図２に示す
様に、上記円筒部２１の内径側にプレス型２５を押し込
み、上記円筒部２１を直径方向外方にかしめ広げる。特
に、かしめ作業に揺動プレス加工を採用すれば、成形時
の荷重を小さくして、軸受内部への影響をなくし、成形
後の予圧管理を適正にできると言った利点がある。又、
上記円筒部２１の奥端縁（この円筒部２１の内径が変化
しない部分の奥端）と上記内輪３の端面２４との距離Ｌ
は、車輪支持用転がり軸受ユニットの大きさ等の応じて
設計的に定めるが、一般的な乗用車用の車輪支持用転が
り軸受ユニットの場合で、５〜１５mm程度とするのが好
ましい。【００１８】又、上記円筒部２１を構成すべく、上記シ
ャフト部材２の端部に形成する円形の凹部２０の先端位
置は、複列に配置した転動体５、５のうち、内側の列を
構成する転動体５の中心よりも内側に位置させている。
即ち、図１に点Ｘで示した、上記凹部２０の先端の、上
記シャフト部材２の軸方向に関する位置は、第二の内輪
軌道である、上記内輪３の外周面に設けた第二の内輪軌
道９に当接する転動体５の中心の、上記シャフト部材２
の軸方向に関する位置よりも、上記シャフト部材２の内
端部側に位置させている。従って、車輪支持用転がり軸
受ユニットを構成するシャフト部材２と外輪４との間に
ラジアル荷重が加わり、上記転動体５から上記第二の内
輪軌道９にラジアル荷重が加わった場合でも、上記シャ
フト部材２の一部でこのラジアル荷重を受ける部分が充
実体である為、このシャフト部材２の耐久性を十分に確
保できる。【００１９】更に、上記第二の内輪軌道９に当接する転
動体５の中心と、上記内輪３の端面２４との、上記シャ
フト部材２の軸方向に関する距離Ｍを、上記各転動体
５、５の外径Ｄの０．７５倍以上（Ｍ≧０．７５Ｄ）と
している。この様に、転動体５の中心と端面２４との距
離Ｍを確保している為、上記内輪３の肩部２３や第二の
内輪軌道９部分の寸法精度や形状精度が悪化する事を防
止して、車輪支持用転がり軸受ユニットの機能を確保で
きる。即ち、これら各部分の寸法精度や形状精度を良好
に確保できるので、車輪支持用転がり軸受ユニットの運
転時に振動等が発生するのを防止すると共に、転動体５
の転動面や第二の内輪軌道９の転がり疲れ寿命等を確保
できる。尚、図示の例では、第一の内輪軌道７をシャフ
ト部材２の中間部外周面に直接形成しているが、この第
一の内輪軌道７は、シャフト部材２と別体の内輪に形成
し、この内輪をこのシャフト部材２に外嵌固定しても良
い。【００２０】次に、図３は、前記の構成要件を組
み込んだ、本発明を適用可能な構造の第２例を示してい
る。本例の場合には、シャフト部材２の内端部で、この
シャフト部材２に外嵌した内輪３の端面２４よりも内方
に突出した部分に、スペーサリング１８を外嵌してい
る。このスペーサリング１８の内半部内周面には、内端
開口に向かう程内径が大きくなる、円錐凹面状の傾斜面
１９を形成している。そして、上記シャフト部材２の内
端部で上記スペーサリング１８の内側に存在する円筒部
２１を直径方向外方にかしめ広げる事により、上記スペ
ーサリング１８を上記内輪３の端面２４に向け抑え付け
て、この内輪３を上記シャフト部材２に結合固定してい
る。又、第二の内輪軌道９と第二の外輪軌道１４との間
に設けた転動体５から内輪３に加わる荷重の作用線（接
触角を表す鎖線αと一致する）の延長位置は、上記傾斜
面１９よりも段部８の軸方向中央寄りで、外径が変化し
ない部分に存在する。【００２１】本例の場合、この様なスペーサリング１８
を設ける事により、上記円筒部２１をかしめ広げる際の
かしめ強度を十分に大きくした場合でも、上記内輪３が
直径方向に弾性変形する事を確実に防止できる。即ち、
本例の場合には、上記円筒部２１をかしめ広げる際に加
わる、直径方向外方に向いた力は、シャフト部材２に外
嵌したスペーサリング１８が受ける。従って、上記円筒
部２１をかしめ広げる作業に伴って、上記内輪３の直径
が変化する事が、前述した第１例の場合よりも少なくな
る（殆ど変化しなくなる）。尚、仮にスペーサリング１
８の寸法精度、及び形状精度が悪化しても、車輪支持用
転がり軸受ユニットの性能には何らの悪影響も及ぼさな
い。又、本例の場合には、上記荷重の作用線の延長位置
を規制している為、この荷重が上記円筒部２１をかしめ
広げた部分に作用する事を防止して、かしめ固定部分の
耐久性を確保できる。スペーサリング１８を設けた点、
並びに作用線の延長位置を規制した点以外の構成及び作
用は、前述した第１例の場合と同様である。【００２２】次に、図４は、前記の構成要件を
組み込んだ、本発明を適用可能な構造の第３例を示して
いる。本例の場合には、シャフト部材２の内端部に外嵌
した内輪３ａの内端部で傾斜面１９を形成した部分の外
径を、この内輪３ａの肩部２３の外径よりも小さくし
て、内輪円筒部２６としている。この様な本例の場合、
上記シャフト部材２の内端部に形成した円筒部２１を、
上記傾斜面１９に向けて直径方向外方にかしめ広げ、上
記内輪３をシャフト部材２に固定する際には、上記内輪
円筒部２６が、かしめ広げに伴う応力の大部分を受け
る。従って、肩部２３に比較して薄肉の内輪円筒部２６
の変形量は多くなるが、上記内輪３ａの肩部２３及び第
二の内輪軌道９の変形量を小さくできる。この結果、車
輪支持用転がり軸受ユニットの回転精度を十分良好な状
態に維持できる。尚、本例の場合には、上記第二の内輪
