JP4114368B2 - Method for manufacturing rolling bearing unit for driving wheel - Google Patents

Method for manufacturing rolling bearing unit for driving wheel Download PDF

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Publication number
JP4114368B2
JP4114368B2 JP2002051988A JP2002051988A JP4114368B2 JP 4114368 B2 JP4114368 B2 JP 4114368B2 JP 2002051988 A JP2002051988 A JP 2002051988A JP 2002051988 A JP2002051988 A JP 2002051988A JP 4114368 B2 JP4114368 B2 JP 4114368B2
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Japan
Prior art keywords
spline hole
peripheral surface
hub
cylindrical
caulking
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JP2002339959A (en
JP2002339959A5 (en
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寛朗 石川
信行 萩原
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NSK Ltd
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NSK Ltd
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0078—Hubs characterised by the fixation of bearings
    • B60B27/0084—Hubs characterised by the fixation of bearings caulking to fix inner race
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J9/00—Forging presses
    • B21J9/02—Special design or construction
    • B21J9/025—Special design or construction with rolling or wobbling dies
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21K—MAKING FORGED OR PRESSED METAL PRODUCTS, e.g. HORSE-SHOES, RIVETS, BOLTS OR WHEELS
    • B21K25/00—Uniting components to form integral members, e.g. turbine wheels and shafts, caulks with inserts, with or without shaping of the components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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

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

Description

【０００１】
【発明の属する技術分野】
この発明は、独立懸架式サスペンションに支持された駆動輪｛ＦＦ車（前置エンジン前輪駆動車）の前輪、ＦＲ車（前置エンジン後輪駆動車）及びＲＲ車（後置エンジン後輪駆動車）の後輪、４ＷＤ車（四輪駆動車）の全輪｝を懸架装置に対して回転自在に支持すると共に、上記駆動輪を回転駆動する為に利用する駆動輪用転がり軸受ユニットの製造方法の改良に関する。
【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駆動輪用転がり軸受ユニットが、各種使用されている。又、独立懸架式サスペンションに駆動輪を支持すると共に、この駆動輪を回転駆動する為の駆動輪用転がり軸受ユニットは、車輪側等速ジョイントと結合自在な構造でなければならない。この車輪側等速ジョイントは、駆動輪の変位やこの駆動輪に付与された舵角に拘らず、駆動力を伝達する為の伝達軸の回転を上記駆動輪に対して円滑に（等速性を確保して）伝達する為に必要である。図１０は、この様な目的で駆動輪用転がり軸受ユニット１と車輪側等速ジョイント２とを組み合わせた、従来から一般的に実施されている構造を示している。
【０００３】
