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JP3651196B2 - Rolling bearing unit for wheels - Google Patents

Rolling bearing unit for wheels Download PDF

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Publication number
JP3651196B2
JP3651196B2 JP21844697A JP21844697A JP3651196B2 JP 3651196 B2 JP3651196 B2 JP 3651196B2 JP 21844697 A JP21844697 A JP 21844697A JP 21844697 A JP21844697 A JP 21844697A JP 3651196 B2 JP3651196 B2 JP 3651196B2
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JP
Japan
Prior art keywords
inner ring
peripheral surface
cylindrical
ring member
outer peripheral
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
JP21844697A
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Japanese (ja)
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JPH1162951A (en
Inventor
裕也 宮崎
英男 大内
康允 水越
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NSK Ltd
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NSK Ltd
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Priority to JP21844697A priority Critical patent/JP3651196B2/en
Publication of JPH1162951A publication Critical patent/JPH1162951A/en
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Publication of JP3651196B2 publication Critical patent/JP3651196B2/en
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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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F16D1/108—Quick-acting couplings in which the parts are connected by simply bringing them together axially having retaining means rotating with the coupling and acting by interengaging parts, i.e. positive coupling
    • 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
    • F16C35/0635—Fixing them on the shaft the bore of the inner ring being of special non-cylindrical shape which co-operates with a complementary shape on the shaft, e.g. teeth, polygonal sections
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/0852—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping between the mating surfaces of the hub and shaft
    • F16D1/0858—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping between the mating surfaces of the hub and shaft due to the elasticity of the hub (including shrink fits)
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/187—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with all four raceways integrated on parts other than race rings, e.g. fourth generation hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F16D2001/103—Quick-acting couplings in which the parts are connected by simply bringing them together axially the torque is transmitted via splined connections

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Description

【０００１】
【発明の属する技術分野】
この発明に係る車輪用転がり軸受ユニットは、ＦＲ車（前置エンジン後輪駆動車）の後輪、ＦＦ車（前置エンジン前輪駆動車）の前輪、４ＷＤ車（四輪駆動車）の全輪等の駆動輪を、懸架装置に対して回転自在に支持する為に利用する。
【０００２】
【従来の技術】
車輪を懸架装置に対して回転自在に支持する為に、外輪と内輪とを転動体を介して回転自在に組み合わせた車輪用転がり軸受ユニットが、各種使用されている。又、操舵輪であると同時に駆動輪でもあるＦＦ車或は４ＷＤ車の前輪を支持する為の車輪用転がり軸受ユニットは、等速ジョイントと組み合わせて、車輪に付与された舵角に拘らず、駆動軸の回転を上記車輪に対して円滑に（等速性を確保して）伝達する必要がある。又、ＦＲ車、４ＷＤ車の後輪を支持する車輪用転がり軸受ユニットも、場合によっては等速ジョイントと組み合わせる場合がある。この様な等速ジョイントと組み合わせて、しかも比較的小型且つ軽量に構成できる車輪用転がり軸受ユニットとして従来から、特開平７−３１７７５４号公報に記載されたものが知られている。
【０００３】
図１２は、この公報に記載された従来構造を示している。車両への組み付け状態で、懸架装置に支持した状態で回転しない外輪１は、外周面にこの懸架装置に支持する為の第一の取付フランジ２を、内周面に複列の外輪軌道２３、２３を、それぞれ有する。上記外輪１の内側には、第一、第二の内輪部材３、４を組み合わせて成るハブ５を配置している。このうちの第一の内輪部材３は、外周面の一端寄り（図１２の左寄り）部分に車輪を支持する為の第二の取付フランジ６を、同じく他端寄り（図１２の右寄り）部分に第一の内輪軌道７を、それぞれ設けた円筒状に形成している。又、この第一の内輪部材３の一端面（図１２の左端面）には、上記第二の取付フランジ６に車輪を取り付ける際に、この車輪を上記ハブ５に対して位置決めする為の位置決め用円筒部２２を設けている。これに対して、駆動軸部材と一体に形成した上記第二の内輪部材４は、一端部（図１２の左端部）を上記第一の内輪部材３を外嵌固定する為の円筒部８とし、他端部（図１２の右端部）を等速ジョイントの外輪となるハウジング部９とし、中間部外周面に第二の内輪軌道１０を設けている。そして、上記各外輪軌道２３、２３と上記第一、第二の内輪軌道７、１０との間に、それぞれ複数個ずつの転動体１１、１１を設ける事により、上記外輪１の内側に上記ハブ５を、回転自在に支持している。
【０００４】
又、上記第一の内輪部材３の内周面と上記第二の内輪部材４の外周面との互いに整合する位置には、それぞれ係止溝１２、１３を形成すると共に、止め輪１４を、これら両係止溝１２、１３に掛け渡す状態で設けて、上記第一の内輪部材３が上記第二の内輪部材４から抜け出るのを防止している。更に、上記第二の内輪部材４の一端面（図１２の左端面）外周縁部と、上記第一の内輪部材３の内周面に形成した段部１５の内周縁部とに溶接１６を施して、上記第一、第二の内輪部材３、４同士を結合固定している。