軌道９に当接する転動体５の中心と、上記内輪３ａの肩
部２３の端面２４ａとの、上記シャフト部材２の軸方向
に関する距離Ｍを、上記各転動体５、５の外径Ｄの０．
７５倍以上（Ｍ≧０．７５Ｄ）としている。又、本例の
場合も、荷重の作用線の延長位置を規制して、かしめ固
定部分の耐久性確保を図っている。その他の構成及び作
用は、前述した第１例の場合と同様である。【００２３】次に、図５は、前記の構成要件を組み
込んだ、本発明を適用可能な構造の第４例を示してい
る。上述した第１〜３例の場合には、外輪４を回転しな
い静止輪とし、シャフト部材２を回転させる構造であっ
たのに対して、本例の場合には、シャフト部材２を懸架
装置に支持して回転させず、外輪４を車輪と共に回転す
る回転輪としている。回転側と静止側とが逆になった以
外の構成及び作用は、前述した第１例の場合と同様であ
る。【００２４】次に、図６は、前記の構成要件を組み
込んだ、本発明の実施の形態の１例を示している。本例
の場合、シャフト部材２の内端部で内輪３の嵌合部より
も突出した部分の外径を、この嵌合部の外径よりも小さ
くしている。即ち、上記シャフト部材２の内端部に形成
した円筒部２１の基端部外周面で、この内輪３の内端開
口部に形成した傾斜面１９よりも少しだけ第二の内輪軌
道９に寄った部分に、０．０２〜１mm程度の僅かな段差
Ｈを有する段差部２７を形成している。そして、上記円
筒部２１のうちの外径の小さくなった部分を、直径方向
外方にかしめ広げ、上記傾斜面１９を抑え付ける様にし
ている。この様に円筒部２１を直径方向外方にかしめ広
げる際には、上記段差部２７がかしめ広げ作業に伴って
折れ曲がる部分の起点となる。この為、かしめ広げ作業
に伴って上記円筒部２１に無理な力が加わりにくくなっ
て、かしめ広げ部分に亀裂等の損傷が発生しにくくな
る。その他の構成及び作用は、前述した第１例の場合と
同様である。尚、本例の構造を上述した、本発明を適用
可能な構造の第４例に適用する場合には、軸方向に関す
る内外方向が逆になる。【００２５】次に、図７は、前記の構成要件を組
み込んだ、本発明を適用可能な構造の第５例を示してい
る。本例の場合、シャフト部材２の内端部外周面の一部
で、内輪３の内端部に形成した傾斜面１９の小径側端部
に対向する部分に、０．１〜２mm程度の深さＫを有する
凹溝２８を、上記外周面の全周に亙って形成している。
そして、上記シャフト部材２の内端部に形成した円筒部
２１のうちの上記凹溝２８よりも内端寄り部分を、直径
方向外方にかしめ広げ、上記傾斜面１９を抑え付ける様
にしている。この様に円筒部２１を直径方向外方にかし
め広げる際には、上記凹溝２８がかしめ広げ作業に伴っ
て折れ曲がる部分の起点となる。この為、かしめ広げ作
業に伴って上記円筒部２１に無理な力が加わりにくくな
って、かしめ広げ部分に亀裂等の損傷が発生しにくくな
る。その他の構成及び作用は、前述した第１例の場合と
同様である。尚、本例の構造を上述した、本発明を適用
可能な構造の第４例に適用する場合にも、軸方向に関す
る内外方向が逆になる。【００２６】【発明の効果】本発明の車輪支持用転がり軸受ユニット
は、以上に述べた通り構成され作用するので、内輪の直
径が変化する事を防止して、この内輪及びこの内輪を固
定する為のかしめ広げ部分が、上記内輪の固定作業に基
づいて損傷する可能性を低くできる。【図面の簡単な説明】【図１】本発明を適用可能な構造の第１例を示す半部断
面図。【図２】シャフト部材の内端部に形成した円筒部をかし
め広げる状態を示す、要部拡大断面図。【図３】本発明を適用可能な構造の第２例を示す半部断
面図。【図４】同第３例を示す半部断面図。【図５】同第４例を示す半部断面図。【図６】本発明の実施の形態の１例を示す要部拡大断面
図。【図７】本発明を適用可能な構造の第５例を示す要部拡
大断面図。【図８】従来構造の第１例を示す半部断面図。【図９】同第２例を示す半部断面図。【符号の説明】１車輪支持用転がり軸受ユニット２シャフト部材３、３ａ内輪４外輪５転動体６第二のフランジ７第一の内輪軌道８段部９第二の内輪軌道１０雄ねじ部１１ナット１２段差面１３第一の外輪軌道１４第二の外輪軌道１５第一のフランジ１６かしめ部１７係止凹部１８スぺーサリング１９傾斜面２０凹部２１円筒部２２シールリング２３肩部２４、２４ａ端面２５プレス型２６内輪円筒部２７段差部２８凹溝２９蓋体【手続補正２】【補正対象書類名】図面【補正対象項目名】図５【補正方法】変更【補正内容】【図５】    ────────────────────────────────────────────────── ───
[Procedure amendment] [Submission date] May 27, 2002 (2005.2.
7) [Procedure amendment 1] [Document name to be amended] Statement [Correction target item name] Full text [Correction method] Change [Correction contents] [Document Name] Statement [Title of the Invention] Rolling bearing unit for supporting wheels [Claims] A first flange is provided on an outer peripheral surface, and a first flange is provided on an inner peripheral surface.