このうちの駆動輪用転がり軸受ユニット１は、外輪３の内径側にハブ４及び内輪５を、複数個の転動体６、６を介して回転自在に支持して成る。このうちの外輪３は、その外周面に設けた第一のフランジ７により懸架装置を構成する図示しないナックルに結合固定した状態で、使用時にも回転しない。又、上記外輪３の内周面には複列の外輪軌道８、８を設けて、この外輪３の内径側に上記ハブ４及び内輪５を、この外輪３と同心に、回転自在に支持している。
【０００４】
このうちのハブ４は、外周面の外端（軸方向に関して外とは、自動車への組み付け状態で車両の幅方向外側となる側で、図１０〜１３の左側、図１〜７、９の下側。本明細書全体で同じ。）寄り部分に、車輪を支持する為の第二のフランジ９を設けている。又、上記ハブ４の外周面の中間部に第一の内輪軌道１０を形成し、同じく内端（軸方向に関して内とは、自動車への組み付け状態で車両の幅方向中央側となる側で、図１０〜１３の右側、図１〜７、９の上側。本明細書全体で同じ。）部に形成した、請求項１に記載した嵌合円筒面部に相当する小径段部１１に、その外周面に第二の内輪軌道１２を形成した上記内輪５を外嵌固定している。又、上記ハブ４の中心部には、スプライン孔１３を設けている。
【０００５】
一方、前記車輪側等速ジョイント２は、等速ジョイント用外輪１４と、等速ジョイント用内輪１５と、複数のボール１６、１６と、スプライン軸１７とを備える。上記等速ジョイント用外輪１４はこのスプライン軸１７の内端部に、このスプライン軸１７と同心に設けられている。この様な等速ジョイント用外輪１４の内周面の円周方向複数個所には外径側係合溝１８、１８を、それぞれこの円周方向に対し直角方向に形成している。又、上記等速ジョイント用内輪１５は、中心部に第二のスプライン孔１９を、その外周面で上記各外径側係合溝１８、１８と整合する部分に内径側係合溝２０、２０を、それぞれ円周方向に対し直角方向に形成している。そして、これら各内径側係合溝２０、２０と上記各外径側係合溝１８、１８との間に上記各ボール１６、１６を、保持器２１により保持した状態で、これら各係合溝２０、１８に沿う転動自在に設けている。尚、上記車輪側等速ジョイント２の構成各部の形状等に就いては、周知のツェッパ型或はバーフィールド型の等速ジョイントの場合と同様であり、本発明の要旨とは関係しないので、詳しい説明は省略する。
【０００６】
上述の様な車輪側等速ジョイント２と前述の様な駆動輪用転がり軸受ユニット１とは、上記スプライン軸１７を上記ハブ４のスプライン孔１３に、内側から外側に向け挿通する。そして、上記スプライン軸１７の外端部で上記ハブ４の外端面から突出した部分に設けた雄ねじ部２２にナット２３を螺合し、更に緊締する事により、互いに結合固定する。この状態で、前記内輪５の内端面は上記等速ジョイント用外輪１４の外端面に当接するので、この内輪５が前記小径段部１１から抜け出る方向に変位する事はない。同時に、前記各転動体６、６に適正な予圧が付与される。
【０００７】
更に、自動車の懸架装置への組み付け状態では、前記等速ジョイント用内輪１５の中心部に設けた第二のスプライン孔１９に、伝達軸２４の外端部に設けた雄スプライン部２５をスプライン係合させて、この伝達軸２４を上記等速ジョイント用内輪１５に、回転力の伝達自在に結合する。又、この伝達軸２４の内端部は、デファレンシャルギヤの出力軸部に設けた、トリポード型のデファレンシャル側等速ジョイント２６の出力部であるトラニオン２７（後述する図１３参照）の中心部に結合固定する。従って、自動車の走行時に上記伝達軸２４は、等速回転する。
【０００８】
又、特開平１１−５４０４号公報には、図１１に示す様に、ハブ４ａの内端部で小径段部１１に外嵌した内輪５よりも内方に突出した部分に存在する円筒部を直径方向外方にかしめ広げ（塑性変形させ）て形成したかしめ部２８により、上記内輪５を上記小径段部１１の段差面２９に向け抑え付ける構造が記載されている。この従来構造の第２例の場合には、上記かしめ部２８による抑え付け力により、各転動体６、６に予圧を付与する。尚、上記公報に記載された構造の場合には、駆動輪用転がり軸受ユニット１ａと車輪側等速ジョイント２との結合は、上述した従来構造の第１例の場合と同様に、スプライン軸１７の外端部に設けた雄ねじ部２２とナット２３との螺合・緊締により行なっている。特開２０００−８７９７９号公報にも、同様の構造が記載されている。
【０００９】
但し、上記図１１に示す様に、上記内輪５を上記ハブ４ａに対し固定する為にかしめ部２８を使用する構造の場合には、このかしめ部２８の形成により、上記各転動体６、６への予圧付与は完了する。従って、上記雄ねじ部２２とナット２３とを省略し、駆動輪用転がり軸受ユニットと車輪側等速ジョイントとを結合して成る車輪駆動用転がり軸受ユニットの小型・軽量化を図る事も可能である。図１２は、この様な観点で構成した車輪駆動用転がり軸受ユニット３０の１例を示している。
【００１０】
この車輪駆動用転がり軸受ユニット３０は、ハブ４ｂの中心部に形成したスプライン孔１３内に挿入したスプライン軸１７の抜け止めを、弾性材製の止め輪３１により図っている。この為に、上記スプライン孔１３の外端部に係止段部３２等の外径側係止部を、上記スプライン軸１７の外端部外周面に係止溝３３等の内径側係止部を、それぞれ設けている。そして、ばね鋼製の線材を欠円環状に形成する事により直径を弾性的に拡縮自在とした、上記止め輪３１を、上記係止段部３２と上記係止溝３３との間に掛け渡している。この様に、止め輪３１により上記スプライン孔１３からの上記スプライン軸１７の抜け止めを図り、駆動輪用転がり軸受ユニット１ｂと車輪側等速ジョイント２とを結合する事により、雄ねじ部とナットとを省略する構造によれば、車輪駆動用転がり軸受ユニット３０の小型・軽量化を図れる。
