JP4085736B2 - Rolling bearing device - Google Patents

Rolling bearing device Download PDF

Info

Publication number
JP4085736B2
JP4085736B2 JP2002233422A JP2002233422A JP4085736B2 JP 4085736 B2 JP4085736 B2 JP 4085736B2 JP 2002233422 A JP2002233422 A JP 2002233422A JP 2002233422 A JP2002233422 A JP 2002233422A JP 4085736 B2 JP4085736 B2 JP 4085736B2
Authority
JP
Japan
Prior art keywords
wheel
rolling bearing
bearing device
axial direction
guide
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
JP2002233422A
Other languages
Japanese (ja)
Other versions
JP2004074815A (en
Inventor
眞平 首藤
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
JTEKT Corp
Original Assignee
JTEKT Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by JTEKT Corp filed Critical JTEKT Corp
Priority to JP2002233422A priority Critical patent/JP4085736B2/en
Publication of JP2004074815A publication Critical patent/JP2004074815A/en
Application granted granted Critical
Publication of JP4085736B2 publication Critical patent/JP4085736B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/80—Labyrinth sealings
    • 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft
    • 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
    • F16C19/185—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 two raceways provided integrally on a part other than a race ring, e.g. a shaft or housing
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward

Landscapes

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

Description

【０００１】
【発明の属する技術分野】
本発明は、転がり軸受装置に関する。
【０００２】
【従来の技術】
車軸用転がり軸受装置は、外輪部材と、この外輪部材に同心かつ径方向内方に配置される内輪部材と、外輪部材と内輪部材との間に転動自在に配置される複列の玉とを有する。
【０００３】
例えば外輪部材は、その外周面途中に径方向外向きに突出してブレーキディスクを取付けるためのハブフランジを有する。このハブフランジの車両インナ側部分の内周面に玉の外輪軌道面が形成され、ハブフランジの車両アウタ側部分は、ブレーキディスクおよびタイヤホイールを重ねて取付けるためのインロー部とされている。
【０００４】
【発明が解決しようとする課題】
上記のように、従来の転がり軸受装置では、外輪部材は、径方向外向きに突出するハブフランジと、その車両インナ側部分および車両アウタ側部分を熱間鍛造によって一体的に形成している。このように３方向に張出す部分を有する外輪部材を、熱間鍛造によって一体的に形成するためには、高価で大掛かりな設備を必要とする。
【０００５】
【課題を解決するための手段】
本発明における転がり軸受装置は、固定輪と、この固定輪に径方向同心に配置されて軸心回りに回転自在に設けられる回転輪と、前記固定輪と回転輪との間に転動自在に設けられる転動体と、前記回転輪の軸方向一方側端部の外周部に、径方向外向きに突出するよう形成されるフランジと、環状のブレーキディスクおよび環状のタイヤホイールを前記フランジに取付ける際に案内する案内部材とを含み、前記案内部材は、前記回転輪とは別体であるとともに、外周部に前記ブレーキディスクおよびタイヤホイールにおける中心穴用の案内面を有する筒状の外側案内部と、この外側案内部の軸方向一方側端部に径方向内方に向けて形成した折曲部を介して前記外側案内部の径方向内方に一体に形成される筒状の内側補強部とから成形され、前記外側案内部の軸方向他方側端部が、前記回転輪の軸方向一方側端部に取付けられており、前記外側案内部の軸方向一方側端部において前記タイヤホイールの取付け穴に対向して前記外側案内部の周方向等配位置に凹部が形成されている。
【０００６】
上記構成において、案内部材を回転輪と別体とすることにより、回転輪の製造のための装置を縮小化し得、製造時間を削減して製造コストを低減し得る。
【０００７】
また、案内部材を、外側案内部と、この外側案内部の径方向内方に配置される内側補強部とから成形したことにより、外側案内部のみの場合に比べて案内部材の剛性が向上する。
【０００８】
また、前記内側補強部は、前記回転輪と固定輪との間の環状空間を軸方向一方側で密封する密封部を有しており、前記密封部の端面と前記固定輪の軸方向一方側端面との間に隙間を形成した構成とすることにより、特別に環状空間の密封部を設ける場合に比べて製造コストを低減し得る。
【０００９】
【発明の実施の形態】
以下、本発明の実施形態に係る転がり軸受装置を、車軸用転がり軸受装置を例に、図面に基づいて説明する。まず図１および図２に基づいて本発明の第一の参考例を説明する。図１は本発明の第一の参考例を示す車軸用転がり軸受装置の全体構成を示す断面図、図２は図１の要部拡大断面図である。
【００１０】
図示のように、第一の参考例における車軸用転がり軸受装置１は、従動輪側に設けられるもので、軸心回りに回転自在な回転輪としての筒状の外輪部材２と、この外輪部材２の径方向内方に配置される固定輪としての内輪部材３，４と、外輪部材２と内輪部材３，４との間の環状空間５に転動自在に配置される転動体としての２列の玉６，７とを有する。
【００１１】
内輪部材３，４は、軸方向に並設した２個の内輪部材３，４が背面組合せ式に用いられている。外輪部材２の車両アウタ側（軸方向一方側）に、径方向外向きに突出するよう形成されるハブフランジ８が形成されている。また車軸用転がり軸受装置１は、ブレーキディスク９およびタイヤホイール１０をハブフランジ８に対して重ねて取付ける際に、ブレーキディスク９およびタイヤホイール１０のそれぞれの中心に形成された取付け穴（中心穴）９ａ，１０ａの周面を案内する案内部材１１を有する。
【００１２】
各列の玉６，７は、それぞれ保持器１２，１３によって円周方向等配位置に保持されている。各内輪部材３，４の各外周面に、各列の玉６，７の内輪軌道面が形成され、外輪部材２の内周面に、各列の玉６，７の外輪軌道面が形成されている。外輪部材２と内輪部材３，４との間の環状空間５を、車両インナ側で密封する密封部材１４が環状空間５の車両インナ側端部に配置されている。
【００１３】
内輪部材３，４の中心穴１５に、車軸１６が挿通され、この車軸１６の車両インナ側には、車両インナ側の内輪部材４から軸方向に突出した位置で径方向外向きに拡径される固定用フランジ１７が一体的に形成される。この固定用フランジ１７は車体側に組付けられた、不図示のキャリアに対して軸心回りに非回転に固定される。
【００１４】
車軸１６の車両アウタ側の端部は、車両アウタ側の内輪部材３から軸方向に突出した部分にねじ部１８が形成されている。このねじ部１８にナット１９が螺着され、これにより各列の玉６，７に所定の予圧が付与される。
【００１５】
図の符号２０は、ハブボルトを示し、このハブボルト２０は、ハブフランジ８に重ねられるブレーキディスク９およびタイヤホイール１０に形成された取付け孔２１に挿通されるものである。
【００１６】
前記案内部材１１は、前記外輪部材２とは別体であり、耐食性に優れる金属製の板状あるいは管状の素材（メッキ鋼板：ＳＥＣＣやステンレス鋼：ＳＵＳ４３０などが用いられる）を冷間鍛造することによって形成されるものである。この案内部材１１は、外輪部材２の車両アウタ側端部開口に嵌着される。
【００１７】
案内部材１１は、径方向外側に配置されてブレーキディスク９およびタイヤホイール１０の案内面２３を有する筒状の外側案内部２４と、この外側案内部２４に、その車両アウタ側端部に径方向内方に向けて形成した折曲部２５を介して車両インナ側に折曲して外側案内部２４に平行に配置された筒状の内側補強部２６と、この内側補強部２６の車両インナ側端部から径方向内方に折曲して形成された環状の密封部２７とから形成される。外側案内部２４と内側補強部２６との間には、折曲部２５によって、環状の間隙２８が形成されている。外側案内部２４の車両インナ側端部は、外輪部材２の中心穴２９における車両アウタ側周面を切削して拡径した嵌着部３０に圧入されている。
【００１８】
密封部２７の端面２７ａと車両アウタ側の内輪部材３の端面３ａとの間にはわずかな隙間３１が形成され、密封部２７の端面２７ａと車両アウタ側の内輪部材３の端面３ａとでラビリンス機能を有する。これにより、軸受内部に泥水等が侵入するのを防止できる。
【００１９】
上記構成において、外輪部材２に対し、各列の玉６，７および内輪部材３，４を組付け、車軸１６を内輪部材３，４の中心穴１５に挿通して、ねじ部１８にナット１９を螺着し、各列の玉６，７に所定の予圧を付与する。その後、案内部材１１における外側案内部２４の端部を、外輪部材２の中心穴２９における嵌着部３０に圧入する。これにより、案内部材１１を外輪部材２に組付ける。
【００２０】
このとき、上記したように、密封部２７の端面２７ａと車両アウタ側の内輪部材３の端面３ａとの間にラビリンス機能を有する隙間３１が形成され、これにより、軸受内部に泥水等が侵入するのを防止できる。なお、図示しないが、案内部材１１の開放側にエンドキャップを設けることで、いっそうシール性は向上する。
【００２１】
上記のようにして、案内部材１１を外輪部材２に組付けた後、ブレーキディスク９およびタイヤホイール１０のそれぞれの中心に形成された取付け穴９ａ，１０ａを案内部材１１における外側案内部２４に案内させて、ブレーキディスク９およびタイヤホイール１０をハブフランジ８に対して重ねて取付ける。
【００２２】
そして、案内部材１１は、外側案内部２４に折曲部２５を介して形成される内側補強部２６を有しているので、車輪側から車両重量による負荷が働いた場合であっても、その荷重を充分に支持し得る。
【００２３】
さらに、案内部材１１は外輪部材２とは別体である。このため外輪部材２は径方向と軸方向一方に張出す部分を有するのみであり、従って、その製造（例えば熱間鍛造）にあたって従来のように大掛かりな装置を使用する必要がなく、また製造のための時間も削減できる。案内部材１１は、金属製の板状あるいは管状の素材を、冷間鍛造によって形成している。このため安価なコストで製造することができる。
【００２４】
図３に第二の参考例を示す。図３は、第二の参考例を示す要部拡大断面図である。この第二の参考例では、案内部材１１は、金属製の板状あるいは管状の素材を用いて、外側案内部２４、折曲部２５、内側補強部２６、密封部２７に加え、外側案内部２４の車両インナ側（図３の右側）の端部に径方向外方へ拡がる係止片３２が形成されている。この係止片３２は、外輪部材２の中心穴２９における嵌着部３０をさらに拡径するよう形成した係止部３６に係合されている。
【００２５】
さらに外側案内部２４は、車両インナ側の大径部３４と車両アウタ側の小径部３５とを有し、大径部３４と小径部３５との間には、段部３３が形成されている。大径部３４と小径部３５とはそれぞれ平行（同心）の環状に形成されている。
【００２６】