【０００５】
一方、上記外輪１の両端開口部と上記ハブ５の中間部外周面との間には、ステンレス鋼板等の金属製で略円筒状のカバー１９ａ、１９ｂと、ゴム、エラストマー等の弾性材製で円環状のシールリング２０ａ、２０ｂとを設けている。これらカバー１９ａ、１９ｂ及びシールリング２０ａ、２０ｂは、上記複数の転動体１１、１１を設置した部分と外部とを遮断し、この部分に存在するグリースが外部に漏出するのを防止すると共に、この部分に雨水、塵芥等の異物が侵入する事を防止する。又、上記第二の内輪部材４の中間部内側には、この第二の内輪部材４の内側を塞ぐ隔板部２１を設けて、この第二の内輪部材４の剛性を確保すると共に、この第二の内輪部材４の先端（図１２の左端）開口からこの第二の内輪部材４の内側に入り込んだ異物が、前記ハウジング部９の内側に設けた等速ジョイント部分にまで達する事を防止している。
【０００６】
上述の様に構成する車輪用転がり軸受ユニットを車両に組み付ける際には、第一の取付フランジ２により外輪１を懸架装置に支持し、第二の取付フランジ６により駆動輪でもある前輪を第一の内輪部材３に固定する。又、エンジンによりトランスミッションを介して回転駆動される、図示しない駆動力伝達軸の先端部を、等速ジョイントを構成する内輪１７の内側にスプライン係合させる。自動車の走行時には、上記内輪１７の回転を、複数の玉１８を介して第二の内輪部材４を含むハブ５に伝達し、上記前輪を回転駆動する。
【０００７】
【発明が解決しようとする課題】
図１２に示した従来構造の場合には、第一、第二の内輪部材３、４同士の結合強度を確保する事が難しく、実用化が難しい。この理由は、次の通りである。第一、第二の内輪部材３、４同士の結合部には、自動車を走行させる為に大きなトルクが加わる。この様に大きなトルクに拘らず、上記結合部で上記第一、第二の内輪部材３、４同士が相対回転する事を防止する為には、上記第一、第二の内輪部材３、４同士を嵌合させただけでは不十分である。従って、実際には、上記第二の内輪部材４の一端面外周縁部と上記第一の内輪部材３の内周面に形成した段部１５の内周縁部との間に施した溶接１６部分により、上記トルクを支承する必要がある。
【０００８】
一方、上記溶接１６の近傍部分には第一の内輪軌道７が存在する。上記溶接１６部分の強度を十分に確保する為には、この溶接１６を、厚肉の全周肉盛り溶接にする事が好ましい。ところが、上記溶接１６を厚肉の全周肉盛り溶接にすると、上記第一の内輪軌道７部分に熱変形による歪みが発生し、車輪用転がり軸受ユニットとしての性能が悪化する。より具体的には、運転時に振動が発生し易くなる他、十分な耐久性を得られない。又、溶接時の熱により、上記第一の内輪軌道７の焼きが戻ってしまい、この第一の内輪軌道７の硬度を十分に維持できなくなり、この第一の内輪軌道７の転がり疲れ寿命が低下する。
本発明は、上述の様な不都合を解消して、小型且つ軽量に構成できる、実用的な車輪用転がり軸受ユニットを提供するものである。
【０００９】
【課題を解決するための手段】
本発明の車輪用転がり軸受ユニットは、前述した従来の車輪用転がり軸受ユニットと同様に、外輪と、第一、第二の内輪部材と、複数個の転動体とから成る。このうちの外輪は、外周面に懸架装置に支持する為の第一の取付フランジを、内周面に複列の外輪軌道を、それぞれ有する。又、上記第一の内輪部材は、上記外輪から突出した部分の外周面に車輪を支持する為の第二の取付フランジを、上記複列の外輪軌道のうちの一端寄り部分の外輪軌道と対向する部分の外周面に第一の内輪軌道を、それぞれ設けている。又、上記第二の内輪部材は、外周面の中間部若しくは一端寄り部分に第二の内輪軌道を、他端部に等速ジョイントの外輪となるハウジング部を、それぞれ有する。又、上記複数個の転動体は、上記各外輪軌道と上記第一、第二の内輪軌道との間にそれぞれ複数個ずつ設けている。更に、上記第一、第二の内輪部材のうちの一方の内輪部材の少なくとも軸方向一部に円筒状部分を、他方の内輪部材の少なくとも軸方向一部に円杆状部分を、それぞれ形成すると共に、これら円筒状部分と円杆状部分とを互いに嵌合させた状態で、上記第一、第二の内輪部材同士を結合している。
【００１０】
又、本発明の車輪用転がり軸受ユニットの場合には、上記円杆状部分の先端部に、外周面を円筒面とした円筒部を形成している。又、上記円筒状部分の内周面の少なくとも軸方向中央部には雌スプライン溝を、上記円杆状部分の外周面の少なくとも軸方向中央部にはこの雌スプライン溝と係合する雄スプライン溝を、それぞれ形成している。そして、上記第一の内輪部材と第二の内輪部材とは、上記雌スプライン溝と雄スプライン溝とを係合させた状態に組み合わせている。そして、この様に上記第一、第二の内輪部材同士を組み合わせた状態で、上記円筒部の先端部で外周面が円筒面である部分を直径方向外方に塑性変形させる事により形成したかしめ部により上記一方の内輪部材の一部を上記他方の内輪部材に向け、軸方向に抑え付けて、上記第一、第二の内輪部材同士を結合固定している。
特に、本発明の車輪用転がり軸受ユニットに於いては、上記円杆状部分の一端部外周面に、上記円筒状部分の一端部内周面とがたつきなく嵌合する一端側円筒面を形成し、上記円筒状部分の他端部内周面と上記円杆状部分の他端部外周面との少なくとも一方の周面に、相手側周面とがたつきなく嵌合する他端側円筒面を形成すると共に、上記一端側円筒面と上記円筒状部分の一端部内周面とを、この他端側円筒面と相手側周面とを、それぞれ嵌合させている。
【００１１】
【作用】
上述の様に構成する本発明の車輪用転がり軸受ユニットの場合には、第一、第二の内輪部材の分離防止は、かしめ部が図る。又、第一、第二の内輪部材同士の間でのトルク伝達は、雌スプライン溝と雄スプライン溝との係合部が行なう。従って、長期間に亙る使用によっても、上記第一の内輪部材と第二の内輪部材とを、相対回転を確実に防止した状態で結合したままに保持できて、等速ジョイントを介しての車輪の回転駆動を確実に行なえる。
又、一端側円筒面と円筒状部分の一端部内周面とを、他端側円筒面と相手側周面とを、それぞれ嵌合させている為、曲げ剛性を十分に大きくできる。
【００１２】
【発明の実施の形態】
図１〜４は、本発明の実施の形態の第１例を示している。使用時に懸架装置に取付固定して回転しない外輪１は、外周面に懸架装置に支持する為の第一の取付フランジ２を、内周面に複列の外輪軌道２３、２３を、それぞれ有する。この様な外輪１の直径方向内側には、ハブ５ａを配置している。このハブ５ａは、第一、第二の内輪部材３ａ、４ａを結合して成る。このうちの第一の内輪部材３ａは、上記外輪１から突出した部分（図示の例では軸方向に関して略中央部分）の外周面に、図示しない車輪を支持する為の第二の取付フランジ６を、上記複列の外輪軌道２３、２３のうちの一端寄り部分（図示の例では、車両への組み付け状態で幅方向外側となる外端寄り部分を言い、図１の左側部分）の外輪軌道２３と対向する部分（図１の右側部分）の外周面に第一の内輪軌道７を、それぞれ設けている。又、上記第二の内輪部材４ａは、外周面の中間部に第二の内輪軌道１０を、他端部（図示の例では、車両への組み付け状態で幅方向中央側となる内端部を言い、図１の右端部）に等速ジョイントの外輪となるハウジング部９を、それぞれ有する。そして、上記各外輪軌道２３、２３と上記第一、第二の内輪軌道７、１０との間にそれぞれ複数個ずつの転動体１１、１１を設けて、上記外輪１の内側に上記ハブ５ａを回転自在に支持している。
【００１３】
上記第一の内輪部材３ａと第二の内輪部材４ａとは、第一の内輪部材３ａの直径方向中央部に円筒状部分２４を、第二の内輪部材４ａの軸方向一端寄り半部（図１の左半部）に円杆状部分２５を、それぞれ形成している。又、上記ハウジング部９と上記円杆状部分２５との境界部分に、段部２７を形成している。上記第一、第二の内輪部材３ａ、４ａ同士は、上記円筒状部分２４と円杆状部分２５とを互いに嵌合させ、この円筒状部分２４の他端面（図１の右端面）を上記段部２７に突き当てた状態で、互いに結合固定している。
【００１４】
この為に、上記円杆状部分２５の先端部に円筒部８ａを形成している。そして、上記第一、第二の内輪部材３ａ、４ａ同士を結合固定する為に、上記円筒部８ａの先端部（図１の左端部）を直径方向外方に塑性変形させて、かしめ部２６としている。そして、このかしめ部２６を上記第一の内輪部材３ａの一端面（図１の左端面）内周縁部に当接させ、上記かしめ部２６により上記円筒状部分２４を上記段部２７に向け、強く抑え付けている。尚、この様に円筒状部分２４の他端面を上記段部２７に突き当てた状態で前記各転動体１１、１１に適正な予圧が付与される様に、上記段部２７の位置等を規制している。尚、上記第一の内輪部材３ａの一端面を上記段部２７に、全周に亙って密に当接自在とすべく、この段部２７の内周縁部の断面の曲率半径ｒ27（図４）を、上記円筒状部分２４の他端内周縁部の断面の曲率半径ｒ24（図２）よりも小さく（ｒ27＜ｒ24）して、当該部分の干渉を防止している。