ColumnOuter ring trackOn the outer ring and the outer peripheral surface of the end
A shaft member provided with a second flange and an inner ring on an outer peripheral surface
At least one having a track and externally fitted to the shaft member;
With the inner ring and the shaft member including the inner ring
First and second inner ring raceways provided on the outer peripheral surface of the rotating part
Multiple pieces are provided between each of the above-mentioned double row outer ring raceways.
The rolling elementShaft memberFormed at the end of
The part of the cylindrical part that protrudes from the inner ring is diametrically
Spread outward and this swaged partWith the above inner ring
RestrainBy the above, the inner ringShaft memberSolid
The rolling bearing unit for wheel supportThis
At the end of the shaft member, a stepped portion is provided outside the base end of the cylindrical portion.
The outer diameter on the tip side is smaller than the diameter.
The part of the cylindrical part with the smaller outer diameter is diametrically outward.
Spread outRolling bearing unit for wheel support
knit. [Claim 2A step is formed at the inner end opening of the inner ring.
On the second inner ring raceway located closer to the cylinder than the slope
2. The wheel support according to claim 1, wherein the wheel support is located at a shifted portion.
Rolling bearing unit. [Claim 3The step of the step is 0.02 to 1 mm,
3. The rolling bearing for supporting wheels according to claim 1.
unit. DETAILED DESCRIPTION OF THE INVENTION [0001] BACKGROUND OF THE INVENTION 1. Field of the Invention
The ball bearing unit connects the wheels of the vehicle to the suspension
Used for rotatably supporting. [0002] 2. Description of the Related Art Wheels of automobiles include rolling bearings for supporting wheels.
The unit supports the suspension. Use in such cases
Rolling bearing unit for wheel support
For example, JP-A-63-106426 and JP-A-63-1
Nos. 84501 and 62-214889,
JP-A-3-31001, U.S. Pat. No. 4,537,270
Specification, Japanese Patent No. 4995844, Japanese Patent No. 5226738
No. 5,490,732, etc.
It is known. FIG. 8 shows a conventional and widely practiced implementation.
Shows an example of a rolling bearing unit for supporting a wheel.