【００１１】
上述の様な車輪駆動用転がり軸受ユニット３０は、図１３に示す様に伝達軸２４及びデファレンシャル側等速ジョイント２６と組み合わせて、車輪用駆動ユニット３４を構成する。このうちのデファレンシャル側等速ジョイント２６は、自動車への組み付け状態では、図示しないデファレンシャルギヤの出力部に結合する。又、上記伝達軸２４は、上記デファレンシャル側等速ジョイント２６の出力部であるトラニオン２７の基端部に内端部を、車輪側等速ジョイント２の入力部である等速ジョイント用内輪１５に外端部を、それぞれ結合している。この様な車輪用駆動ユニット３４により、上記デファレンシャルギヤの出力部からハブ４ｂに支持した駆動輪に回転力を伝達し、この駆動輪を回転駆動する。
【００１２】
上述した図１１〜１３に示す様な、かしめ部２８によりハブ４ａ、４ｂに対し内輪５を固定する構造の場合には、図１０に示す構造から雄ねじ部２２及びナット２３を省略する事により、コスト低減を図れるだけでなく、車輪駆動用転がり軸受ユニット３０、延いては車輪駆動ユニット３４の小型・軽量化を図れる。このうちの車輪駆動用転がり軸受ユニット３０は、懸架装置に組み込んだばねよりも車輪側に存在する、所謂ばね下荷重になる為、少しの軽量化も乗り心地や走行安定性を中心とする走行性能の向上に寄与する。
【００１３】
【発明が解決しようとする課題】
長期間に亙って使用する駆動輪用転がり軸受ユニット１ａ、１ｂを構成するハブ４ａ、４ｂに対し内輪５を固定する為のかしめ部２８の強度は十分に確保する必要がある。従って、このかしめ部２８を形成する為に要する荷重は、揺動かしめ等の、加工時に加わる荷重を比較的低く抑えられる方法を採用したとしても、相当に大きくなる。そして、この様な荷重は上記ハブ４ａ、４ｂの内端部に、軸方向外方に向いたスラスト荷重として加わる。この為、何らの対策も施さない場合には、上記ハブ４ａ、４ｂの中心部に形成したスプライン孔１３の一部（特に内端寄り部分）が、僅かとは言え径方向内方に変形する事が、本発明者等が行なった実験の結果分かった。
【００１４】
即ち、従来は、上記ハブ４ａ、４ｂの内端部に設けた円筒部３７（後述する参考例の１例を示す図１〜２参照）を上記かしめ部２８に加工する場合、この円筒部３７を径方向外方にかしめ広げるので、このかしめ部２８の近傍に位置する、上記スプライン孔１３の内端は径方向外方に変形するものと考えられていた。ところが、上述の様に、上記かしめ部２８の加工時に加わるスラスト荷重が大きく、このスラスト荷重に対する横歪みの影響が従来考えられていた以上に大きくなる為、上記かしめ部２８の近傍である上記スプライン孔１３の内端部が、逆に径方向内方に変形する事を、本発明者等が発見した。何れにしても、上記スプライン孔１３がその一部でも径方向内方に変形した場合には、上記スプライン孔１３内にスプライン軸１７を挿入しにくくなり、車輪駆動用転がり軸受ユニット３０の組立作業を行ないにくくなってしまう。
【００１５】
上記スプライン孔１３の変形に拘らず、上記スプライン孔１３内へのスプライン軸１７の挿入作業を容易に行なえる様にする為には、このスプライン孔１３の内径寸法をスプライン軸１７の外径寸法よりも十分に大きくしたり、上記かしめ部２８の加工後に上記スプライン孔１３を再加工する事が考えられる。このうち、スプライン孔１３の内径寸法を大きくする事は、このスプライン孔１３と上記スプライン軸１７とのスプライン係合部のバックラッシュの増大に繋がり、自動車の運転時に著しい異音が発生する原因ともなる為、好ましくない。又、上記スプライン孔１３の再加工を行なう事は、上記駆動輪用転がり軸受ユニット１ａ、１ｂの製造コストを高くする原因となる為、やはり好ましくない。
本発明の駆動輪用転がり軸受ユニットの製造方法は、この様な事情に鑑みて発明したものである。
【００１６】
【課題を解決するための手段】
本発明の駆動輪用転がり軸受ユニットの製造方法により造る駆動輪用転がり軸受ユニットは、前述した従来から知られている駆動輪用転がり軸受ユニットと同様に、外輪と、ハブと、内輪と、複数の転動体とを備える。
このうちの外輪は、外周面に懸架装置に結合固定する為の第一のフランジを、内周面に複列の外輪軌道を、それぞれ有する。
又、上記ハブは、中心部にスプライン孔を、外周面の外端寄り部分に駆動輪を支持固定する為の第二のフランジを、外周面の中間部に直接又は別体の内輪を介して第一の内輪軌道を、外周面の内端寄り部分に嵌合円筒面部を、それぞれ有する。
又、上記内輪は、外周面に第二の内輪軌道を有し、上記嵌合円筒面部に外嵌した状態で、上記ハブの内端部に形成された円筒部を径方向外方に塑性変形させて形成されたかしめ部により内端面を抑え付けられて、上記ハブに固定されたものである。
更に、上記各転動体は、上記複列の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転動自在に設けられているものである。