【００１５】
又、上記円筒状部分２４の内周面には雌スプライン溝２８を、この内周面の全長に亙り形成している。この雌スプライン溝２８の歯底面の内接円の直径Ｒ1 （図２）は、全長に亙り変化しないが、歯先面の内接面の直径Ｒ2 、Ｒ3 は、途中で異ならせている。即ち、上記円筒状部分２４の一端寄り部分に於ける歯先面の直径Ｒ2 を、中間部及び他端寄り部分に於ける歯先面の直径Ｒ3 よりも少し小さく（Ｒ2 ＜Ｒ3 ）している。
【００１６】
一方、上記円杆状部分２５の外周面の軸方向中間部には、上記雌スプライン溝２８と係合する雄スプライン溝２９を形成している。又、この雄スプライン溝２９を軸方向両側から挟む、上記円杆状部分２５の一端部分及び他端部分に、１対の円筒状外周面部３０ａ、３０ｂを、それぞれ形成している。上記雄スプライン溝２９の歯先面の外接円の直径Ｄ1 （図４）は、上記雌スプライン溝２８の歯底面の内接円の直径Ｒ1 よりも小さく（Ｄ1 ＜Ｒ1 ）している。又、上記雄スプライン溝２９の歯底面の外接円の直径Ｄ2 は、上記雌スプライン溝２８の一端寄り部分に於ける歯先面の内接円の直径Ｒ2 よりも大きく、中間部及び他端寄り部分に於ける歯先面の内接円の直径Ｒ3 よりも小さく（Ｒ2 ＜Ｄ2 ＜Ｒ3 ）している。又、上記両円筒状外周面部３０ａ、３０ｂのうち、上記円杆状部分２５の一端部に形成した円筒状外周面部３０ａの外径Ｄ3 は、上記円筒状部分２４の一端寄り部分に於ける歯先面の直径Ｒ2 よりも僅かに大きく（Ｄ3 ＞Ｒ2 ）している。又、上記円杆状部分２５の他端部に形成した円筒状外周面部３０ｂの外径Ｄ4 は、上記円筒状部分２４の他端寄り部分に於ける歯先面の直径Ｒ3 よりも僅かに大きく（Ｄ 4 ＞Ｒ3 ）している。
【００１７】
それぞれを上述の様に構成した円筒状部分２４を有する第一の内輪部材３ａと円杆状部分２５を有する第二の内輪部材４ａとを結合固定する作業は、次の様にして行なう。結合する以前の状態では、前記円筒部８ａの先端部にかしめ部２６を形成せず、この円筒部８ａの先端部は、上記一端部側の円筒状外周面部３０ａと単一円筒面上に存在する。又、上記第一の内輪部材３ａの一端面に形成した、車輪挿入案内用の円筒部２２には蓋体３１を嵌着せず、上記第一の内輪部材３ａの一端側を開口させておく。この状態で上記円杆状部分２５を上記円筒状部分２４内に、この円筒状部分２４の他端開口側から、前記段部２７がこの円筒状部分２４の他端面に突き当たるまで押し込み、上記雌スプライン溝２８と雄スプライン溝２９とを係合させる。又、これら雌スプライン溝２８と雄スプライン溝２９とを係合させると共に、上記各円筒状外周面部３０ａ、３０ｂを上記雌スプライン溝２８の軸方向両端部の歯先面に、それぞれ締り嵌めにより内嵌する。
【００１８】
そして、この様に上記第一、第二の内輪部材３ａ、４ａ同士を組み合わせた状態で、上記円筒部８ａの先端部を直径方向外方に塑性変形させてかしめ部２６とし、上記第一、第二の内輪部材３ａ、４ａを結合する。最後に、上記円筒部２２に上記蓋体３１を嵌着する。この蓋体３１は、上記第一の内輪部材３ａの内側に雨水等が入り込み、上記雌スプライン溝２８と雄スプライン溝２９との係合部が錆びる事を防止する。尚、上述の様に第一、第二の内輪部材３ａ、４ａ同士を結合固定するのに先立って、前記外輪１の内側には、それぞれが保持器３２により保持された複数個の転動体１１、１１、並びにシールリング２０ａ、２０ｂを装着しておく。尚、本例の場合には、これら両シールリング２０ａ、２０ｂとして同種のものを使用できる様にすべく、上記外輪１の両端部の内径、並びに第一、第二の内輪部材３ａ、４ａの中間部外周面でこの外輪１の両端部内周面が対向する部分の外径及び形状を同じ（形状に就いては対称形）にしている。又、上記第二の内輪部材４ａの中間部で前記ハウジング部９の基部に対応する部分には土手状の突部３５を、全周に亙り形成している。そして、この突部３５の端縁部と上記外輪１の開口周縁部とを近接させて、当該部分にラビリンス隙間を形成し、上記外輪１の他端側開口部分のシール性向上を図っている。
【００１９】
又、上記円筒状部分２４の内周面部分で図２に斜格子で示した部分、並びに上記円杆状部分２５の外周面部分の一部で図４に斜格子で示した部分は、高周波焼き入れ等による硬化処理を施して、当該部分の硬度を必要とする程度にまで高めている。又、上記円杆状部分２５の中間部外周面で、上記雄スプライン溝２９と前記他端部側の円筒状外周面部３０ｂとの境界部分には、逃げ溝３３を、全周に亙って形成している。この逃げ溝３３の底部の直径Ｄ33は、上記雄スプライン溝２９の歯底面の外接円の直径Ｄ2 よりも小さく（Ｄ33＜Ｄ2 ）している。本例の場合には、この様な逃げ溝３３を形成する事により、上記雄スプライン溝２９の加工を容易に行なえる様にしている。
【００２０】
上述の様に構成する本例の車輪用転がり軸受ユニットの場合には、上記第一、第二の内輪部材３ａ、４ａ同士の分離防止は、かしめ部２６が図る。又、これら第一、第二の内輪部材３ａ、４ａ同士の間でのトルク伝達は、雌スプライン溝２８と雄スプライン溝２９との係合部が行なう。更に、旋回時に加わるモーメント荷重は、一端側、他端側両円筒面部である円筒状外周面部３０ａ、３０ｂと上記雌スプライン溝２８の両端部の歯先面との嵌合部が支承する。従って、長期間に亙る使用によっても、上記第一の内輪部材３ａと第二の内輪部材４ａとを、相対回転を確実に防止した状態で結合したままに保持できて、等速ジョイントを介しての車輪の回転駆動を確実に行なえる。
【００２１】
即ち、上記かしめ部２６には、上記第一、第二の内輪部材３ａ、４ａ同士を結合する為の力が加わるのみで、これら両内輪部材３ａ、４ａ同士の間で伝達するトルクに基づく力や、上記モーメント荷重に基づく力が加わる事はない。この為、上記かしめ部２６に、このかしめ部２６の径を縮める方向の力が加わる事はなく、このかしめ部２６による上記両内輪部材３ａ、４ａ同士の結合力を、長期間に亙って十分に保持できる。又、上記雌スプライン溝２８と雄スプライン溝２９との係合部は、上記第一、第二の内輪部材３ａ、４ａ同士の間でのトルク伝達のみを行ない、上記モーメント荷重を支承する事はないので、上記両内輪部材３ａ、４ａを結合して成るハブ５ａの曲げ剛性を十分に確保できる。この点に就いて、図５〜６を参照しつつ説明する。
【００２２】
車輪用転がり軸受ユニットを組み込んだ自動車の旋回時に上記ハブ５ａには、上記第一の内輪部材３ａの中心軸と上記第二の内輪部材４ａの中心軸をずらせようとする方向（曲げ方向）のモーメント荷重が加わる。このモーメント荷重は、前記円筒状部分２４と前記円杆状部分２５との嵌合部が支承する。本例の場合、上記モーメント荷重を、軸方向に離隔した位置に設けた１対の円筒状外周面部３０ａ、３０ｂと、上記雌スプライン溝２８の両端部の歯先面との、１対の嵌合部が支承する。これら１対の嵌合部は、スプライン係合部を挟んで軸方向両側に配置しているので、これら両嵌合部の中心同士の距離Ｌ（図５）は十分に大きく、しかも嵌合面の一部が上記モーメント荷重の作用方向に対し直角方向に存在する為、上記曲げ剛性を大きくできる。これに対して、上記円筒状部分２４と上記円杆状部分２５との嵌合部に、（上記１対の円筒状外周面部３０ａ、３０ｂを設ける事なく）全長に亙って雌スプライン溝２８と雄スプライン溝２９とを形成した場合には、上記曲げ剛性を大きくできない。
【００２３】
即ち、上記雌スプライン溝２８と雄スプライン溝２９との係合を可能にすべく、これら雌スプライン溝２８及び雄スプライン溝２９の歯底面と歯先面との間には、図６に示す様に、多少の隙間３４ａ、３４ｂを介在させなければならない。又、上記雌スプライン溝２８と雄スプライン溝２９との係合に基づき大きなトルクを伝達可能にする為、これら両スプライン溝２８、２９の円周方向両側面と直径方向との傾斜角度θは小さくしなければならない。従って、上記雌スプライン溝２８と雄スプライン溝２９との係合部のラジアル荷重に対する剛性は、あまり大きくできない。この結果、上述の様に、上記円筒状部分２４と上記円杆状部分２５との嵌合部に、全長に亙って雌スプライン溝２８と雄スプライン溝２９とを形成した場合には、上記曲げ剛性を大きくできない。本例の場合には、上記１対の円筒状外周面部３０ａ、３０ｂを設ける事により、上記曲げ剛性を十分に大きくしたものである。
【００２４】
次に、図７〜１０は、本発明の実施の形態の第２例を示している。本例の場合には、上述した第１例の場合とは逆に、第一の内輪部材３ｂの内半部（図７の右半部）に円杆状部分２５ａを、第二の内輪部材４ｂの外半部（図７の左半部）に円筒状部分２４ａを、それぞれ形成している。そして、上記円杆状部分２５ａの先端部（図７の右端部）に形成したかしめ部２６ａを、上記第二の内輪部材４ｂの中間部内周面に形成した段部３６に向けかしめ付けて、上記第一、第二の内輪部材３ｂ、４ｂ同士を結合固定している。円杆状部分２５ａと円筒状部分２４ａとの設置位置を逆にし、その結果、上記両内輪部材３ｂ、４ｂ同士の結合部の構成各部の位置が、車両の幅方向に関して内外逆になった以外の構成及び作用は、上述した第１例の場合と同様であるから、同等部分には同一符号を付して、重複する説明を省略する。