なお係止片３２から大径部３４にかけて、軸方向に沿って円周方向等配位置に複数個形成されるもので大径部３４の円周方向等配位置に不図示のスリットが形成される。これらスリットによって係止片３２から大径部３４にかけて縮径することが可能になる。案内部材１１を外輪部材２に取付ける際は、係止片３２から大径部３４にかけて縮径して、外側案内部２４を嵌着部３０に嵌着する。他の構成は上記第一の参考例と同様であるので、同一の符号を付してその説明を省略する。
【００２７】
この第二の参考例においては、外側案内部２４の軸方向途中位置において径方向に沿う段部３３を形成している分だけ案内部材１１の剛性が向上し、より確実に負荷を支持することができる。さらに、案内部材１１に係止片３２を形成して嵌着部３０に形成した係止部３６に係止させているので、案内部材１１の引抜き抵抗を増大させることができる。
【００２８】
次に、図４に基づいて本発明の第三の参考例を説明する。図４は本発明の第三の参考例を示す要部拡大断面図である。この第三の参考例では、案内部材１１の外側案内部２４の軸方向途中位置に、周方向に沿う凹部３７が形成されている点で、第一の参考例と異なる。この凹部３７の両側には、径方向に沿う段部３８，３９が形成され、車両アウタ側の段部３８の方が車両インナ側の段部３９に比べて低く形成され、これにより、外側案内部２４は車両アウタ側の小径部４０と、車両インナ側の大径部４１とを有する。
【００２９】
凹部３７を形成する底部４２は、小径部４０よりもさらに小径で、小径部４０および大径部４１に平行（同心）な環状に形成されている。案内部材１１の車両アウタ側端面から凹部３７までの軸方向に沿った距離は、タイヤホイール１０の幅に等しく形成され、凹部３７からハブフランジ８までの軸方向に沿った距離は、ブレーキディスク９の幅に等しく形成されている。他の構成は上記第一の参考例と同様であるので、同一の符号を付してその説明を省略する。
【００３０】
この第三の参考例において、案内部材１１に、段部３８，３９を設けた分だけ案内部材１１の剛性が向上し、負荷に対する抵抗力を増大させることができる。
【００３１】
ところで、一般に、案内部（インロー部）の外周面には、タイヤホイール１０の取付け穴１０ａの内周面との凝着を防止するために、凝着防止用の塗装が施される。これは、製造コストの上昇要因となる。
【００３２】
しかし、本発明の第三の参考例では、小径部４０に凹部３７を形成して、小径部４０の外周面と取付け穴１０ａの内周面との接触面積を従来に比べて小さくしてある。これにより、タイヤホイール１０の取付け穴１０ａの内周面との凝着を抑えることができるため、従来の凝着防止用の塗装を省略することができ、製造コストの低減を図り得る。他の作用効果は、上記第一の参考例と同様であるので、その説明を省略する。
【００３３】
次に、図５および図６に基づいて本発明の実施形態を説明する。本実施形態は、案内部材１１と、タイヤホイール１０の取付け穴１０ａの周面との凝着を防止する例であり、径方向にくぼむ凹部８７を、軸方向に沿って外側案内部２４の円周方向等配位置に配置するものである。この場合も、双方の部材の接触面積が小さくなり、双方の部材の凝着を防止することができ、凝着防止用の塗装を省略することができる。その他の部分において、上記各参考例と同様の機能を有する構成部分には、同一の符号を付してその説明を省略する。
【００３４】
上記各参考例ならびに実施形態における車軸用転がり軸受装置１は、従動輪側に適用される場合を説明した。これに対し、本発明の第四の参考例に係る車軸用転がり軸受装置１は、駆動輪側に適用される。
【００３５】
図７は、本発明の第四の参考例に係る車軸用転がり軸受装置の全体構成を示す断面図である。
【００３６】
この参考例における車軸用転がり軸受装置１は、車体側に軸心回りに非回転に取付けられる外輪部材５０と、この外輪部材５０に径方向に同心に配置されて軸心回りに回転自在に設けられる内輪部材５１と、外輪部材５０と内輪部材５１との間の環状空間５２に転動自在に配置される２列の玉５３，５４とを備える。これら各列の玉５３，５４は、保持器５５によって円周方向等配位置に配置されている。
【００３７】
外輪部材５０の外周面上に、図示しない車体側に取付けられる固定用フランジ５６が、径方向外向きに突出して形成される。
【００３８】
内輪部材５１は、中心穴５７を有するハブ軸５８と、このハブ軸５８の車両インナ側に形成された環状の凹部５９に嵌着する環状部材６０とから形成される。このハブ軸５８は、その車両アウタ側に径方向外方に突出するハブフランジ６１が一体的に形成されている。内輪部材５１の中心穴５７における車両アウタ側内周面には、中心穴５７よりも大きな内径を有する嵌着部６２が形成されている。
【００３９】
ハブ軸５８の外周面に、一方列の玉５３の内輪軌道面が形成され、環状部材６０の外周面に、他方列の玉５４の内輪軌道面が形成されている。外輪部材５０の内周面に、両列の玉５３，５４の外輪軌道面が形成されている。環状空間５２の車両アウタ側および車両インナ側に、環状空間５２を両側で密封する密封部材６３，６４が配置されている。
【００４０】
内輪部材５１の中心穴５７に、車軸（駆動軸）６５がスプライン部６６を介して内輪部材５１と軸心回りに回転一体に組付けられ、車軸６５の端部に形成したねじにナット６７が螺着されることにより、環状部材６０がハブ軸５８に対して回転一体に取付けられるとともに、各列の玉５３，５４に対して所定の予圧が付与される。
【００４１】
また車軸用転がり軸受装置１は、ブレーキディスク６８およびタイヤホイール６９をハブフランジ６１に対して重ねて取付ける際に、ブレーキディスク６８およびタイヤホイール６９のそれぞれの中心に形成された取付け穴６８ａ，６９ａの周面を案内する案内部材７０を有する。
【００４２】
この案内部材７０は、径方向外側に配置されてブレーキディスク６８およびタイヤホイール６９の案内面７１を有する筒状の外側案内部７２と、この外側案内部７２に、その車両アウタ側端部に径方向内方に向けて形成した折曲部７３を介して車両インナ側に折曲して外側案内部７２に平行に配置された筒状の内側補強部７４とからなる。
【００４３】
外側案内部７２と内側補強部７４とは、互いに平行に形成され、外側案内部７２の軸方向長さに比べて内側補強部７４の軸方向長さがわずかに短く形成されている。案内部材７０は、金属製の板状あるいは管状の素材を用いて冷間鍛造やプレス加工で形成される。
【００４４】
図の符号７５は、ハブボルトを示し、このハブボルト７５は、ハブフランジ６１に重ねられるブレーキディスク６８およびタイヤホイール６９に形成された取付け孔７６に挿通されるものである。
【００４５】
上記構成の車軸用転がり軸受装置１は、外輪部材５０に対して玉５３，５４を組込み、内輪部材５１を組込んで、ナッ６７をねじに螺着する。続いて、案内部材７０の外側案内部７２を嵌着部６２に圧入するようにして組立てる。
【００４６】
続いて、ブレーキディスク６８およびタイヤホイール６９のそれぞれの中心に形成された取付け穴６８ａ，６９ａを案内部材７０における外側案内部７２に案内させて、ブレーキディスク６８およびタイヤホイール６９をハブフランジ６１に対して重ねて取付ける。
【００４７】
そしてこの参考例では、車軸６５が軸心回りに回転するのに伴なって、内輪部材５１が軸心回りに回転し、ブレーキディスク６８およびタイヤホイール６９（タイヤ）が軸心回りに回転駆動する。
【００４８】
この参考例においても、案内部材７１は、外側案内部７２に折曲部７３を介して形成される内側補強部７４を有しているので、車輪側から車両重量による負荷が働いた場合であっても、その荷重を充分に支持し得る。
【００４９】
なお図示しないが、この参考例においても案内部材７１の開放側（車両アウタ側）に、エンドキャップを挿着することで、軸受部分に対するシール性を確保することができる。
【００５０】
なお、この第四の参考例における案内部材７０を、上記第二の参考例、あるいは第三の参考例で示したように、外側案内部７２を大径部と小径部とから形成するようにしてもよい。この場合は、いっそう案内部材７０の剛性を向上させることができる。
【００５１】
【発明の効果】
以上の説明から明らかな通り、本発明によれば、ブレーキディスクおよびタイヤホイールを取付けるための案内部材を、回転輪とは別体の構成としたことにより、全体の製造コストが安価になり、案内部材に、外側案内部の径方向内方に配置される内側補強部を設けたことにより、剛性の高い案内部材となる。
【図面の簡単な説明】
【図１】 本発明の第一の参考例を示す車軸用転がり軸受装置の全体構成を示す断面図である。
【図２】 同じく図１の要部拡大断面図である。
【図３】 本発明の第二の参考例を示す要部拡大断面図である。
【図４】 本発明の第三の参考例を示す要部拡大断面図である。
【図５】 本発明の実施形態を示す要部拡大断面図である。
【図６】 同じく拡大正面図である。
【図７】 本発明の第四の参考例に係る車軸用転がり軸受装置の全体構成を示す断面図である。
【符号の説明】
１ 車軸用転がり軸受装置
２ 外輪部材
３，４ 内輪部材
８ ハブフランジ
９ ブレーキディスク
１０ タイヤホイール
１１ 案内部材
２３ 案内面
２４ 外側案内部
２５ 折曲部
２６ 内側補強部
２７ 密封部
３０ 嵌着部
３１ 隙間[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a rolling bearing device.
[0002]
[Prior art]
The rolling bearing device for an axle includes an outer ring member, an inner ring member that is concentric with the outer ring member and radially inward, and a double-row ball that is rotatably disposed between the outer ring member and the inner ring member. Have
[0003]
For example, the outer ring member has a hub flange for projecting radially outward in the middle of the outer peripheral surface thereof to attach a brake disk. The outer ring raceway surface of the ball is formed on the inner peripheral surface of the vehicle inner side portion of the hub flange, and the vehicle outer side portion of the hub flange is an inlay portion for attaching the brake disk and the tire wheel in a stacked manner.
[0004]
[Problems to be solved by the invention]
As described above, in the conventional rolling bearing device, the outer ring member integrally forms the hub flange projecting radially outward, the vehicle inner side portion, and the vehicle outer side portion by hot forging. Thus, in order to integrally form the outer ring member having the portions protruding in the three directions by hot forging, expensive and large-scale equipment is required.
[0005]
[Means for Solving the Problems]