【００１７】
特に、本発明の駆動輪用転がり軸受ユニットの製造方法に於いては、上記円筒部を径方向外方に塑性変形させて上記かしめ部とする際に、上記ハブの内径側に抑え治具を挿入し、この抑え治具の内端部のみを、上記スプライン孔の内端部と、上記円筒部の内周面の外端部と、このスプライン孔の内端部とこの円筒部の内周面の外端部との間部分とのうちの少なくとも何れかの部分に係合させると共に、サポート治具に設けた中空筒状の支持筒部の先端面により、上記ハブの外端面でスプライン孔の周囲部分のみを支承しておく事により、上記かしめ部の加工に伴って上記スプライン孔の内端部が内径側に変形する事を防止する。
【００１９】
【作用】
上述の様に構成する本発明の駆動輪用転がり軸受ユニットの製造方法及び車輪用駆動ユニットによれば、特にスプライン孔の内径寸法を大きくしたり、かしめ部の形成後にこのスプライン孔を再加工したりしなくても、このスプライン孔へのスプライン軸の挿入作業を容易に行なえる。
即ち、上記かしめ部を形成する際に上記ハブの内径側に抑え治具を挿入し、この抑え治具の内端部のみを、このスプライン孔の内端部と、円筒部の内周面の外端部と、このスプライン孔の内端部とこの円筒部の内周面の外端部との間部分とのうちの少なくとも何れかの部分に係合させておく事により、上記かしめ部の加工に伴って上記スプライン孔の内端部が内径側に変形する事を防止しているので、上記かしめ部を形成すべく上記円筒部を塑性変形させる際にハブに加わる荷重に拘らず、上記スプライン孔の変形を抑えられる。
又、上記かしめ部を形成する際に、サポート治具に設けた中空筒状の支持筒部の先端面により、ハブの外端面でスプライン孔の周囲部分のみを支承している為、かしめ部の加工に伴って第二のフランジが変形する事を防止できる。即ち、サポート治具を大径にし、このサポート治具の上端面により上記ハブの外周面に形成した第二のフランジの外側面を支える事も考えられるが、上記かしめ部の加工に伴ってこの第二のフランジが変形する可能性がある。この第二のフランジの変形は、ディスクブレーキを構成するロータの振れを大きくし、制動時に発生する振動や騒音を大きくする原因となる。これに対して、サポート治具に設けた中空筒状の支持筒部の先端面により、ハブの外端面でスプライン孔の周囲部分を支承すれば、この様な問題が生じる事はない。
【００２０】
【発明の実施の形態】
図１〜２は、本発明に関する参考例の１例を示している。尚、本参考例の特徴は、ハブ４ｃの内端部の小径段部１１に外嵌した内輪５の内端面を抑え付けるべく、このハブ４ｃの内端部にかしめ部２８を形成する際に、このハブ４ｃの中心部に形成したスプライン孔１３が変形しない様にすべく、このハブ４ｃの内径側に抑え治具４１を挿入した状態で上記かしめ部２８の加工を行なう様にした点にある。その他の部分の基本的な構造及び作用に就いては、前述の図１１に示した従来構造の第２例、或は図１２〜１３に示した、この第２例の構造を改良したもの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若しくは簡略にし、以下、本参考例の特徴部分並びに上記各例の場合と異なる部分を中心に説明する。
【００２１】
上記内輪５の内周面と内端面とは、断面形状が凸円弧形である面取り部３５により滑らかに連続している。又、上記内輪５の内端部でこの面取り部３５の径方向外側に位置する部分には段付部３６を全周に亙り形成して、この面取り部３５部分の径方向に関する厚さを、この部分よりも外寄り部分の厚さに比べて小さくしている。この構成により、上記かしめ部２８の形成作業に伴って上記内輪５の内端部に径方向外方に加わる大きな力に拘らず、この内輪５の中間部外周面に形成した第二の内輪軌道１２の形状が歪むのを防止している。
【００２２】
上記かしめ部２８を形成すべく、上記ハブ４ｃの内端部に形成した円筒部３７は、外周面を円筒面とし、内周面を、内端開口に向かうほど内径が大きくなる方向に僅かに（例えば母線が中心軸に対し０〜５度程度）傾斜したテーパ面としている。尚、図示の例では、上記円筒部３７の外周面と上記内輪５を外嵌する為の小径段部１１の外周面との境界部に、断面形状が凹円弧状である段差部３８を形成して、これら両外周面同士の間に僅かな（例えば０．０１〜０．５mm程度の）段差を設けている。この様な段差部３８は、上記かしめ部２８を形成する為に上記円筒部３７を径方向外方に塑性変形させる際に変形の基点となって、この円筒部３７から上記かしめ部２８への加工を、亀裂や過大な空隙等の欠陥を生じさせずに、滑らかに行なえる様にする為に設けている。この為に、上記段差部３８と上記小径段部１１との境界部の軸方向位置を、上記面取り部３５の外端部の軸方向位置とほぼ一致させている。又、上記円筒部３７の先端面（内端面）外周縁部には面取りを施して、上記加工の過程でこの外周縁部に加わる引っ張り方向の力に拘らず、この外周縁部に亀裂等の損傷が発生しにくくしている。
【００２３】