【００２５】
次に、図１１は、本発明の実施の形態の第３例を示している。本例の場合には、外輪１の一端部である内端部（車両への取付状態で幅方向中央側の端部を言い、図１１の右端部）に形成した嵌合部３７を、懸架装置を構成するナックルの取付孔（図示せず）に嵌合させる際に、第一の内輪部材３ｃと第二の内輪部材４ｃとから成るハブ５ｂの内半部（図１１の右半部）を上記ナックルの取付孔に挿通自在としている。この為に、上記第二の内輪部材４ｃの一端寄り半部である内半部に形成したハウジング部９ａの外径Ｄ9aを、上記嵌合部３７の外径Ｄ37以下（Ｄ9a≦Ｄ37）としている。又、上記ハウジング部９ａの開口端部には、より小径の取付部３８を全周に亙って形成し、この取付部３８に、ステンレス鋼板等、耐食性を有する金属板から成る結合筒３９の基半部４０を外嵌固定している。この結合筒３９は、大径の基半部４０と小径の先半部４１とを段部４２で連続させる事により、断面クランク型で全体を円筒状に形成している。この様な結合筒３９は、上記段部４２を上記取付部３８の先端面に突き当て、上記基半部４０の先端縁部を上記取付部３８の基端部（図１１の左端部）外周面に形成した係止溝４３にかしめ付ける事により、上記第二の内輪部材４ｃの内端部に固定している。尚、上記基半部４０の内周面と上記取付部３８の外周面との間にはＯリング４４を設けて、これら両周面同士の間を通じて、上記第二の内輪部材４ｃ内に雨水等が入り込む事を防止している。
【００２６】
車両への組み付け状態で、上述の様な結合筒３９の先半部４１には、防塵・防水の為のブーツ４５の端部を外嵌固定する。即ち、このブーツ４５の端部を上記先半部４１に外嵌し、更にこの端部の外周面をバンド４６で抑え付けている。上記先半部４１の中間部外周面には凹溝４７若しくは突条を形成し、この凹溝４７若しくは突条と上記ブーツ４５の端部内周面とを係合させて、このブーツ４５の端部が上記先半部４１から外れる事を防止している。尚、上記結合筒３９の外径Ｄ39も、上記嵌合部３７の外径Ｄ37以下（Ｄ39≦Ｄ37）としている。尚、図示はしないが、等速ジョイントは車輪側だけでなく、減速機（デファレンシャルギア）側にも用いる。これら２個の等速ジョイントと軸受とを一体にした状態で車両に組み付ければ、自動車メーカーでの組立てが容易となる。この場合には、ブーツ４５及びバンド４６も組み付けた状態となるので、上記バンド４６の外接円の直径も、上記嵌合部３７の外径Ｄ37以下にする必要がある。又、上記取付部３８の内周面は、等速ジョイントのボール溝の交点付近で曲線形状として、等速ジョイントへのボールの組み込みが可能となる範囲で、上記係止溝４３部分の肉厚を極力厚くしている。尚、本例の様に結合筒先端までの長さが長くなると、等速ジョイントのジョイント角を大きくできないが、後輪の場合には大きなジョイント角を要求されないので、特に後輪用として本例は、外径寸法を大きくしない為の有効な構造である。
【００２７】
更に、図示の例では、前記ハウジング部９ａの奥端部に円形凹部４８を、このハウジング部９ａと同心に形成している。この円形凹部４８の内径Ｒ48は、前記第一の内輪部材３ｃと第二の内輪部材４ｃとを結合すべく、この第二の内輪部材４ｃの外端部に形成したかしめ部２６の外径Ｄ26よりも大きい（Ｒ48＞Ｄ26）。この様な円形凹部４８には、上記かしめ部２６の形成作業時に、受台（図示せず）を嵌合させて、このかしめ部２６を形成する際に上記第二の内輪部材４ｃに加わるスラスト荷重を受ける。上記内径Ｒ48を上記外径Ｄ26よりも大きくしている為、上記かしめ部２６の加工を揺動かしめにより行ない、上記スラスト荷重が上記第二の内輪部材４ｃの円周方向の一部にのみ加わった場合にも、この第二の内輪部材４ｃが傾斜する事を確実に防止して、良質のかしめ部２６を形成できる。その他の構成及び作用は、前述した第１例と同様であるから、同等部分には同一符号を付して、重複する説明を省略する。
【００２８】
【発明の効果】
本発明の車輪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、小型且つ軽量に構成できて、しかも実用的な車輪用転がり軸受ユニットを提供できる。
【図面の簡単な説明】
【図１】本発明の実施の形態の第１例を示す断面図。
【図２】図１のＡ部から第一の内輪部材のみを取り出して示す部分断面図。
【図３】図２の左方から見た図。
【図４】図１のＡ部から第二の内輪部材のみを取り出して示す部分断面図。
【図５】モーメント荷重に対する剛性を確保できる状態を説明する為の部分断面図。
【図６】同じく図５のＢ−Ｂ断面図。
【図７】本発明の実施の形態の第２例を示す断面図。
【図８】図７のＣ部から第一の内輪部材のみを取り出して示す部分断面図。
【図９】図７のＣ部から第二の内輪部材のみを取り出して示す部分断面図。
【図１０】図９の右方から見た図。
【図１１】本発明の実施の形態の第３例を示す部分断面図。
【図１２】従来構造の１例を示す部分断面図。
【符号の説明】
１ 外輪
２ 第一の取付フランジ
３、３ａ、３ｂ、３ｃ 第一の内輪部材
４、４ａ、４ｂ、４ｃ 第二の内輪部材
５、５ａ、５ｂ ハブ
６ 第二の取付フランジ
７ 第一の内輪軌道
８、８ａ 円筒部
９、９ａ ハウジング部
１０ 第二の内輪軌道
１１ 転動体
１２ 係止溝
１３ 係止溝
１４ 止め輪
１５ 段部
１６ 溶接
１７ 内輪
１８ 玉
１９ａ、１９ｂ カバー
２０ａ、２０ｂ シールリング
２１ 隔板部
２２ 円筒部
２３ 外輪軌道
２４、２４ａ 円筒状部分
２５、２５ａ 円杆状部分
２６、２６ａ かしめ部
２７ 段部
２８ 雌スプライン溝
２９ 雄スプライン溝
３０ａ、３０ｂ 円筒状外周面部
３１ 蓋体
３２ 保持器
３３ 逃げ溝
３４ａ、３４ｂ 隙間
３５ 突部
３６ 段部
３７ 嵌合部
３８ 取付部
３９ 結合筒
４０ 基半部
４１ 先半部
４２ 段部
４３ 係止溝
４４ Ｏリング
４５ ブーツ
４６ バンド
４７ 凹溝
４８ 円形凹部[0001]
BACKGROUND OF THE INVENTION
The rolling bearing unit for wheels according to the present invention includes a rear wheel of an FR vehicle (front engine rear wheel drive vehicle), a front wheel of an FF vehicle (front engine front wheel drive vehicle), and all wheels of a 4WD vehicle (four wheel drive vehicle). The drive wheels are used to rotatably support the suspension device.
[0002]
[Prior art]
In order to rotatably support a wheel with respect to a suspension device, various types of wheel rolling bearing units are used in which an outer ring and an inner ring are rotatably combined via rolling elements. In addition, the wheel rolling bearing unit for supporting the front wheel of the FF vehicle or 4WD vehicle which is the steering wheel as well as the driving wheel is combined with the constant velocity joint, regardless of the steering angle given to the wheel. It is necessary to transmit the rotation of the drive shaft to the wheel smoothly (with a constant speed). Also, a rolling bearing unit for a wheel that supports the rear wheel of the FR vehicle or 4WD vehicle may be combined with a constant velocity joint in some cases. Conventionally, a rolling bearing unit for a wheel that can be combined with such a constant velocity joint and can be made relatively small and light is disclosed in JP-A-7-317754.