The rolling bearing device according to the present invention includes a fixed ring, a rotating wheel disposed concentrically in the radial direction of the fixed ring and provided to be rotatable about an axis, and freely rotatable between the fixed wheel and the rotating wheel. When attaching a rolling element to be provided, a flange formed so as to protrude radially outward at an outer peripheral portion of one end portion in the axial direction of the rotating wheel, and an annular brake disk and an annular tire wheel. A cylindrical outer guide portion that is separate from the rotating wheel and has a guide surface for a center hole in the brake disc and the tire wheel on an outer peripheral portion; A cylindrical inner reinforcing portion integrally formed radially inward of the outer guide portion via a bent portion formed radially inward at one axial end of the outer guide portion. Molded from The other axial end portion of the side guide part, said mounted on one axial end portion of the rotating ring and, in opposition to the mounting hole of the tire wheel in the one axial end portion of the outer guide portion Concave portions are formed at equal circumferential positions of the outer guide portion.
[0006]
In the above configuration, by separating the guide member from the rotating wheel, the apparatus for manufacturing the rotating wheel can be reduced, the manufacturing time can be reduced, and the manufacturing cost can be reduced.
[0007]
Further, by forming the guide member from the outer guide portion and the inner reinforcing portion arranged radially inward of the outer guide portion, the rigidity of the guide member is improved as compared with the case of only the outer guide portion. .
[0008]
The inner reinforcing portion has a sealing portion that seals the annular space between the rotating wheel and the fixed wheel on one side in the axial direction, and the end surface of the sealing portion and the one side in the axial direction of the fixed wheel By adopting a configuration in which a gap is formed between the end surfaces, the manufacturing cost can be reduced as compared with the case where a sealing portion of an annular space is provided.
[0009]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, a rolling bearing device according to an embodiment of the present invention will be described with reference to the drawings, taking an axle rolling bearing device as an example. First, a first reference example of the present invention will be described with reference to FIGS. FIG. 1 is a cross-sectional view showing an overall configuration of an axle rolling bearing device according to a first reference example of the present invention, and FIG. 2 is an enlarged cross-sectional view of a main part of FIG.
[0010]
As shown in the figure, the axle rolling bearing device 1 in the first reference example is provided on the driven wheel side, and has a cylindrical outer ring member 2 as a rotating wheel that is rotatable around an axis, and the outer ring member. 2 as rolling elements that are arranged so as to be freely rollable in an annular space 5 between the outer ring member 2 and the inner ring members 3, 4. With balls 6 and 7 in a row.
[0011]
As the inner ring members 3 and 4, two inner ring members 3 and 4 arranged in parallel in the axial direction are used in a rear combination type. A hub flange 8 is formed on the vehicle outer side (one axial side) of the outer ring member 2 so as to protrude radially outward. The axle rolling bearing device 1 has mounting holes (center holes) formed at the centers of the brake disk 9 and the tire wheel 10 when the brake disk 9 and the tire wheel 10 are mounted on the hub flange 8 in an overlapping manner. It has the guide member 11 which guides the surrounding surface of 9a, 10a.
[0012]
The balls 6 and 7 in each row are held at circumferentially equidistant positions by holders 12 and 13, respectively. Inner ring raceway surfaces of the balls 6 and 7 in each row are formed on the outer peripheral surfaces of the inner ring members 3 and 4, and outer ring raceway surfaces of the balls 6 and 7 in each row are formed on the inner peripheral surface of the outer ring member 2. ing. A sealing member 14 that seals the annular space 5 between the outer ring member 2 and the inner ring members 3 and 4 on the vehicle inner side is disposed at the vehicle inner side end of the annular space 5.
[0013]
An axle 16 is inserted into the center hole 15 of the inner ring members 3 and 4, and the diameter of the axle 16 is increased radially outward at a position protruding in the axial direction from the inner ring member 4 on the vehicle inner side. The fixing flange 17 is integrally formed. The fixing flange 17 is fixed to the carrier (not shown) mounted on the vehicle body side so as not to rotate around the axis.
[0014]
The end portion on the vehicle outer side of the axle 16 is formed with a screw portion 18 at a portion protruding in the axial direction from the inner ring member 3 on the vehicle outer side. A nut 19 is screwed onto the threaded portion 18 so that a predetermined preload is applied to the balls 6 and 7 in each row.
[0015]
Reference numeral 20 in the drawing denotes a hub bolt, and the hub bolt 20 is inserted into a brake disc 9 that is superimposed on the hub flange 8 and a mounting hole 21 formed in the tire wheel 10.
[0016]
The guide member 11 is separate from the outer ring member 2 and is cold forged with a metal plate-like or tubular material (plated steel plate: SECC, stainless steel: SUS430, etc.) having excellent corrosion resistance. Is formed. The guide member 11 is fitted into the vehicle outer side end opening of the outer ring member 2.