上述の様な円筒部３７の内周面の軸方向外端部と、上記ハブ４ｃの中心部に形成した前記スプライン孔１３の軸方向内端部との間には、円すい凹面状の傾斜面部３９を形成している。この傾斜面部３９は、軸方向内方に向かうほど直径が大きくなる方向に傾斜した円すい凹面状である。この様な傾斜面部３９の母線は、上記ハブ４ｃの中心軸に対し、上記円筒部３７の内周面よりも大きく（例えば２０〜７０度、より好ましくは２５〜６５度）傾斜している。この様な傾斜面部３９は、例えば自動車メーカーで上記スプライン孔１３内に車輪側等速ジョイント２を構成するスプライン軸１７（図１０〜１３参照）を挿入する為のガイド面として機能し、このスプライン軸１７の挿入作業を容易に行なえる様にする。尚、上記傾斜面部３９と上記円筒部３７の内周面との境界部は、好ましくは、上記面取り部３５の軸方向外端位置よりも、僅かに（例えば０〜２mm）軸方向外方に位置させる。
【００２４】
上述の様な形状を有する円筒部３７を径方向外方に塑性変形させて、前記かしめ部２８とする際には、上記ハブ４ｃの中心軸を鉛直方向に配置した状態で、このハブ４ｃの外端面（下面）をサポート治具４０により支承する。このサポート治具４０は、中空筒状の支持筒部６０を有し、この支持筒部６０の上端面で、上記ハブ４ｃの外端面で上記スプライン孔１３の周囲部分を支承する。又、上記スプライン孔１３内に、抑え治具４１の上端部を挿入する。この抑え治具４１の上端部には雄スプライン部４２が形成されており、上記かしめ部２８の加工作業の間中、この雄スプライン部４２が上記スプライン孔１３の外端から内端（下端から上端）に至るまで、全長に亙ってがたつきなくスプライン係合したままの状態となる。尚、上記雄スプライン部４２の形状は、車輪用駆動ユニット３４（図１３参照）を組み立てた状態で上記スプライン孔１３内に挿入される、上記スプライン軸１７の外周面に形成された雄スプライン部（図１０〜１３参照）と実質的に同じものである。
【００２５】
上記円筒部３７を径方向外方に塑性変形させて上記かしめ部２８とする作業は、上述の様にハブ４ｃの外端面をサポート治具４０により支承し、上記スプライン孔１３内に上記抑え治具４１の雄スプライン部４２を挿入した状態で、揺動プレス装置のラム（図示省略）にセットしたかしめ治具４３により、上記円筒部３７を抑え付ける事で行なう。このかしめ治具４３は、中心軸を鉛直軸に対し少し（例えば１〜３度程度）だけ傾斜した状態で支持されており、この傾斜に基づく揺動運動（振れ回り運動）に基づいて上記円筒部３７の円周方向の一部に、軸方向外方に向いた大きな力を付与する。この力が付与される部分が、上記円筒部３７の円周方向に関して連続的に変化するので、この円筒部３７が全周に亙って軸方向並びに径方向外方に塑性変形し、図２に示す様なかしめ部２８とされる。
【００２６】
この様にして上記円筒部３７を上記かしめ部２８に加工する際、上記スプライン孔１３の内端部が径方向内方に変形する傾向になる。但し、このスプライン孔１３には、この内端部に至る部分まで、上記抑え治具４１の雄スプライン部４２が挿入されている為、上記スプライン孔１３の内端部が径方向内方に変形する事は殆どない。この為、本参考例の製造方法により駆動輪用転がり軸受ユニットを造れば、特に上記スプライン孔１３の内径寸法を大きくしたり、上記かしめ部２８の形成後にこのスプライン孔１３を再加工したりしなくても、このスプライン孔１３へのスプライン軸１７（図１０〜１３参照）の挿入作業を容易に行なえる。尚、上記かしめ部２８の加工が完了した状態では、上記スプライン孔１３の内端部内周面と上記雄スプライン部４２の上端部外周面とが強く当接する可能性がある。但し、この雄スプライン部４２を設けた上記抑え治具４１は、工場に設置した油圧シリンダ等のアクチュエータにより、大きな力で上記スプライン孔１３から抜き出せる。従って、上記かしめ部２８を加工した後のハブ４ｃ内から上記抑え治具４１を抜き取る作業が特に面倒になる事はない。
【００２７】
次に、図３は、本発明の実施の形態の第１例を示している。本例の場合には、ハブ４ｄの内端寄り部分の内周面で、円筒部３７の外端部（下端部）とスプライン孔１３の内端部（上端部）との間部分に傾斜面部３９ａ、３９ｂを、２段に亙って設けている。そして、これら両傾斜面部３９ａ、３９ｂ同士の間に、円筒面部４４を形成している。このうちのスプライン孔１３寄りの傾斜面部３９ａは、例えば自動車メーカーで上記スプライン孔１３内に車輪側等速ジョイント２を構成するスプライン軸１７（図１０〜１３参照）を挿入する為のガイド面として機能し、このスプライン軸１７の挿入作業を容易に行なえる様にする為に利用する。従って、上記スプライン孔１３寄りの傾斜面部３９ａの母線は、上記ハブ４ｄの中心軸に対し、例えば０〜６０度程度、より好ましくは０〜４５度程度傾斜している。
【００２８】
これに対して、上記円筒部３７寄りの傾斜面部３９ｂは、上記円筒面部４４と上記円筒部３７の内周面とを連続させる役目を持ち、ガイド面としての役目は持たない。即ち、上記傾斜面部３９ｂは、前記かしめ部２８の加工時に、上記円筒部３７だけを変形させて、この円筒部３７の変形が上記スプライン孔１３の内端部まで及ばない様に、このスプライン孔１３の内端部に隣接した部分の肉厚を大きくする為に設けたものである。従って、上記円筒部３７寄りの傾斜面部３９ｂの母線の上記ハブ４ｄの中心軸に対する傾斜角度は、例えば６０〜９０度程度の大きな値とする事も可能である。勿論、これよりも小さな傾斜角度としても良い。
【００２９】