[0003]
FIG. 12 shows a conventional structure described in this publication. The outer ring 1 that does not rotate while being supported by the suspension device in the state of being mounted on the vehicle has a first mounting flange 2 for supporting the suspension device on the outer peripheral surface, and a double row outer ring raceway 23 on the inner peripheral surface. 23 respectively. A hub 5 formed by combining first and second inner ring members 3 and 4 is disposed inside the outer ring 1. Of these, the first inner ring member 3 has a second mounting flange 6 for supporting the wheel on one end (to the left in FIG. 12) of the outer peripheral surface, and also on the other end (to the right in FIG. 12). The first inner ring raceway 7 is formed in a cylindrical shape provided. Further, on one end surface (left end surface in FIG. 12) of the first inner ring member 3, positioning is performed for positioning the wheel with respect to the hub 5 when the wheel is mounted on the second mounting flange 6. A cylindrical portion 22 is provided. On the other hand, the second inner ring member 4 formed integrally with the drive shaft member has one end portion (left end portion in FIG. 12) as a cylindrical portion 8 for externally fitting and fixing the first inner ring member 3. The other end portion (the right end portion in FIG. 12) is a housing portion 9 that becomes the outer ring of the constant velocity joint, and the second inner ring raceway 10 is provided on the outer peripheral surface of the intermediate portion. A plurality of rolling elements 11, 11 are provided between the outer ring raceways 23, 23 and the first and second inner ring raceways 7, 10, so that the hub is provided inside the outer ring 1. 5 is rotatably supported.
[0004]
In addition, locking grooves 12 and 13 are formed at positions where the inner peripheral surface of the first inner ring member 3 and the outer peripheral surface of the second inner ring member 4 are aligned with each other, and a retaining ring 14 is provided. The first inner ring member 3 is provided in a state of being stretched over both the locking grooves 12 and 13 to prevent the first inner ring member 3 from coming out of the second inner ring member 4. Furthermore, welding 16 is applied to the outer peripheral edge of one end surface (left end surface in FIG. 12) of the second inner ring member 4 and the inner peripheral edge of the step portion 15 formed on the inner peripheral surface of the first inner ring member 3. Thus, the first and second inner ring members 3 and 4 are coupled and fixed to each other.
[0005]
On the other hand, between the opening at both ends of the outer ring 1 and the outer peripheral surface of the intermediate portion of the hub 5 are made of a metal and substantially cylindrical cover 19a, 19b such as a stainless steel plate, and an elastic material such as rubber or elastomer. Annular seal rings 20a and 20b are provided. The covers 19a and 19b and the seal rings 20a and 20b block the portion where the plurality of rolling elements 11 and 11 are installed from the outside, prevent the grease existing in this portion from leaking to the outside, Prevents foreign matter such as rainwater and dust from entering the area. Further, on the inner side of the intermediate portion of the second inner ring member 4, a partition plate portion 21 for closing the inner side of the second inner ring member 4 is provided to ensure the rigidity of the second inner ring member 4, and this The foreign matter that has entered the inside of the second inner ring member 4 from the opening (left end in FIG. 12) of the second inner ring member 4 is prevented from reaching the constant velocity joint provided inside the housing portion 9. doing.
[0006]
When the rolling bearing unit for a wheel configured as described above is assembled to a vehicle, the outer ring 1 is supported on the suspension device by the first mounting flange 2, and the front wheel that is also the driving wheel is first supported by the second mounting flange 6. The inner ring member 3 is fixed. Further, a tip portion of a driving force transmission shaft (not shown) that is rotationally driven by the engine via the transmission is spline-engaged with the inner side of the inner ring 17 constituting the constant velocity joint. During traveling of the automobile, the rotation of the inner ring 17 is transmitted to the hub 5 including the second inner ring member 4 via the plurality of balls 18 to rotationally drive the front wheel.
[0007]
[Problems to be solved by the invention]
In the case of the conventional structure shown in FIG. 12, it is difficult to ensure the bonding strength between the first and second inner ring members 3, 4 and it is difficult to put it to practical use. The reason for this is as follows. A large torque is applied to the connecting portion between the first and second inner ring members 3 and 4 in order to drive the automobile. In order to prevent the first and second inner ring members 3 and 4 from rotating relative to each other at the coupling portion regardless of such a large torque, the first and second inner ring members 3 and 4 are prevented. Simply fitting them together is not sufficient. Therefore, in actuality, the weld 16 portion applied between the outer peripheral edge of the one end surface of the second inner ring member 4 and the inner peripheral edge of the step portion 15 formed on the inner peripheral surface of the first inner ring member 3. Therefore, it is necessary to support the torque.
[0008]
On the other hand, the first inner ring raceway 7 exists in the vicinity of the weld 16. In order to sufficiently secure the strength of the weld 16 portion, it is preferable that the weld 16 is a thick all-around weld. However, if the welding 16 is thick all-around welding, the first inner ring raceway 7 is distorted by thermal deformation, and the performance as a rolling bearing unit for a wheel is deteriorated. More specifically, vibration is likely to occur during operation, and sufficient durability cannot be obtained. Further, the heat of the welding causes the baking of the first inner ring raceway 7 to return, so that the hardness of the first inner ring raceway 7 cannot be sufficiently maintained, and the rolling fatigue life of the first inner ring raceway 7 is increased. descend.
The present invention provides a practical rolling bearing unit for a wheel that eliminates the above-mentioned disadvantages and can be configured to be small and light.
[0009]
[Means for Solving the Problems]
The wheel rolling bearing unit of the present invention includes an outer ring, first and second inner ring members, and a plurality of rolling elements, as in the conventional wheel rolling bearing unit described above. Out of these, the outer ring has a first mounting flange for supporting the suspension device on the outer peripheral surface, and a double row outer ring raceway on the inner peripheral surface. The first inner ring member has a second mounting flange for supporting a wheel on an outer peripheral surface of a portion protruding from the outer ring, and is opposed to an outer ring raceway at a portion near one end of the double row outer ring raceway. The first inner ring raceway is provided on the outer peripheral surface of the portion to be performed. The second inner ring member has a second inner ring raceway at an intermediate portion or a portion near one end of the outer peripheral surface, and a housing portion serving as an outer ring of a constant velocity joint at the other end. The plurality of rolling elements are respectively provided between the outer ring raceways and the first and second inner ring raceways. Furthermore, a cylindrical portion is formed on at least a part in the axial direction of one inner ring member of the first and second inner ring members, and a conical portion is formed on at least a part in the axial direction of the other inner ring member. At the same time, the first and second inner ring members are joined together in a state in which the cylindrical portion and the circular ring-shaped portion are fitted to each other.
[0010]
  In the case of the rolling bearing unit for wheels of the present invention,, At the tip of the above circular bowlThe outer peripheral surface is a cylindrical surfaceA cylindrical portion is formed. A female spline groove is formed at least in the axial central portion of the inner peripheral surface of the cylindrical portion, and a male spline groove engaged with the female spline groove is provided in at least the axial central portion of the outer peripheral surface of the circular ring-shaped portion. Are formed respectively. The first inner ring member and the second inner ring member are combined in a state where the female spline groove and the male spline groove are engaged. And in the state which combined the said 1st and 2nd inner ring members in this way, the front-end | tip part of the said cylindrical partWhere the outer peripheral surface is a cylindrical surfaceA part of the one inner ring member is directed toward the other inner ring member by a caulking portion formed by plastic deformation of the first inner ring member and the second inner ring member. Is fixed.
  In particular, in the rolling bearing unit for a wheel according to the present invention, one end side cylindrical surface is formed on the outer peripheral surface of the one end portion of the circular ring-shaped portion so that the one end portion inner peripheral surface of the cylindrical portion fits smoothly. And the other end side cylindrical surface that fits to the other side peripheral surface without a backlash with at least one of the other end portion inner peripheral surface of the cylindrical portion and the other end portion outer peripheral surface of the circular ring shaped portion. The one end side cylindrical surface and the one end inner peripheral surface of the cylindrical portion are fitted to the other end side cylindrical surface and the mating peripheral surface, respectively.
[0011]
[Action]
  In the case of the rolling bearing unit for a wheel of the present invention configured as described above, the caulking portion is intended to prevent separation of the first and second inner ring members. Further, torque transmission between the first and second inner ring members is performed by an engaging portion between the female spline groove and the male spline groove. Therefore, even when used over a long period of time, the first inner ring member and the second inner ring member can be held in a state where relative rotation is reliably prevented, and the wheel via the constant velocity joint can be held. Can be reliably rotated.
  Further, since the one end side cylindrical surface and the one end inner peripheral surface of the cylindrical portion are fitted to the other end side cylindrical surface and the counterpart peripheral surface, the bending rigidity can be sufficiently increased.