[0017]
The guide member 11 is disposed on the radially outer side and has a cylindrical outer guide portion 24 having a guide surface 23 of the brake disk 9 and the tire wheel 10, and the outer guide portion 24 is radially disposed on the vehicle outer side end portion thereof. A cylindrical inner reinforcing portion 26 that is bent toward the vehicle inner side through a bent portion 25 formed inward and arranged in parallel to the outer guide portion 24, and the vehicle inner side of the inner reinforcing portion 26 It is formed from an annular sealing portion 27 formed by bending inward in the radial direction from the end portion. An annular gap 28 is formed by the bent portion 25 between the outer guide portion 24 and the inner reinforcing portion 26. A vehicle inner side end portion of the outer guide portion 24 is press-fitted into a fitting portion 30 whose diameter is increased by cutting a vehicle outer side peripheral surface in the center hole 29 of the outer ring member 2.
[0018]
A slight gap 31 is formed between the end surface 27a of the sealing portion 27 and the end surface 3a of the inner ring member 3 on the vehicle outer side, and the labyrinth is formed between the end surface 27a of the sealing portion 27 and the end surface 3a of the inner ring member 3 on the vehicle outer side. It has a function. This can prevent muddy water and the like from entering the bearing.
[0019]
In the above configuration, the balls 6, 7 and the inner ring members 3, 4 in each row are assembled to the outer ring member 2, the axle 16 is inserted through the center hole 15 of the inner ring members 3, 4, and the nut 19 And a predetermined preload is applied to the balls 6 and 7 in each row. Thereafter, the end portion of the outer guide portion 24 in the guide member 11 is press-fitted into the fitting portion 30 in the center hole 29 of the outer ring member 2. Thereby, the guide member 11 is assembled to the outer ring member 2.
[0020]
At this time, as described above, the gap 31 having a labyrinth function is formed between the end surface 27a of the sealing portion 27 and the end surface 3a of the inner ring member 3 on the vehicle outer side, so that muddy water or the like enters the bearing. Can be prevented. Although not shown in the drawings, the sealing performance is further improved by providing an end cap on the open side of the guide member 11.
[0021]
After the guide member 11 is assembled to the outer ring member 2 as described above, the mounting holes 9a and 10a formed at the centers of the brake disc 9 and the tire wheel 10 are guided to the outer guide portion 24 of the guide member 11. Then, the brake disc 9 and the tire wheel 10 are attached to the hub flange 8 so as to overlap each other.
[0022]
And since the guide member 11 has the inner side reinforcement part 26 formed in the outer side guide part 24 via the bending part 25, even if it is a case where the load by a vehicle weight acts from the wheel side, The load can be fully supported.
[0023]
Further, the guide member 11 is a separate body from the outer ring member 2. For this reason, the outer ring member 2 only has a portion projecting in one of the radial direction and the axial direction. Therefore, it is not necessary to use a large-scale apparatus as in the prior art in the production (for example, hot forging), and Time can be reduced. The guide member 11 is made of a metal plate or tubular material by cold forging. For this reason, it can be manufactured at a low cost.
[0024]
FIG. 3 shows a second reference example . FIG. 3 is an enlarged sectional view of a main part showing a second reference example . In the second reference example , the guide member 11 is made of a metal plate-like or tubular material, in addition to the outer guide portion 24, the bent portion 25, the inner reinforcing portion 26, and the sealing portion 27, and the outer guide portion. A locking piece 32 that extends outward in the radial direction is formed at an end portion of the vehicle inner side 24 (right side in FIG. 3). The locking piece 32 is engaged with a locking portion 36 formed so as to further expand the diameter of the fitting portion 30 in the center hole 29 of the outer ring member 2.
[0025]
Further, the outer guide portion 24 has a large diameter portion 34 on the vehicle inner side and a small diameter portion 35 on the vehicle outer side, and a step portion 33 is formed between the large diameter portion 34 and the small diameter portion 35. . The large diameter part 34 and the small diameter part 35 are each formed in a parallel (concentric) annular shape.
[0026]
In addition, a plurality of slits (not shown) are formed in the circumferentially equidistant positions of the large diameter portion 34 from the locking pieces 32 to the large diameter portions 34 along the axial direction. The These slits enable the diameter to be reduced from the locking piece 32 to the large diameter portion 34. When the guide member 11 is attached to the outer ring member 2, the diameter is reduced from the locking piece 32 to the large diameter portion 34, and the outer guide portion 24 is fitted to the fitting portion 30. Since other configurations are the same as those of the first reference example , the same reference numerals are given and description thereof is omitted.
[0027]