本例の場合、上記円筒部３７を径方向外方に塑性変形させて、かしめ部２８とする際には、上記ハブ４ｄの中心軸を鉛直方向に配置した状態で、このハブ４ｄの外端面（下面）をサポート治具４０により支承する。又、上記スプライン孔１３内に抑え治具４１ａを、このスプライン孔１３の内端開口から外方に（図３の上から下に）挿入する。本例の実施に使用する上記抑え治具４１ａの上端部には、前述した参考例の様な雄スプライン部４２（図１参照）は形成していない。その代わりに、上記抑え治具４１ａの上端部に、外向フランジ状の支え鍔部４５を形成している。この支え鍔部４５は、上記スプライン孔１３寄りの傾斜面部３９ａと上記円筒面部４４との内側にほぼがたつきなく内嵌自在な形状及び大きさを有するもので、その外径は、上記円筒面部４４の内径と同じか、この内径よりも僅かに小さくしている。
【００３０】
上述の様な抑え治具４１ａは、上記円筒部３７を塑性変形してかしめ部２８とする為の加工作業の間中、図示しない引っ張り装置により下方に引っ張り続け、上記支え鍔部４５が上記円筒面部４４の内径側に位置する様にする。この状態で、上記円筒部３７にかしめ治具４３（図１参照）を強く押し付けて、この円筒部３７を径方向外方に塑性変形させ、上記かしめ部２８とする。この様にして上記円筒部３７を上記かしめ部２８に加工する際、上記スプライン孔１３の内端部が径方向内方に変形する傾向になる。但し、このスプライン孔１３の内側（図３の上側）に隣接する円筒面部４４に上記抑え治具４１ａの支え鍔部４５が、僅かな締り嵌め若しくは極く小さな隙間の隙間嵌により内嵌されている為、上記スプライン孔１３の内端部が径方向内方に、実用上問題となる程変形する事はない。
【００３１】
尚、上記かしめ部２８の加工作業中、上記抑え治具４１ａを下方に引っ張る力は、上記円筒面部４４と上記支え鍔部４５との係合が外れるのを防止できる程度の、小さな値（例えば数百Ｎ程度）とする。この理由は、上記力を大きくし過ぎて、この力に基づいて前記ハブ４ｄが軸方向に圧縮されると、この力の解除に伴うこのハブ４ｄの弾性復元に伴って、各転動体６、６に付与した予圧が低下若しくは喪失する為である。
【００３２】
又、この点は、前述した参考例（及び後述する第２〜６例）の場合も同様であるが、上記かしめ部２８の加工作業に伴ってかしめ治具４３（図１参照）からこのかしめ部２８に加わるスラスト荷重の作用点の最大半径Ｒが、サポート治具４０の外径Ｄの１／２以下（Ｒ≦Ｄ／２）となる様に、このサポート治具４０及び上記かしめ部２８の径方向寸法を規制している。この理由は、比較的軽荷重でこのかしめ部２８の加工を行なえる、揺動かしめを採用した場合でも、かしめ加工時に上記ハブ４ｄの姿勢が不安定になる事を防止する為である。
【００３３】
即ち、円周方向の一部にのみかしめの為の荷重を加え、この荷重を加える位置を円周方向に移動させる揺動かしめは、全周を一度に変形させる一般的なかしめ加工に比べてかしめ加工の為に要する荷重を遥かに小さくできる反面、被加工部に加わる荷重が円周方向に関して不均一となる。この為、Ｒ＞Ｄ／２となり、加工荷重が上記サポート治具４０の支承面の外周縁よりも径方向外方にはみ出すと、このサポート治具４０に載置された上記ハブ４ｄの姿勢が不安定になり、良質のかしめ部２８を得にくくなる。このハブ４ｄの姿勢を安定させる為に、上記抑え治具４１ａを下方に引っ張る力を強くする事も考えられるが、前述の理由により採用する事は難しい。又、サポート治具を大径にし、このサポート治具の上端面により上記ハブ４ｄの外周面に形成した第二のフランジ９の外側面（下面）を支える事も考えられるが、上記かしめ部２８の加工に伴って上記第二のフランジ９が変形する可能性がある。この第二のフランジ９の変形は、ディスクブレーキを構成するロータの振れを大きくし、制動時に発生する振動や騒音を大きくする原因となる為、やはり採用は難しい。これに対して、上記最大半径Ｒを上記外径Ｄの１／２以下（Ｒ≦Ｄ／２）とすれば、これらの問題を総て解決できる。
【００３４】
次に、図４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、前述の図１〜２に示した参考例の場合と同様のハブ４ｃを使用し、上述した第１例の場合と同様の抑え治具４１ａの支え鍔部４５により、スプライン孔１３の内端部と円筒部３７の外端部との間に存在する傾斜面部３９を内径側から支承している。この様な本例の構造でも、この傾斜面部３９の傾斜角度が極端に高くなければ、この傾斜面部３９を内径側から支え、かしめ部の加工に伴って上記スプライン孔１３の内端部が径方向内方に変形する事を防止できる。その他の部分の構成及び作用は、上述した第１例の場合と同様である。
【００３５】
次に、図５は、本発明の実施の形態の第３例を示している。前述の参考例、実施の形態の第１例及び上述の第２例の構造の場合に、ハブ４ｃ、４ｄの中間部外周面に直接第一の内輪軌道１０を形成していたのに対して、本例の場合には、外周面に第一の内輪軌道１０を形成した内輪５ａを、ハブ４ｅの中間部に外嵌している。そして、外周面に第二の内輪軌道１２を形成した内輪５の外端面を、上記内輪５ａの内端面に突き当てている。又、本例の場合には、前述した第１例及び上述した第２例の場合と同様の抑え治具４１ａの支え鍔部４５により、円筒部３７の外端部を内径側から支承している。即ち、この支え鍔部４５をこの円筒部３７の外端部に、締り嵌め若しくは極く小さな隙間の隙間嵌により内嵌した状態で、上記円筒部３７をかしめ部に加工する様にしている。その他の部分の構造及び作用は、上述した第２例の場合と同様である。