You. The rolling bearing unit 1 for supporting a wheel includes a shaft
A member 2, an inner ring 3, an outer ring 4, and a plurality of rolling elements 5, 5
And Outer end of the outer peripheral surface of the shaft member 2
Part (outside means that the outer
The left side of each figure. Conversely, centered in the width direction
The inner side is called the inner side, and is the right side of each figure. ) Outside the above
The part protruding from the wheel 4 has a second
A flange 6 is formed. Also, the shaft member 2
The first inner ring raceway 7 is located at the middle part, and the outer diameter is also located at the inner end.
Steps 8 having reduced dimensions are respectively formed. [0003] Then, a second portion is provided on the outer peripheral surface of the step portion 8.
The inner ring 3 having the inner ring raceway 9 is externally fitted. Up
A male screw portion 10 is formed at the inner end of the shaft member 2,
The tip of the male thread 10 is moved from the inner end face of the inner ring 3
Also protrude inward. And in this male screw part 10
Between the screwed nut 11 and the step surface 12 of the step 8
By holding the inner ring 3, the inner ring 3 is
It is fixedly connected to a predetermined position of the shaft member 2. Male screw above
A locking recess 17 is formed on the outer peripheral surface of the tip of the portion 10.
You. Then, the nut 11 was tightened with a predetermined torque.
Then, a part of the nut 11 is aligned with the locking recess 17.
This part is crimped inward in the diameter direction.
In this way, the slot 11 is prevented from loosening. In addition, the shaft part
A pair of inner races are externally fitted to the material 2 and the outer peripheral surfaces of these pair of inner races
In addition, the structure in which the first and second inner raceways 7 and 9 are provided
Known from. On the inner peripheral surface of the outer ring 4, the first
A first outer raceway 13 facing the inner raceway 7 and the second outer raceway 13;
Forming a second outer raceway 14 opposite to the inner raceway 9
I have. And these first and second inner raceways 7, 9 and
The rolling elements 5 between the first and second outer raceways 13 and 14;
5 are provided in plurality. Each of these rolling elements
The outer end openings of the installation spaces 5 and 5 are formed by seal rings 22.
The inner end openings are closed by lids 29, respectively.
In the illustrated example, balls are used as the rolling elements 5 and 5.
Rolling bearing unit for wheel support
In the case of nuts, tapered rollers are used as these rolling elements
In some cases. [0005] Rolling bearing unit for wheel support as described above
In order to assemble 1 into an automobile, the outer ring 4 is connected to the outer periphery of the outer ring 4.
Suspension device by first flange 15 formed on part of surface
, And the wheel is fixed to the second flange 6. This
As a result, this wheel is rotatably supported with respect to the suspension.
It is. The above-mentioned US Pat. No. 5,226,738 is disclosed.
In the written description, a rolling bearing unit for wheel support having a structure as shown in FIG.
Knit 1 is described. The field of the second example of this conventional structure
In this case, one of the cylindrical portions formed at the inner end of the shaft member 2
The part protruding inward from the inner end face of the inner ring 3
By bending outwards, the caulked portion 16 is formed
I have. Then, the caulked portion 16 and the step surface 12 of the step portion 8 are formed.
, The inner ring 3 is sandwiched. [0007] The conventional structure shown in FIG.
In the case of the first example, the locking recess is provided at the tip of the male screw portion 10.
17 and part of the nut 11 in the diametric direction
Work to crimp inward is required. Because of this,
Parts manufacturing work and assembly work for the rolling bearing unit 1
Is troublesome, and the cost increases. In the case of the structure of the second example shown in FIG.
Caulking for connecting and fixing the inner ring 3 to the shaft member 2
When the portion 16 is formed, the caulked portion 16 is
A force directed diametrically outward is applied to the inner peripheral surface of the. this
Therefore, the diameter of the inner ring 3 changes, albeit slightly. Soshi
When the amount of change becomes large, cracks or the like
In addition to the possibility of damage occurring, the rolling element 5,
It is troublesome to maintain the preload given to 5 at an appropriate value.
And the rolling bearing unit 1 for wheel support including the inner ring 3
It may be difficult to ensure the durability of the. Special
Then, the inner ring 3 rotates with respect to the shaft member 2.
In order to prevent this, the caulking strength of the caulking part 16 is sufficient
If you try to secure the
Therefore, it is difficult to ensure the durability of the inner ring 3. [0009] In view of such circumstances, Japanese Patent Application No. Hei 8-3680.
No. 0 has a spacer ring between the inner ring end face and the swaged part.
To the outside in the diametrical direction associated with the work of forming
Disclosure of structure that receives facing force by this spacer ring
Have been. According to the structure according to the preceding invention, the caulked portion
Diametrically outward force generated during the formation of
Is mostly received by the spacer ring. Therefore,
The inner ring hardly receives this diametrically outward force,
The inner ring can be prevented from being damaged. However, such a spacer
Even in the case of a structure with a ring, the caulking part itself
The amount of processing from the cylinder is large, and the deformation
Cracks and the like are likely to occur, and it is difficult to ensure durability. [0010] Rolling bearing unit for supporting wheels of the present invention
Is like thisIn view of the caulking sectionDamage such as cracks
It is hard to generate, and the inner ring is fixed to the shaft member.