In the second reference example , the rigidity of the guide member 11 is improved by the amount of the stepped portion 33 extending along the radial direction at an intermediate position in the axial direction of the outer guide portion 24, and the load is supported more reliably. Can do. Furthermore, since the locking piece 32 is formed on the guide member 11 and is locked to the locking portion 36 formed on the fitting portion 30, the pulling resistance of the guide member 11 can be increased.
[0028]
Next, a third reference example of the present invention will be described based on FIG. FIG. 4 is an enlarged cross-sectional view of a main part showing a third reference example of the present invention. In the third reference example, the axial intermediate position of the outer guide portion 24 of the guide member 11, in that the recess 37 along the circumferential direction is formed, different from the first reference example. On both sides of the concave portion 37, step portions 38 and 39 are formed along the radial direction, and the step portion 38 on the vehicle outer side is formed lower than the step portion 39 on the vehicle inner side. The portion 24 has a small diameter portion 40 on the vehicle outer side and a large diameter portion 41 on the vehicle inner side.
[0029]
The bottom portion 42 that forms the recess 37 has a smaller diameter than the small diameter portion 40 and is formed in an annular shape that is parallel (concentric) to the small diameter portion 40 and the large diameter portion 41. The distance along the axial direction from the vehicle outer side end surface of the guide member 11 to the recess 37 is formed equal to the width of the tire wheel 10, and the distance along the axial direction from the recess 37 to the hub flange 8 is the brake disc 9. It is formed equal to the width of. Since other configurations are the same as those of the first reference example , the same reference numerals are given and description thereof is omitted.
[0030]
In the third reference example , the rigidity of the guide member 11 is improved by the provision of the step portions 38 and 39 in the guide member 11, and the resistance force against the load can be increased.
[0031]
By the way, in general, a coating for preventing adhesion is applied to the outer peripheral surface of the guide portion (inlay portion) in order to prevent adhesion with the inner peripheral surface of the mounting hole 10a of the tire wheel 10. This becomes an increase factor of the manufacturing cost.
[0032]
However, in the third reference example of the present invention, the concave portion 37 is formed in the small-diameter portion 40, and the contact area between the outer peripheral surface of the small-diameter portion 40 and the inner peripheral surface of the mounting hole 10a is reduced as compared with the conventional example. . Thereby, since adhesion with the inner peripheral surface of the mounting hole 10a of the tire wheel 10 can be suppressed, the conventional coating for preventing adhesion can be omitted, and the manufacturing cost can be reduced. Other functions and effects are the same as those of the first reference example, and thus description thereof is omitted.
[0033]
Next, an embodiment of the present invention will be described based on FIG. 5 and FIG. The present embodiment is an example of preventing adhesion between the guide member 11 and the peripheral surface of the mounting hole 10a of the tire wheel 10, and a concave portion 87 recessed in the radial direction is provided along the axial direction with the outer guide portion 24. in which circumferentially disposed equidistant position of. Also in this case, the contact area of both members becomes small, the adhesion of both members can be prevented, and the coating for preventing adhesion can be omitted. In other parts, components having the same functions as those in each of the reference examples are given the same reference numerals, and the description thereof is omitted.
[0034]
The axle rolling bearing device 1 in each of the above reference examples and embodiments has been described as applied to the driven wheel side. On the other hand, the axle rolling bearing device 1 according to the fourth reference example of the present invention is applied to the drive wheel side.
[0035]
FIG. 7 is a cross-sectional view showing the overall configuration of an axle rolling bearing device according to a fourth reference example of the present invention.
[0036]
The axle rolling bearing device 1 in this reference example is provided on the vehicle body side so as to be non-rotatable around the shaft center, and is arranged concentrically in the radial direction on the outer ring member 50 so as to be rotatable around the shaft center. An inner ring member 51, and two rows of balls 53 and 54 that are rotatably disposed in an annular space 52 between the outer ring member 50 and the inner ring member 51. The balls 53 and 54 in each row are arranged at equidistant positions in the circumferential direction by a cage 55.
[0037]
On the outer peripheral surface of the outer ring member 50, a fixing flange 56 attached to the vehicle body (not shown) is formed so as to protrude outward in the radial direction.
[0038]
The inner ring member 51 is formed by a hub shaft 58 having a center hole 57 and an annular member 60 fitted into an annular recess 59 formed on the vehicle inner side of the hub shaft 58. The hub shaft 58 is integrally formed with a hub flange 61 projecting radially outward on the vehicle outer side. A fitting portion 62 having an inner diameter larger than that of the center hole 57 is formed on a vehicle outer side inner peripheral surface of the center hole 57 of the inner ring member 51.