【００３６】
次に、図６は、本発明の実施の形態の第４例を示している。本例の場合には、円筒部３７の内周面を、内端開口部に向かう程内径が大きくなる方向に僅かに（中心軸に対する母線の傾斜角度αが１０度以下）傾斜したテーパ面としている。又、抑え治具４１ｂの上端部に形成した支え鍔部４５ａの外周面を、上記円筒部３７の内周面と同方向に同角度だけ傾斜させている。そして、この円筒部３７を塑性変形させてかしめ部２８（図２参照）を形成する際には、上記支え鍔部４５ａを上記円筒部３７の外端部にくさび状に隙間なく嵌合させる。
【００３７】
この状態で上記円筒部３７を塑性変形させてかしめ部２８を形成すれば、スプライン孔１３の内端部が径方向内方に変形する事を防止できる。又、上記傾斜角度αの値は小さいので、上記円筒部３７が径方向内方に変形しようとする力に伴って、上記支え鍔部４５ａを上方に変位させようとする力は小さい。従って、かしめ加工の間中、上記抑え治具４１ｂを下方に引っ張っておく力は小さくて済み、この力を得る為の油圧設備等は小型のもので良い。その他の部分の構成及び作用は、上述した第３例の場合と同様である。
【００３８】
次に、図７〜８は、本発明の実施の形態の第５例を示している。本例の場合には、円筒部３７を塑性変形させてかしめ部２８を形成する際に、スプライン孔１３の内端部が径方向内方に変形するのを防止する為の抑え治具４１ｃとして、外径側抑え素子４６と内径側抑え素子４７とを組み合わせて成るものを使用している。このうちの外径側抑え素子４６は、全体を略円筒状に形成したもので、上半部（上下は、上記かしめ部２８を形成する状態を示す、図７による。）に複数のスリット４８、４８を、それぞれ上端面に達する状態で形成している。そして、上記外径側抑え素子４６の上半部に、上記各スリット４８、４８の幅を狭めつつ外径を小さくする方向の弾力を付与している。尚、これら各スリット４８、４８は、次述する大径円筒面部４９の、弾性変形に基づく直径の拡縮量を大きくできる様に、円周上に６〜８本程度と多く設け、且つ軸方向長さをできるだけ長くしている。
【００３９】
この様な外径側抑え素子４６の上端部には、ハブ４ｆの内周面内端寄り部分を内径側から支える為の大径円筒面部４９を設けている。尚、上記外径側抑え素子４６の上半部の外径が弾性的に縮まった状態で、上記大径円筒面部４９の外径は、上記スプライン孔１３の歯先円の直径以下となる。又、上記ハブ４ｆの内周面内端寄り部分でこのスプライン孔１３の内端部に隣接する部分に、上記大径円筒面部４９を当接させる為の円筒面部５０を形成している。この円筒面部５０の内径は、上記スプライン孔１３の歯底円の直径と同じか、この歯底円の直径よりも僅かに大きくしている。
【００４０】
一方、上記外径側抑え素子４６の上端部内周面に、上端に向かう程内径が大きくなる方向に傾斜した、部分円すい凹面状の、内径側テーパ係合部５１を形成している。これに合わせて、前記内径側抑え素子４７の上端部に、上方に向かう程外径が大きくなる、外径側テーパ係合部５２を形成している。上記外径側抑え素子４６の上端部の直径は、この外径側抑え素子４６に対する上記内径側抑え素子４７の軸方向変位に伴う、上記内径側、外径側両係合部５１、５２同士の係合により拡縮する。この様な外径側抑え素子４６と内径側抑え素子４７とは、この外径側抑え素子４６の下端部に形成した通孔５３を挿通し、この内径側抑え素子４７の下端部に形成したねじ孔５４に螺合したボルト５５により結合している。尚、上記内径側抑え素子４７の上端面には、六角レンチ等の工具を係止する為の、六角孔等の係止凹孔５６を形成している。又、上記外径側抑え素子４６と内径側抑え素子４７との間には圧縮ばね５７を設けて、この内径側抑え素子４７に、上記外径側抑え素子４６から抜け出る方向の弾力を付与している。
【００４１】
本例の場合、かしめ部２８の加工作業に先立って上記円筒面部５０を、上記外径側抑え素子４６の大径円筒面部４９により内径側から抑える。この作業を行なう為に、先ず、少なくとも上記内径側抑え素子４７の外径側テーパ係合部５２を上記外径側抑え素子４６の内径側テーパ係合部５１の内径側に位置させずにおく。そして、上記大径円筒面部４９の直径を縮めた状態で、この大径円筒面部４９を上記円筒面部５０の内径側に位置させる。この作業は、前記ハブ４ｆを上記外径側抑え素子４６に対し、上方から下方に外嵌する事により行なう。
【００４２】
次いで、上記係止凹孔５６に工具を係止して、上記内径側抑え素子４７の回転を防止しつつ、前記ボルト５５を緊締して、上記内径側抑え素子４７の外径側テーパ係合部５２を上記外径側抑え素子４６の内径側テーパ係合部５１の内径側に引き込む。この引き込みに伴って、この外径側抑え素子４６の上半部の直径が広がり、上記大径円筒面部４９が上記円筒面部５０に密接する。この結果、前記スプライン孔１３の内端部が、内径が縮まらない様に抑えられた状態となるので、前述した各例の場合と同様に、前記ハブ４ｆの内端部に形成した円筒部３７を径方向外方に塑性変形させて、前記かしめ部２８を形成する。このかしめ部２８を形成した後は、再び上記係止凹孔５６に工具を係止して、上記内径側抑え素子４７の回転を防止しつつ、上記ボルト５５を緩める。すると、この内径側抑え素子４７が前記圧縮ばね５７に押されて上方に変位し、上記内径側抑え素子４７の外径側テーパ係合部５２が上記外径側抑え素子４６の内径側テーパ係合部５１から抜け出る。この結果、この外径側抑え素子４６の上半部の直径が縮まるので、上記ハブ４ｆを上方に抜き取る。尚、図７には、互いに別体とした外径側抑え素子４６とサポート治具４０ａとを嵌合組み合わせた場合に就いて示しているが、これら外径側抑え素子４６とサポート治具４０ａとを一体に構成しても良い。その他の部分の構造及び作用は、前述した各例の場合と同様である。