Work to form locking recesses to prevent nuts from loosening
Cost by eliminating the work of caulking nuts and nuts
It was invented for the purpose of reduction. [0011] SUMMARY OF THE INVENTION According to the present invention, a wheel supporting roll is provided.
Each bearing unit is a conventional or prior invention wheel support.
Like the rolling bearing unit, the first flange
With multiple rows on the inner circumferenceOuter ring trackOutside each provided
A ring and a shaft part provided with a second flange on the outer peripheral surface of the end part
Material and an inner ring raceway on the outer peripheral surface
The at least one inner ring and the inner ring
A third portion provided on the outer peripheral surface of a portion that rotates with the shaft member.
Between the first and second inner raceways and the double row outer raceways.
And a plurality of rolling elements provided respectively. And on
RecordShaft memberOf the cylindrical part formed at the end of
The part protruding from the ring is swaged diametrically outward and
Above due to the swollen partHold down inner ringBy things
And the inner ring aboveShaft memberIt is fixed to. Special
In the rolling bearing unit for supporting wheels of the present invention,
IsA step portion is provided at the end of the shaft member,
Shape with the outer diameter at the distal end smaller than the outer diameter at the proximal end
Has formed. And the outer diameter of this cylindrical part is small
Caulk out the part that has become diametrically outwarding.In addition, good
Best of all,Caulking the cylindrical part at the peripheral edge of the opening of the inner ring
Place the part where the outer peripheral surface of the expanded part is pressed against the open end
Conical concave inclined surface with larger diameter as it goesAnd More preferably, the following: Configuration requirements
, Respectively, or ~ Selected from
Implement multiple configuration requirements in combination with the above requirements.
You.   An end of the shaft member to form the cylindrical portion
At the tip of the circular recessShaft memberAxis
The position for the direction isExists near the cylinderSecond
The shaft member at the center of the rolling element abutting on the inner raceway
End side of the shaft member above the position in the axial direction
Located in.   The center of the rolling element contacting the second inner ring raceway and the upper
With the end face of the inner ring or the end face of the shoulder of the inner ring
The distance of the shaft member in the axial direction is outside the rolling element.
It is 0.75 times or more the diameter.   Outer diameter of the part where the inclined surface is formed at the end of the inner ring
Is smaller than the outer diameter of the shoulder of the inner ring.   Part of the outer peripheral surface of the distal end of the shaft member,
A concave groove is formed in the portion facing the small-diameter side end of the slope, and
And formed at the end of the shaft member.
The part of the cylindrical part that is closer to the tip than the concave groove
Spread outward.   Extension position of the line of action of load applied to inner ring from rolling elements
Is closer to the axial center of the shaft member than the inclined surface.
In the part where the outer diameter of this shaft member does not change,
Let [0013] The wheel supporting roller of the present invention configured as described above is provided.
The bearing unit rotates the wheels relative to the suspension.
The function of supporting the bearing is the conventional rolling bearing unit for wheel support.
It is the same as a set. In particular, the rolling shaft for wheel support of the present invention
In the case of the receiving unit, it is formed at the end of the shaft member.
Cylindrical partThe part to be swaged out has a small outer diameter via the step
Because it is a small part, with caulking work
It becomes difficult to apply excessive force to the cylindrical part, and the swaging part
The damage such as cracks is less likely to occur. [0014] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIGS.
The present invention incorporatingThe applicable structure ofShow the first example
ing. still,This exampleIs characterized in that the shaft member 2
The structure of the part for fixing the wheel 3 is provided. Structure of other parts
The operation is the same as that of the conventional structure shown in FIG.
Therefore, duplicate explanation is omitted or simplified,
Hereinafter, the description will focus on the features of the present invention. Step 8 formed at the inner end of shaft member 2
The inner ring 3 externally fitted to the step 8 at a portion near the inner end of the middle
On the inner peripheral surface of the inner end, the inner diameter increases toward the inner end opening.
, A conical concave inclined surface 19 is formed. This slope
The surface 19 is inclined with respect to the center axis of the shaft member 2.
Is about 20 to 60 degrees. In addition,
A circular recess 20 is formed on the inner end surface of the shaft member 2.
As a result, a cylindrical portion 21 is formed at the inner end of the shaft member 2.
Has formed. In the case of this example, this cylindrical portion 21 is
At the inner end of the shaft member 2, substantially within the shoulder 23 of the inner ring 3.