[0012]
DETAILED DESCRIPTION OF THE INVENTION
1 to 4 show a first example of an embodiment of the present invention. The outer ring 1 that is fixedly attached to the suspension device and does not rotate during use has a first attachment flange 2 for supporting the suspension device on the outer peripheral surface, and double-row outer ring raceways 23 and 23 on the inner peripheral surface. A hub 5a is disposed inside the outer ring 1 in the diameter direction. The hub 5a is formed by connecting first and second inner ring members 3a and 4a. Of these, the first inner ring member 3a has a second mounting flange 6 for supporting a wheel (not shown) on the outer peripheral surface of a portion protruding from the outer ring 1 (in the example shown, a substantially central portion with respect to the axial direction). The outer ring raceway 23 of the double row outer ring raceways 23, 23 (in the example shown, the outer end raceway portion that is the outer end portion that is the outer side in the width direction in the assembled state in the vehicle and is the left side portion in FIG. 1). The first inner ring raceway 7 is provided on the outer peripheral surface of the portion (right side portion in FIG. 1) facing each other. The second inner ring member 4a has a second inner ring raceway 10 in the middle of the outer peripheral surface, and the other end (in the example shown, the inner end that is the center in the width direction when assembled to the vehicle). In other words, the housing 9 is provided on the outer ring of the constant velocity joint at the right end of FIG. A plurality of rolling elements 11, 11 are provided between the outer ring raceways 23, 23 and the first and second inner ring raceways 7, 10, and the hub 5 a is placed inside the outer ring 1. It is supported rotatably.
[0013]
The first inner ring member 3a and the second inner ring member 4a have a cylindrical portion 24 at the diametrical central portion of the first inner ring member 3a and a half portion closer to one axial end of the second inner ring member 4a (see FIG. The left half of 1) is formed with a conical portion 25. In addition, a stepped portion 27 is formed at the boundary portion between the housing portion 9 and the circular bowl-shaped portion 25. The first and second inner ring members 3a, 4a are configured such that the cylindrical portion 24 and the circular ring-shaped portion 25 are fitted to each other, and the other end surface (right end surface in FIG. 1) of the cylindrical portion 24 is In a state of abutting against the stepped portion 27, they are coupled and fixed to each other.
[0014]
For this purpose, a cylindrical portion 8 a is formed at the tip of the circular bowl-shaped portion 25. Then, in order to couple and fix the first and second inner ring members 3a, 4a, the distal end portion (left end portion in FIG. 1) of the cylindrical portion 8a is plastically deformed outward in the diametrical direction, and the caulking portion 26 is obtained. It is said. Then, the caulking portion 26 is brought into contact with an inner peripheral edge portion of one end surface (the left end surface in FIG. 1) of the first inner ring member 3a, and the caulking portion 26 directs the cylindrical portion 24 toward the step portion 27. It is strongly suppressed. The position of the stepped portion 27 is regulated so that an appropriate preload is applied to each of the rolling elements 11, 11 with the other end surface of the cylindrical portion 24 being in contact with the stepped portion 27 in this way. doing. It should be noted that the radius of curvature r of the cross section of the inner peripheral edge portion of the step portion 27 is such that one end surface of the first inner ring member 3a can be in close contact with the step portion 27 over the entire circumference.27(FIG. 4), the radius of curvature r of the cross section of the inner peripheral edge of the other end of the cylindrical portion 24.twenty fourSmaller than (Fig. 2) (r27<Rtwenty four) To prevent interference of the part.
[0015]
A female spline groove 28 is formed on the inner peripheral surface of the cylindrical portion 24 over the entire length of the inner peripheral surface. The diameter R of the inscribed circle on the bottom surface of the female spline groove 281 (FIG. 2) does not change over the entire length, but the diameter R of the inscribed surface of the tooth tip surface2 , RThree Is different on the way. That is, the diameter R of the tooth tip surface in the portion near one end of the cylindrical portion 24.2 The diameter R of the tooth tip surface at the middle part and the part near the other endThree A little smaller than (R2 <RThree )doing.
[0016]
  On the other hand, a male spline groove 29 that engages with the female spline groove 28 is formed in the axially intermediate portion of the outer peripheral surface of the circular bowl-shaped portion 25. In addition, a pair of cylindrical outer peripheral surface portions 30a and 30b are formed on one end portion and the other end portion of the circular ring-shaped portion 25 sandwiching the male spline groove 29 from both sides in the axial direction. Diameter D of circumscribed circle of tooth tip surface of male spline groove 291 (FIG. 4) is the diameter R of the inscribed circle of the tooth bottom surface of the female spline groove 28.1 Smaller than (D1 <R1 )doing. The diameter D of the circumscribed circle of the tooth bottom surface of the male spline groove 292 Is the diameter R of the inscribed circle of the tooth tip surface at a portion near one end of the female spline groove 28.2 Larger than the diameter R of the inscribed circle of the tooth tip at the middle and the other endThree Smaller than (R2 <D2 <RThree )doing. Also, the outer diameter D of the cylindrical outer peripheral surface portion 30a formed at one end of the circular bowl-shaped portion 25 of the both cylindrical outer peripheral surface portions 30a and 30b.Three Is the diameter R of the tooth tip surface at a portion near one end of the cylindrical portion 24.2 Slightly larger than (DThree > R2 )doing. Further, the outer diameter D of the cylindrical outer peripheral surface portion 30b formed at the other end portion of the circular bowl-shaped portion 25.Four Is the diameter R of the tooth tip surface at the other end portion of the cylindrical portion 24.Three Slightly larger than (D Four > RThree )doing.
[0017]
  A first inner ring member 3a having a cylindrical portion 24 each configured as described above;Circle-shaped partThe operation of connecting and fixing the second inner ring member 4a having 25 is performed as follows. In the state before the coupling, the caulking portion 26 is not formed at the distal end portion of the cylindrical portion 8a, and the distal end portion of the cylindrical portion 8a exists on the cylindrical outer peripheral surface portion 30a on the one end side and the single cylindrical surface. To do. Further, the lid 31 is not fitted on the wheel insertion guide cylindrical portion 22 formed on one end surface of the first inner ring member 3a, and one end side of the first inner ring member 3a is opened. In this state, the circular ring-shaped portion 25 is pushed into the cylindrical portion 24 from the other end opening side of the cylindrical portion 24 until the stepped portion 27 abuts against the other end surface of the cylindrical portion 24, and the female portion The spline groove 28 and the male spline groove 29 are engaged. In addition, the female spline groove 28 and the male spline groove 29 are engaged with each other, and the cylindrical outer peripheral surface portions 30a and 30b are respectively fitted into the tooth tip surfaces of both ends in the axial direction of the female spline groove 28 by interference fitting. Fit.
[0018]
  And in the state which combined the said 1st, 2nd inner ring members 3a and 4a in this way, the front-end | tip part of the said cylindrical part 8a is plastically deformed to diameter direction outward, and it is set as the crimp part 26, said 1st, The second inner ring members 3a and 4a are coupled. Finally, the lid 31 is fitted to the cylindrical portion 22. The lid 31 prevents rainwater or the like from entering the first inner ring member 3a and rusting of the engaging portion between the female spline groove 28 and the male spline groove 29. In addition, prior to the first and second inner ring members 3a and 4a being coupled and fixed as described above, a plurality of rolling elements 11 each held by a cage 32 are provided inside the outer ring 1. 11, and seal rings 20a, 20b are mounted. In the case of this example, in order to be able to use the same kind of both the seal rings 20a and 20b, the inner diameters of both ends of the outer ring 1 and the first and secondInner ring memberThe outer diameters and shapes of the outer peripheral surfaces of the intermediate portions 3a and 4a that are opposed to the inner peripheral surfaces of both ends of the outer ring 1 are the same (symmetrical in terms of shape). Further, a bank-like protrusion 35 is formed over the entire circumference at a portion corresponding to the base portion of the housing portion 9 in the intermediate portion of the second inner ring member 4a. And the edge part of this protrusion 35 and the opening peripheral part of the said outer ring | wheel 1 are adjoined, the labyrinth clearance gap is formed in the said part, and the sealing performance improvement of the other end side opening part of the said outer ring | wheel 1 is aimed at. .
[0019]
Further, the portion indicated by the oblique lattice in FIG. 2 on the inner peripheral surface portion of the cylindrical portion 24 and the portion indicated by the oblique lattice in FIG. A hardening process such as quenching is performed to increase the hardness of the part to a necessary level. In addition, on the outer peripheral surface of the intermediate portion of the circular bowl-shaped portion 25, a clearance groove 33 is formed over the entire circumference at the boundary portion between the male spline groove 29 and the cylindrical outer peripheral surface portion 30b on the other end side. Forming. Diameter D of the bottom of the escape groove 3333Is the diameter D of the circumscribed circle of the tooth bottom surface of the male spline groove 292 Smaller than (D33<D2 )doing. In this example, the male spline groove 29 can be easily processed by forming such a relief groove 33.