[0039]
The inner ring raceway surface of the balls 53 in one row is formed on the outer circumferential surface of the hub shaft 58, and the inner ring raceway surface of the balls 54 in the other row is formed on the outer circumferential surface of the annular member 60. Outer ring raceway surfaces of the balls 53 and 54 in both rows are formed on the inner circumferential surface of the outer ring member 50. Sealing members 63 and 64 for sealing the annular space 52 on both sides are arranged on the vehicle outer side and the vehicle inner side of the annular space 52.
[0040]
An axle (drive shaft) 65 is assembled to the center hole 57 of the inner ring member 51 through a spline portion 66 so as to rotate integrally with the inner ring member 51, and a nut 67 is attached to a screw formed at the end of the axle 65. By being screwed, the annular member 60 is rotationally and integrally attached to the hub shaft 58, and a predetermined preload is applied to the balls 53 and 54 in each row.
[0041]
Further, the axle rolling bearing device 1 has mounting holes 68a and 69a formed at the centers of the brake disc 68 and the tire wheel 69 when the brake disc 68 and the tire wheel 69 are attached to the hub flange 61 in an overlapping manner. It has the guide member 70 which guides a surrounding surface.
[0042]
This guide member 70 is arranged on the outer side in the radial direction and has a cylindrical outer guide portion 72 having a guide surface 71 of the brake disc 68 and the tire wheel 69. It consists of a cylindrical inner reinforcing portion 74 that is bent toward the vehicle inner side via a bent portion 73 formed inward in the direction and arranged in parallel to the outer guide portion 72.
[0043]
The outer guide portion 72 and the inner reinforcement portion 74 are formed in parallel to each other, and the axial length of the inner reinforcement portion 74 is slightly shorter than the axial length of the outer guide portion 72. The guide member 70 is formed by cold forging or pressing using a metal plate-like or tubular material.
[0044]
Reference numeral 75 in the drawing denotes a hub bolt, and the hub bolt 75 is inserted into a mounting hole 76 formed in the brake disk 68 and the tire wheel 69 that are overlapped with the hub flange 61.
[0045]
The axle rolling bearing device 1 having the above-described configuration incorporates balls 53 and 54 into the outer ring member 50, incorporates the inner ring member 51, and screws a nut 67 onto a screw. Subsequently, the outer guide part 72 of the guide member 70 is assembled so as to be press-fitted into the fitting part 62.
[0046]
Subsequently, the mounting holes 68 a and 69 a formed at the centers of the brake disc 68 and the tire wheel 69 are guided to the outer guide portion 72 of the guide member 70, so that the brake disc 68 and the tire wheel 69 are connected to the hub flange 61. And install them one after another.
[0047]
In this reference example , as the axle 65 rotates about the axis, the inner ring member 51 rotates about the axis, and the brake disc 68 and the tire wheel 69 (tire) are driven to rotate about the axis. .
[0048]
Also in this reference example , since the guide member 71 has the inner reinforcing portion 74 formed on the outer guide portion 72 via the bent portion 73, the load due to the vehicle weight is applied from the wheel side. However, the load can be sufficiently supported.
[0049]
Although not shown in the figure, also in this reference example , the end cap is inserted into the open side (vehicle outer side) of the guide member 71, thereby ensuring the sealing performance for the bearing portion.
[0050]
In the fourth reference example , as shown in the second reference example or the third reference example , the outer guide part 72 is formed of a large diameter part and a small diameter part. May be. In this case, the rigidity of the guide member 70 can be further improved.
[0051]
【The invention's effect】
As is apparent from the above description, according to the present invention, the guide member for mounting the brake disc and the tire wheel is configured separately from the rotating wheel, so that the entire manufacturing cost is reduced and the guide is reduced. By providing the member with the inner reinforcing portion disposed radially inward of the outer guide portion, the guide member has high rigidity.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing an overall configuration of an axle rolling bearing device according to a first reference example of the present invention.
2 is an enlarged cross-sectional view of the main part of FIG.
FIG. 3 is an enlarged cross-sectional view of a main part showing a second reference example of the present invention.
FIG. 4 is an enlarged cross-sectional view of a main part showing a third reference example of the present invention.
FIG. 5 is an enlarged cross-sectional view of a main part showing an embodiment of the present invention .
FIG. 6 is an enlarged front view of the same.
FIG. 7 is a cross-sectional view showing the overall configuration of an axle rolling bearing device according to a fourth reference example of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Rolling bearing apparatus for axles 2 Outer ring member 3, 4 Inner ring member 8 Hub flange 9 Brake disk 10 Tire wheel 11 Guide member 23 Guide surface 24 Outer guide part 25 Bending part 26 Inner reinforcement part 27 Sealing part 30 Fit part 31 Gap