Present on the side part. The inner ring 3 having the above-described inclined surface 19 is formed.
With the cylindrical portion 21 provided at the inner end of the shaft member 2.
It is fixed to this shaft member 2 by swaging and
inventionIs applicable structure,Rolling bearings for wheel support
When knitting, the case of the conventional structure shown in FIG.
The amount of deformation of the swaged portion is smaller than that of. That is,
In the case of the above-mentioned conventional structure, since the caulked portion 16 is formed,
The cylindrical part formed at the inner end of the shaft member 2 is diametrically outward.
To 90 degrees, while the wheel support of the present invention
In order to constitute a rolling bearing unit, the cylindrical portion 21
When caulking and widening, this cylindrical part 21 is set at the above-mentioned inclination angle.
What is necessary is just to deform by θ (= 20 to 60 degrees). Because of this,
The distortion generated in the caulked portion is kept small,
It is possible to suppress the occurrence of damage such as cracks in the tightening part
You. Also, in order to reduce the amount of deformation,
Based on the formation, it exists around the cylindrical portion 21
To the inner ring 3 which is a member, diametrically outward of the inner ring 3
The applied force can be reduced to prevent the inner ring 3 from being damaged.
You. Note that the cylindrical portion 21 is swept outward in the diameter direction.
Spreading work is performed by forging or oscillating pressing
Do. Regardless of which processing method is adopted, it is shown in FIG.
Press the press die 25 into the inner diameter side of the cylindrical portion 21
Then, the cylindrical portion 21 is swaged outward in the diameter direction. Special
In addition, if rocking press processing is used for caulking work,
To reduce the load on
There is an advantage that the preload control can be properly performed later. or,
The inner edge of the cylindrical portion 21 (the inner diameter of the cylindrical portion 21 changes.
Distance L between the inner end 3 and the end face 24 of the inner ring 3
Depends on the size of the rolling bearing unit for wheel support, etc.
It is determined by design, but the wheel support roll for general passenger cars
5 to 15 mm
Good. Further, in order to form the cylindrical portion 21,
Tip position of circular recess 20 formed at the end of shaft member 2
The inner row of the rolling elements 5, 5 arranged in multiple rows is
It is positioned inside the center of the rolling element 5 that constitutes it.
That is, the upper part of the tip of the recess 20 shown by the point X in FIG.
The position of the shaft member 2 in the axial direction is the second inner ring.
A second inner ring gauge provided on the outer peripheral surface of the inner ring 3 as a track
The shaft member 2 at the center of the rolling element 5 abutting on the road 9
Than the position in the axial direction of the shaft member 2
It is located on the end side. Therefore, the wheel supporting rolling shaft
Between the shaft member 2 and the outer ring 4 constituting the receiving unit
A radial load is applied, and the rolling element 5
Even when a radial load is applied to the wheel raceway 9,
The part of the shaft member 2 that receives this radial load is full.
Since it is a real substance, the durability of this shaft member 2 is sufficiently confirmed.
Can be maintained. Further, the rolling contact with the second inner raceway 9 is made.
The shear between the center of the moving body 5 and the end face 24 of the inner ring 3
The distance M in the axial direction of the shaft member 2 is
0.75 times or more (M ≧ 0.75D) of the outer diameter D of 5,5
are doing. Thus, the distance between the center of the rolling element 5 and the end face 24 is
Since the separation M is secured, the shoulder 23 of the inner ring 3 and the second
Prevents dimensional accuracy and shape accuracy of inner ring raceway 9 from deteriorating
Stop to secure the function of the wheel supporting rolling bearing unit.
Wear. In other words, the dimensional accuracy and shape accuracy of these parts are good.
Operation of the rolling bearing unit for supporting wheels.
In addition to preventing occurrence of vibration and the like during rolling, the rolling element 5
The rolling contact life of the second inner ring raceway 9
it can. In the illustrated example, the first inner raceway 7 is shuffled.
Is formed directly on the outer peripheral surface of the intermediate portion of the
One inner raceway 7 is formed on an inner race separate from the shaft member 2.
Then, the inner ring may be externally fitted and fixed to the shaft member 2.
No. Next, FIG. Set the configuration requirements
The present inventionThe applicable structure ofShows a second example
You. In the case of this example, the inner end of the shaft member 2
Inner than the end face 24 of the inner ring 3 fitted externally to the shaft member 2
The spacer ring 18 is externally fitted to the
You. The inner peripheral surface of the inner half of the spacer ring 18 has an inner end.
Conical concave inclined surface whose inner diameter increases toward the opening
19 are formed. And, of the shaft member 2
A cylindrical portion at the end inside the spacer ring 18
21 by crimping it outward in the diametric direction.