[0020]
  Configure as aboveThis exampleIn the case of this wheel rolling bearing unit, the caulking portion 26 prevents the first and second inner ring members 3a, 4a from being separated from each other. Further, torque transmission between the first and second inner ring members 3a, 4a is performed by the engaging portion between the female spline groove 28 and the male spline groove 29. Furthermore, the moment load applied at the time of turning is supported by the fitting portions between the cylindrical outer peripheral surface portions 30a and 30b, which are both cylindrical surface portions on one end side and the other end side, and the tooth tip surfaces at both ends of the female spline groove 28. Therefore, even when used over a long period of time, the first inner ring member 3a and the second inner ring member 4a can be held in a state in which relative rotation is reliably prevented and can be held via a constant velocity joint. The rotation of the wheels can be reliably performed.
[0021]
That is, only the force for joining the first and second inner ring members 3a, 4a is applied to the caulking portion 26, and the force based on the torque transmitted between the inner ring members 3a, 4a. In addition, no force based on the moment load is applied. For this reason, no force is applied to the caulking portion 26 in the direction of reducing the diameter of the caulking portion 26, and the coupling force between the inner ring members 3a and 4a by the caulking portion 26 is applied over a long period of time. Can hold enough. Further, the engaging portion between the female spline groove 28 and the male spline groove 29 only transmits torque between the first and second inner ring members 3a, 4a, and supports the moment load. Therefore, the bending rigidity of the hub 5a formed by connecting the inner ring members 3a and 4a can be sufficiently secured. This point will be described with reference to FIGS.
[0022]
When the automobile incorporating the wheel rolling bearing unit is turned, the hub 5a has a direction (bending direction) in which the central axis of the first inner ring member 3a and the central axis of the second inner ring member 4a are shifted. Moment load is applied. This moment load is supported by a fitting portion between the cylindrical portion 24 and the circular flange portion 25. In the case of this example, the moment load is a pair of fittings between a pair of cylindrical outer peripheral surface portions 30a, 30b provided at positions separated in the axial direction and the tooth tip surfaces at both ends of the female spline groove 28. The joint will support. Since the pair of fitting portions are arranged on both sides in the axial direction with the spline engaging portion interposed therebetween, the distance L (FIG. 5) between the centers of both the fitting portions is sufficiently large, and the fitting surface Is present in a direction perpendicular to the acting direction of the moment load, the bending rigidity can be increased. On the other hand, the female spline groove 28 is formed over the entire length (without providing the pair of cylindrical outer peripheral surface portions 30a and 30b) at the fitting portion between the cylindrical portion 24 and the circular flange-shaped portion 25. When the male spline groove 29 is formed, the bending rigidity cannot be increased.
[0023]
That is, in order to enable the engagement between the female spline groove 28 and the male spline groove 29, a gap between the tooth bottom surface and the tooth tip surface of the female spline groove 28 and the male spline groove 29 is as shown in FIG. In addition, some gaps 34a and 34b must be interposed. Further, in order to transmit a large torque based on the engagement between the female spline groove 28 and the male spline groove 29, the inclination angle θ between the circumferential side surfaces of both the spline grooves 28 and 29 and the diameter direction is small. Must. Therefore, the rigidity against the radial load of the engaging portion between the female spline groove 28 and the male spline groove 29 cannot be increased so much. As a result, as described above, when the female spline groove 28 and the male spline groove 29 are formed over the entire length in the fitting portion between the cylindrical portion 24 and the circular ring-shaped portion 25, Bending rigidity cannot be increased. In this example, the bending rigidity is sufficiently increased by providing the pair of cylindrical outer peripheral surface portions 30a and 30b.
[0024]
7 to 10 show a second example of the embodiment of the present invention. In the case of this example, conversely to the case of the first example described above, the circular inner portion 25a is provided in the inner half part (the right half part in FIG. 7) of the first inner ring member 3b, and the second inner ring member. Cylindrical portions 24a are formed in the outer half of 4b (the left half of FIG. 7). Then, the caulking portion 26a formed at the tip end portion (the right end portion in FIG. 7) of the circular hook-shaped portion 25a is caulked toward the step portion 36 formed on the inner peripheral surface of the intermediate portion of the second inner ring member 4b. The first and second inner ring members 3b and 4b are coupled and fixed to each other. The installation positions of the circular bowl-shaped part 25a and the cylindrical part 24a are reversed, and as a result, the positions of the constituent parts of the joint part between the inner ring members 3b and 4b are reversed inside and outside in the vehicle width direction. Since the configuration and operation are the same as in the case of the first example described above, the same parts are denoted by the same reference numerals, and redundant description is omitted.
[0025]
  Next, FIG. 11 shows a third example of the embodiment of the present invention. In the case of this example, the fitting portion 37 formed at the inner end portion (the end portion on the center side in the width direction in the attached state to the vehicle and the right end portion in FIG. 11) which is one end portion of the outer ring 1 is suspended. The inner half (the right half in FIG. 11) of the hub 5b composed of the first inner ring member 3c and the second inner ring member 4c when fitted into a mounting hole (not shown) of a knuckle constituting the apparatus. Can be inserted into the mounting hole of the knuckle. For this purpose, the outer diameter D of the housing part 9a formed in the inner half part which is a half part near the one end of the second inner ring member 4c.9aThe outer diameter D of the fitting portion 3737Below (D9a≦ D37). In addition, a smaller-diameter mounting portion 38 is formed on the entire open end of the opening portion of the housing portion 9a, and a coupling cylinder 39 made of a corrosion-resistant metal plate such as a stainless steel plate is formed on the mounting portion 38. The base half 40 is fitted and fixed. The coupling cylinder 39 is formed in a cross-sectional crank shape and is formed into a cylindrical shape by connecting a large-diameter base half 40 and a small-diameter leading half 41 at a step 42. Such a coupling tube 39 has the step portion 42 and the mounting portion.38The second edge portion of the base half 40 is affixed to a locking groove 43 formed on the outer peripheral surface of the base end portion (the left end portion in FIG. 11) of the mounting portion 38. The inner ring member 4c is fixed to the inner end portion. An O-ring 44 is provided between the inner peripheral surface of the base half portion 40 and the outer peripheral surface of the mounting portion 38, and rainwater enters the second inner ring member 4c through the two peripheral surfaces. Etc. are prevented from entering.
[0026]
  In the assembled state to the vehicle, the end portion of the boot 45 for dustproofing and waterproofing is externally fitted and fixed to the first half portion 41 of the coupling cylinder 39 as described above. That is, the end portion of the boot 45 is externally fitted to the front half portion 41, and the outer peripheral surface of this end portion is held down by the band 46. A concave groove 47 or a protrusion is formed on the outer peripheral surface of the intermediate portion of the tip half 41, and the end of the boot 45 is engaged by engaging the concave groove 47 or the protrusion with the inner peripheral surface of the end of the boot 45. The portion is prevented from coming off from the first half portion 41. The outer diameter D of the connecting cylinder 3939The outer diameter D of the fitting portion 3737Below (D39≦ D37). Although not shown, the constant velocity joint is used not only on the wheel side but also on the reduction gear (differential gear) side. With these two constant velocity joints and bearings in one piecevehicleIf it is assembled, it will be easy to assemble at an automobile manufacturer. In this case, since the boot 45 and the band 46 are also assembled, the diameter of the circumscribed circle of the band 46 is also the outer diameter D of the fitting portion 37.37Must be: Further, the inner peripheral surface of the mounting portion 38 has a curved shape near the intersection of the ball grooves of the constant velocity joint, and the wall thickness of the portion of the locking groove 43 is within a range where the ball can be incorporated into the constant velocity joint. Is made as thick as possible. The tip of the connecting cylinder as in this exampleLength toIf the is longer, the joint angle of the constant velocity joint cannot be increased, but in the case of the rear wheel, a large joint angle is not required, so this example is particularly effective for the rear wheel because it does not increase the outer diameter. is there.
[0027]
Further, in the illustrated example, a circular recess 48 is formed concentrically with the housing part 9a at the back end of the housing part 9a. The inner diameter R of this circular recess 4848The outer diameter D of the caulking portion 26 formed at the outer end portion of the second inner ring member 4c so as to couple the first inner ring member 3c and the second inner ring member 4c.26Greater than (R48> D26). The circular recess 48 is fitted with a cradle (not shown) during the formation of the caulking portion 26, and the thrust applied to the second inner ring member 4c when the caulking portion 26 is formed. Take the load. Inside diameter R48The above outer diameter D26Therefore, the second caulking portion 26 is processed by swing caulking and the thrust load is applied only to a part of the second inner ring member 4c in the circumferential direction. It is possible to reliably prevent the inner ring member 4c from being inclined and to form the high-quality caulking portion 26. Since other configurations and operations are the same as those of the first example described above, the same parts are denoted by the same reference numerals, and redundant description is omitted.