Claims (3)

固定輪と、この固定輪に径方向同心に配置されて軸心回りに回転自在に設けられる回転輪と、前記固定輪と回転輪との間に転動自在に設けられる転動体と、前記回転輪の軸方向一方側端部の外周部に、径方向外向きに突出するよう形成されるフランジと、環状のブレーキディスクおよび環状のタイヤホイールを前記フランジに取付ける際に案内する案内部材とを含み、
前記案内部材は、前記回転輪とは別体であるとともに、外周部に前記ブレーキディスクおよびタイヤホイールにおける中心穴用の案内面を有する筒状の外側案内部と、この外側案内部の軸方向一方側端部に径方向内方に向けて形成した折曲部を介して前記外側案内部の径方向内方に一体に形成される筒状の内側補強部とから成形され、前記外側案内部の軸方向他方側端部が、前記回転輪の軸方向一方側端部に取付けられており、前記外側案内部の軸方向一方側端部において前記タイヤホイールの取付け穴に対向して前記外側案内部の周方向等配位置に凹部が形成されている、転がり軸受装置。A fixed wheel, a rotating wheel disposed concentrically in the radial direction on the fixed wheel and provided to be rotatable about an axis, a rolling element provided to be rotatable between the fixed wheel and the rotating wheel, and the rotation A flange formed on the outer peripheral portion of one end in the axial direction of the wheel so as to protrude radially outward; and a guide member for guiding the annular brake disc and the annular tire wheel when the annular tire wheel is attached to the flange. ,
The guide member is separate from the rotating wheel, and has a cylindrical outer guide portion having a guide surface for a center hole in the brake disc and the tire wheel on an outer peripheral portion, and one axial direction of the outer guide portion. A cylindrical inner reinforcing portion integrally formed radially inward of the outer guide portion via a bent portion formed radially inward at a side end portion; The other end portion in the axial direction is attached to one end portion in the axial direction of the rotating wheel, and the outer guide portion faces the mounting hole of the tire wheel at the one end portion in the axial direction of the outer guide portion. A rolling bearing device in which recesses are formed at equally spaced positions in the circumferential direction . 請求項１記載の転がり軸受装置であって、
前記内側補強部は、前記回転輪と固定輪との間の環状空間を軸方向一方側で密封する密封部を有しており、
前記密封部の端面と前記固定輪の軸方向一方側端面との間に隙間を形成した、転がり軸受装置。The rolling bearing device according to claim 1,
The inner reinforcing portion has a sealing portion that seals an annular space between the rotating wheel and the fixed wheel on one side in the axial direction,
A rolling bearing device in which a gap is formed between an end surface of the sealing portion and an end surface on one axial side of the fixed ring. 請求項１または２記載の転がり軸受装置であって、
前記案内部材は冷間鍛造にて形成されている、転がり軸受装置。A rolling bearing device according to claim 1 or 2 ,
A rolling bearing device in which the guide member is formed by cold forging.
JP2002233422A 2002-08-09 2002-08-09 Rolling bearing device Expired - Fee Related JP4085736B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2002233422A JP4085736B2 (en) 2002-08-09 2002-08-09 Rolling bearing device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2002233422A JP4085736B2 (en) 2002-08-09 2002-08-09 Rolling bearing device