Of the inner ring 3 toward the end face 24 of the inner ring 3
The inner ring 3 is fixedly connected to the shaft member 2.
You. Also, between the second inner raceway 9 and the second outer raceway 14.
Line of action of load applied to the inner ring 3 from the rolling elements 5
The extension position of the line (corresponding to the chain line α representing the antenna)
The outer diameter changes near the center of the step portion 8 in the axial direction from the surface 19.
There is no part. In the case of this embodiment, such a spacer ring 18
Is provided, so that when the cylindrical portion 21 is swaged and expanded,
Even when the swaging strength is sufficiently increased,
Elastic deformation in the diameter direction can be reliably prevented. That is,
In the case of this example, when the cylindrical portion 21 is swaged and expanded,
In other words, the diametrically outward force is applied to the shaft member 2.
The fitted spacer ring 18 receives. Therefore, the above cylinder
With the work of caulking and expanding the portion 21, the diameter of the inner ring 3
Changes less than in the first example described above.
(Almost no change). In addition, temporarily, the spacer ring 1
8 for wheel support even if dimensional accuracy and shape accuracy of 8 deteriorate
Has no adverse effect on the performance of the rolling bearing unit
No. In the case of this example, the extension position of the line of action of the load
This load caulks the cylindrical part 21
Prevent it from acting on the expanded part,
Durability can be ensured. The point that a spacer ring 18 is provided;
Configuration and operation other than the point where the extension position of the action line is restricted
The use is the same as in the case of the first example described above. Next, FIG. Configuration requirements
The present invention incorporatedThe applicable structure ofShow the third example
I have. In the case of the present example, the shaft member 2 is externally fitted to the inner end.
Outside the portion where the inclined surface 19 is formed at the inner end of the inner ring 3a
The diameter is smaller than the outer diameter of the shoulder 23 of the inner race 3a.
Thus, the inner ring cylindrical portion 26 is formed. In the case of this example,
The cylindrical portion 21 formed at the inner end of the shaft member 2 is
Swage diametrically outward toward the inclined surface 19, and
When fixing the inner ring 3 to the shaft member 2, the inner ring
The cylindrical portion 26 receives most of the stress caused by swaging.
You. Therefore, the inner ring cylindrical portion 26 which is thinner than the shoulder portion 23
Of the inner ring 3a and the shoulder 23
The amount of deformation of the second inner raceway 9 can be reduced. As a result, the car
The rotational accuracy of the wheel bearing rolling bearing unit is sufficiently good.
Can be maintained. In the case of this example, the second inner ring is used.
The center of the rolling element 5 in contact with the track 9 and the shoulder of the inner ring 3a
In the axial direction of the shaft member 2 with the end face 24a of the portion 23
With respect to the outer diameter D of each of the rolling elements 5 and.
75 times or more (M ≧ 0.75D). Also, in this example
In some cases, the extension of the load action line is
The durability of fixed parts is ensured. Other configurations and works
The use is the same as in the case of the first example described above. Next, FIG.
The present inventionThe applicable structure ofShows a fourth example
You. In the case of the first to third examples described above, the outer ring 4 is not rotated.
A stationary wheel, and a structure in which the shaft member 2 is rotated.
On the other hand, in the case of this example, the shaft member 2 is suspended.
The outer ring 4 is rotated together with the wheels without being rotated by being supported by the device.
Rotating wheel. Because the rotating side and the stationary side were reversed
The other configuration and operation are the same as those of the first example described above.
You. Next, FIG.ofCombine configuration requirements
Of the embodiment of the present inventionOne exampleIs shown. This example
, The inner end of the shaft member 2 is
The outer diameter of the protruding part is smaller than the outer diameter of this fitting part.
Comb. That is, it is formed at the inner end of the shaft member 2.
The inner end of the inner ring 3 is opened on the outer peripheral surface of the base end of the cylindrical portion 21.
The second inner ring gauge is slightly smaller than the inclined surface 19 formed at the mouth.
A slight step of about 0.02 to 1 mm on the part near the road 9
A step 27 having H is formed. And the above circle
The portion of the cylindrical portion 21 having a reduced outer diameter is defined by a diametrical direction.
Caulk outward and spread out so that the inclined surface 19 is suppressed.
ing. In this way, the cylindrical portion 21 is swaged outward in the diametrical direction and widened.
When stepping down, the step 27 is swaged
It is the starting point of the bent part. For this reason, swaging work
As a result, it becomes difficult to apply excessive force to the cylindrical portion 21.
To reduce the likelihood of damage such as cracks in the swaged portion
You. Other configurations and operations are the same as those of the first example described above.