[0028]
【The invention's effect】
Since the wheel rolling bearing unit of the present invention is configured and operates as described above, it is possible to provide a practical wheel rolling bearing unit that can be made small and lightweight.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing a first example of an embodiment of the present invention.
FIG. 2 is a partial cross-sectional view showing only the first inner ring member taken out from the portion A of FIG.
3 is a diagram viewed from the left side of FIG. 2;
4 is a partial cross-sectional view showing only a second inner ring member taken out from the portion A in FIG. 1. FIG.
FIG. 5 is a partial cross-sectional view for explaining a state in which rigidity against moment load can be ensured.
6 is a cross-sectional view taken along the line BB in FIG.
FIG. 7 is a sectional view showing a second example of the embodiment of the present invention.
8 is a partial cross-sectional view showing only the first inner ring member taken out from part C of FIG.
9 is a partial cross-sectional view showing only the second inner ring member taken out from part C of FIG.
10 is a view from the right side of FIG. 9;
FIG. 11 is a partial sectional view showing a third example of the embodiment of the present invention.
FIG. 12 is a partial cross-sectional view showing an example of a conventional structure.
[Explanation of symbols]
1 outer ring
2 First mounting flange
3, 3a, 3b, 3c First inner ring member
4, 4a, 4b, 4c Second inner ring member
5, 5a, 5b hub
6 Second mounting flange
7 First inner ring raceway
8, 8a Cylindrical part
9, 9a Housing part
10 Second inner ring raceway
11 Rolling elements
12 Locking groove
13 Locking groove
14 Retaining ring
15 steps
16 Welding
17 Inner ring
18 balls
19a, 19b Cover
20a, 20b Seal ring
21 Separator
22 Cylindrical part
23 Outer ring raceway
24, 24a Cylindrical part
25, 25a Circle-shaped part
26, 26a Caulking part
27 steps
28 Female spline groove
29 Male spline groove
30a, 30b Cylindrical outer peripheral surface
31 lid
32 Cage
33 Escape Groove
34a, 34b clearance
35 Projection
36 steps
37 Fitting part
38 Mounting part
39 Combined cylinder
40 base half
41 first half
42 steps
43 Locking groove
44 O-ring
45 boots
46 bands
47 Groove
48 circular recess

Claims (2)

外周面に懸架装置に支持する為の第一の取付フランジを、内周面に複列の外輪軌道を、それぞれ有する外輪と、この外輪から突出した部分の外周面に車輪を支持する為の第二の取付フランジを、上記複列の外輪軌道のうちの一端寄り部分の外輪軌道と対向する部分の外周面に第一の内輪軌道を、それぞれ設けた第一の内輪部材と、外周面の中間部若しくは一端寄り部分に第二の内輪軌道を、他端部に等速ジョイントの外輪となるハウジング部を、それぞれ有する第二の内輪部材と、上記各外輪軌道と上記第一、第二の内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、上記第一、第二の内輪部材のうちの一方の内輪部材の少なくとも軸方向一部に円筒状部分を、他方の内輪部材の少なくとも軸方向一部に円杆状部分を、それぞれ形成すると共に、これら円筒状部分と円杆状部分とを互いに嵌合させた状態で、上記第一、第二の内輪部材同士を結合している車輪用転がり軸受ユニットに於いて、上記円杆状部分の先端部には、外周面を円筒面とした円筒部が形成されており、上記円筒状部分の内周面の少なくとも軸方向中央部には雌スプライン溝が、上記円杆状部分の外周面の少なくとも軸方向中央部にはこの雌スプライン溝と係合する雄スプライン溝が、それぞれ形成されており、上記第一の内輪部材と第二の内輪部材とは、上記雌スプライン溝と雄スプライン溝とを係合させた状態で、上記円筒部の先端部で外周面が円筒面である部分を直径方向外方に塑性変形させる事により形成したかしめ部により上記一方の内輪部材の一部を上記他方の内輪部材に向け、軸方向に抑え付ける事により結合固定されており、上記円杆状部分の一端部外周面に、上記円筒状部分の一端部内周面とがたつきなく嵌合する一端側円筒面を形成し、この円筒状部分の他端部内周面と上記円杆状部分の他端部外周面との少なくとも一方の周面に、相手側周面とがたつきなく嵌合する他端側円筒面を形成すると共に、上記一端側円筒面と上記円筒状部分の一端部内周面とを、この他端側円筒面と相手側周面とを、それぞれ嵌合させている事を特徴とする車輪用転がり軸受ユニット。A first mounting flange for supporting the suspension device on the outer peripheral surface, an outer ring having a double row outer ring raceway on the inner peripheral surface, and a second for supporting the wheel on the outer peripheral surface of the portion protruding from the outer ring. A first inner ring member provided with a first inner ring raceway on the outer peripheral surface of a portion of the double-row outer ring raceway facing the outer ring raceway at one end portion of the double row, and an intermediate between the outer peripheral surface A second inner ring member having a second inner ring raceway at a portion or a portion near one end, and a housing portion serving as an outer ring of a constant velocity joint at the other end portion, each outer ring raceway and the first and second inner rings. A plurality of rolling elements provided between each of the first and second inner ring members, and at least one axial portion of the inner ring member of the first and second inner ring members and a cylindrical portion of the other inner ring member. At least part of the circular shape is formed in the axial direction. In addition, in the rolling bearing unit for a wheel in which the first and second inner ring members are coupled to each other in a state in which the cylindrical portion and the circular ring-shaped portion are fitted to each other, A cylindrical portion having an outer peripheral surface as a cylindrical surface is formed at the distal end portion of the portion, and a female spline groove is provided at least in the axial central portion of the inner peripheral surface of the cylindrical portion, and the outer periphery of the circular cone-shaped portion. A male spline groove that engages with the female spline groove is formed at least in the axial central portion of the surface, and the first inner ring member and the second inner ring member are formed by the female spline groove and the male spline, respectively. In a state where the groove is engaged, a part of the one inner ring member is formed by a caulking portion formed by plastically deforming a portion whose outer peripheral surface is a cylindrical surface at the tip of the cylindrical portion outward in the diametrical direction. In the axial direction toward the other inner ring member By attaching e are fixedly coupled at one end portion outer peripheral surface of the circular rod-shaped portion, forming one end side cylindrical surface which fits without play an end portion inner peripheral surface of the cylindrical portion, the cylindrical On the other peripheral surface of the other end portion inner peripheral surface of the part and the other end portion outer peripheral surface of the circular ring-shaped portion, and forming the other end side cylindrical surface that fits the other side peripheral surface without rattling, A rolling bearing unit for a wheel, wherein the one end side cylindrical surface and the one end inner peripheral surface of the cylindrical portion are fitted to the other end side cylindrical surface and the counterpart peripheral surface, respectively . 第一、第二の内輪部材同士を組み合わせた状態で互いに軸方向に突き当たる、円筒状部分の軸方向端部と、円杆状部分の端部に存在する段部とに、それぞれ硬化処理を施している、請求項１に記載した車輪支持用転がり軸受ユニット。  The first and second inner ring members are combined and subjected to hardening treatment on the axial end portion of the cylindrical portion and the step portion existing at the end portion of the conical portion, which face each other in the axial direction. The rolling bearing unit for supporting a wheel according to claim 1.
JP21844697A 1997-08-13 1997-08-13 Rolling bearing unit for wheels Expired - Fee Related JP3651196B2 (en)

Priority Applications (1)

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Applications Claiming Priority (1)

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JP21844697A JP3651196B2 (en) 1997-08-13 1997-08-13 Rolling bearing unit for wheels

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JP2004186126A Division JP2004278804A (en) 2004-06-24 2004-06-24 Rolling bearing unit for wheel
JP2004186127A Division JP2004316922A (en) 2004-06-24 2004-06-24 Rolling bearing unit for wheel
JP2004189141A Division JP4096920B2 (en) 2004-06-28 2004-06-28 Rolling bearing unit for wheels
JP2004189811A Division JP2005042914A (en) 2004-06-28 2004-06-28 Rolling bearing unit for wheel
JP2005000446A Division JP2005162204A (en) 2005-01-05 2005-01-05 Rolling bearing unit for wheel

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