Publications (2)

Publication Number Publication Date
JP2004074815A JP2004074815A (en) 2004-03-11
JP4085736B2 true JP4085736B2 (en) 2008-05-14

Family

ID=32018554

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2002233422A Expired - Fee Related JP4085736B2 (en) 2002-08-09 2002-08-09 Rolling bearing device

Country Status (1)

Country Link
JP (1) JP4085736B2 (en)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4581615B2 (en) * 2004-10-13 2010-11-17 日本精工株式会社 Wheel supporting hub unit, raceway member of wheel supporting hub unit, and manufacturing method thereof
EP1647418B1 (en) 2004-10-13 2012-06-27 Nsk Ltd. Hub unit with wheel support and bearing ring, and method of manufacturing the hub unit
JP2007022175A (en) * 2005-07-13 2007-02-01 Jtekt Corp Hub unit and method for adjusting stiffness of hub unit
JP5040108B2 (en) 2005-12-08 2012-10-03 日本精工株式会社 Manufacturing method of bearing ring member constituting rolling bearing unit for supporting wheel
JP2007161037A (en) * 2005-12-12 2007-06-28 Mitsubishi Motors Corp Wheel assembling structure of vehicle
JP5017951B2 (en) * 2006-07-25 2012-09-05 日本精工株式会社 Hub unit bearing
US20100210369A1 (en) * 2009-02-17 2010-08-19 Jtekt Corporation Wheel bearing device and manufacturing method therefor
JP5765607B2 (en) * 2010-06-30 2015-08-19 いすゞ自動車株式会社 Vehicle wheel hub
JP6035588B2 (en) * 2013-01-18 2016-11-30 内山工業株式会社 Cap for bearing device

Also Published As

Publication number Publication date
JP2004074815A (en) 2004-03-11

Similar Documents

Publication Publication Date Title
JP4085736B2 (en) Rolling bearing device
JP2003094905A (en) Bearing device for axle
JP2000234624A5 (en)
JP4304771B2 (en) Wheel support hub unit and assembly method thereof
JP4239495B2 (en) Bearing device
JP2010089664A (en) Bearing device for wheel
JP4003446B2 (en) Bearing device
JP5087901B2 (en) Rolling bearing device for wheels
JP4078945B2 (en) Rolling bearing device
JP2008173995A (en) Bearing device for wheel
JP2016109183A (en) Outer ring for rolling bearing unit, and rolling bearing unit for supporting wheel
JP4042528B2 (en) Rolling bearing device
JP4333116B2 (en) Rolling bearing sealing device
JP2006105343A (en) Bearing device for wheel
JP4134872B2 (en) Rolling bearing device
JP2007278518A (en) Bearing device for vehicle
JP2004116716A (en) Rolling bearing device
JP2004116715A (en) Rolling bearing device
JP2006144966A (en) Rolling bearing device
JP4178312B2 (en) Rolling bearing device
JP2005299685A (en) Rolling bearing unit for wheel support
JP4639548B2 (en) Support body for vehicle bearing device
JP2004036851A (en) Rolling bearing device
WO2020225992A1 (en) Vehicle wheel bearing device
WO2003071147A1 (en) Rolling bearing unit for supporting wheel

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20050708

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20070516

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20070522

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20070720

A02 Decision of refusal

Free format text: JAPANESE INTERMEDIATE CODE: A02

Effective date: 20071002

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20071128

A911 Transfer of reconsideration by examiner before appeal (zenchi)

Free format text: JAPANESE INTERMEDIATE CODE: A911

Effective date: 20071207

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20080129

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20080211

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20110228

Year of fee payment: 3

R150 Certificate of patent or registration of utility model

Free format text: JAPANESE INTERMEDIATE CODE: R150

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20110228

Year of fee payment: 3

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20120229

Year of fee payment: 4

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20120229

Year of fee payment: 4

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130228

Year of fee payment: 5

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130228

Year of fee payment: 5

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20140228

Year of fee payment: 6

LAPS Cancellation because of no payment of annual fees