The same is true. In addition, the structure of this example is described above.Apply the present invention
Of possible structureWhen applied to the fourth example,
The inside and outside directions are reversed. Next, FIG. Set the configuration requirements
The present inventionFifth Example of a Structure to which the Method can be AppliedShows
You. In the case of this example, a part of the outer peripheral surface of the inner end portion of the shaft member 2
Then, the small diameter side end of the inclined surface 19 formed at the inner end of the inner ring 3
Has a depth K of about 0.1 to 2 mm in the portion facing
The concave groove 28 is formed over the entire outer peripheral surface.
And a cylindrical portion formed at the inner end of the shaft member 2.
21 is a portion closer to the inner end than the groove 28,
Caulking outward in the direction to hold down the inclined surface 19
I have to. In this way, the cylindrical portion 21 is slid outward in the diameter direction.
When expanding, the concave groove 28 is
It is the starting point of the bent part. For this reason, swaging work
It is difficult for excessive force to be applied to the cylindrical part 21 with the work.
Therefore, damage such as cracks is unlikely to occur in the swaged part
You. Other configurations and operations are the same as those of the first example described above.
The same is true. In addition, the structure of this example is described above.Apply the present invention
Of possible structureWhen applied to the fourth example, the
The inside and outside directions are reversed. [0026] The rolling bearing unit for supporting wheels according to the present invention.
Is constructed and operates as described above,
This inner ring and this inner ring are fixed by preventing the diameter from changing.
The swaged part to secure the inner ring is
Lower the possibility of damageit can. [Brief description of the drawings] FIG. 1 shows the present invention.The applicable structure ofHalf-section showing the first example
Area view. FIG. 2 shows a hollow section formed at an inner end of a shaft member.
The principal part expanded sectional view which shows the state which expands. FIG. 3 shows the present invention.The applicable structure ofHalf-section showing the second example
Area view. FIG. 4 is a half sectional view showing the third example. FIG. 5 is a half sectional view showing the fourth example. FIG. 6One example of an embodiment of the present inventionMain section enlarged cross section showing
FIG. FIG. 7Fifth example of structure to which the present invention can be appliedMain part expansion indicating
Large sectional view. FIG. 8 is a half sectional view showing a first example of a conventional structure. FIG. 9 is a half sectional view showing the second example. [Explanation of symbols] 1 Rolling bearing unit for wheel support 2 Shaft member 3, 3a Inner ring 4 Outer ring 5 rolling elements 6 Second flange 7 First inner ring track 8 steps 9 Second inner ring track 10 Male thread 11 nuts 12 Step surface 13 First outer ring orbit 14 Second outer ring orbit 15 First flange 16 Caulking part 17 Locking recess 18 Spacer 19 Slope 20 recess 21 cylindrical part 22 Seal ring 23 Shoulder 24, 24a end face 25 Press type 26 Inner ring cylindrical part 27 Step 28 groove 29 Lid [Procedure amendment 2] [Document name to be amended] Drawing [Correction target item name] Fig. 5 [Correction method] Change [Correction contents] FIG. 5

───────────────────────────────────────────────────── フロントページの続きＦターム(参考） 3J017 AA02 DA01 DB08 3J101 AA02 AA32 AA43 AA54 AA62 BA77 FA44 FA55 GA02 GA03 ────────────────────────────────────────────────── ─── Continuation of front page F term (reference) 3J017 AA02 DA01 DB08 3J101 AA02 AA32 AA43 AA54 AA62 BA77 FA44 FA55 GA02 GA03

Claims

Claims: 1. A shaft provided with an outer ring provided with a first flange on an outer peripheral surface, a plurality of rows of inner ring tracks on an inner peripheral surface, and a second flange provided on an outer peripheral surface of an end portion. At least one member having an inner raceway on an outer peripheral surface and having an outer ring
A plurality of inner rings, and a plurality of rollers each provided between the first and second inner ring raceways provided on the outer peripheral surface of a portion including the inner ring and rotating with the shaft member, and the double-row outer ring raceway. A part protruding from the inner ring in a part of the cylindrical portion formed at the end of the shaft is swaged outward in the diametric direction, and the swaged portion directly or via a spacer ring to the inner ring. By holding down
In the wheel bearing rolling bearing unit for fixing the inner ring to the shaft, a portion of the inner ring or a portion where the cylindrical portion is swaged at an opening peripheral edge of a spacer ring externally fitted closer to the tip of the shaft than the inner ring. A rolling bearing unit for supporting a wheel, characterized in that the portion against which the outer peripheral surface is pressed is a conical concave inclined surface whose inner diameter increases toward the opening end.