【００４３】
尚、上記かしめ部を加工した後、抑え治具の抜き取り作業の為に、ハブの内端部内周面と抑え治具の外周面との間に隙間が存在する状態となる場合には、その隙間に基づき、加工後に抑え治具を取り除いた時の弾性変形分だけ、上記ハブの内径が縮まる事が避けられない。これに対して本例の場合には、拡縮可能な抑え治具４１ｃを用い、ボルト５５の締め付けトルクを調節する事によって、上記かしめ部２８を加工する際の上記ハブ４ｆの内径の拡大量を予め制御した上で、このかしめ部２８の加工を行なう事ができる。この為、このかしめ部２８を加工する前後での、上記ハブ４ｆの内径寸法の変化量を最小に抑える事が可能になる。しかも、本例の様に、ハブ４ｆの円筒面部５０を抑え付ける方法は、前述した参考例の様なスプライン孔部分を抑える方法とは異なり、雄、雌両スプライン同士を係合する為に抑え治具の円周方向の位相を合わせる必要がなくなるだけでなく、抑え治具の金型が作り易いと言った利点がある。但し、本例の変形例として、抑え治具の外周面のうちでハブの内周面と当接する部分を雄スプラインとし、この部分でスプライン孔１３を抑え付ける事も可能である。
【００４４】
次に、図９は、本発明の実施の形態の第６例を示している。本例の場合には、ハブ４ｇの内端部に設けた円筒部３７を径方向外方に塑性変形させてかしめ部２８とする場合に、上記ハブ４ｇの中心部に設けたスプライン孔１３の内端部に、抑え治具４１ｄを内嵌する様にしている。この為に本例に使用する抑え治具４１ｄは、下方（上下は、上記かしめ部２８を形成する状態を示す、図９による。）に向かう程外径が小さくなる、円すい台状に形成している。又、上記抑え治具４１ｄの外周面には、上記スプライン孔１３の内周面に形成したスプライン歯を進入させる凹溝５８、５８を、軸方向に形成している。上記かしめ部２８の加工に伴う、上記ハブ４ｇのスプライン孔１３の変形は、このスプライン孔１３の軸方向内端部で局部的に発生するので、本例の場合には、上記円すい台状の抑え治具４１ｄを使用して、この抑え治具４１ｄと上記スプライン孔１３の内端部とを隙間なく係合させる様にしている。
【００４５】
上記円筒部３７を径方向外方に塑性変形させて上記かしめ部２８とする場合には、かしめ治具４３の下面により、圧縮ばね５９を介して上記抑え治具４１ｄを上記ハブ４ｇに押圧しつつ、上記かしめ治具４３により上記円筒部３７を塑性変形させる。この結果、上記スプライン孔１３の内端部の内径が縮まるのを抑えつつ、上記かしめ部２８の加工作業を行なえる。尚、上記圧縮ばね５９は、その下端部又は上端部を、上記抑え治具４１ｄの上面又は上記かしめ治具４３の下面に結合しておけば、取り扱い性の向上、並びに上記かしめ部２８の加工時の位置決めを図れる。その他の部分の構造及び作用は、前述した各例の場合と同様である。
【００４６】
【発明の効果】
本発明の駆動輪用転がり軸受ユニットの製造方法は、以上に述べた通り構成され作用するので、小型・軽量で自動車の走行性能の向上に寄与できる構造を、より低コストで実現できる。
【図面の簡単な説明】
【図１】 本発明に関する参考例の１例を、かしめ部を加工する状態で示す断面図。
【図２】同じくかしめ部を加工した後の状態で示す断面図。
【図３】 本発明の実施の形態の第１例を示す、図１と同様の図。
【図４】 同第２例を示す、図１と同様の図。
【図５】 同第３例を示す、図１と同様の図。
【図６】 同第４例を示す、図１と同様の図。
【図７】 同第５例を示す、図１と同様の図。
【図８】外径側抑え素子を取り出して図７の斜め下方から見た状態で示す斜視図。
【図９】 本発明の実施の形態の第６例を示す、図１と同様の図。
【図１０】従来構造の第１例を示す断面図。
【図１１】同第２例を示す半部断面図。
【図１２】この第２例を改良した構造を示す断面図。
【図１３】この改良した構造を組み込んだ車輪用駆動ユニットの断面図。
【符号の説明】
１、１ａ、１ｂ 駆動輪用転がり軸受ユニット
２ 車輪側等速ジョイント
３ 外輪
４、４ａ、４ｂ、４ｃ、４ｄ、４ｅ、４ｆ、４ｇ ハブ
５、５ａ 内輪
６ 転動体
７ 第一のフランジ
８ 外輪軌道
９ 第二のフランジ
１０ 第一の内輪軌道
１１ 小径段部
１２ 第二の内輪軌道
１３ スプライン孔
１４ 等速ジョイント用外輪
１５ 等速ジョイント用内輪
１６ ボール
１７ スプライン軸
１８ 外径側係合溝
１９ 第二のスプライン孔
２０ 内径側係合溝
２１ 保持器
２２ 雄ねじ部
２３ ナット
２４ 伝達軸
２５ 雄スプライン部
２６ デファレンシャル側等速ジョイント
２７ トラニオン
２８ かしめ部
２９ 段差面
３０ 車輪駆動用転がり軸受ユニット
３１ 止め輪
３２ 係止段部
３３ 係止溝
３４ 車輪用駆動ユニット
３５ 面取り部
３６ 段付部
３７ 円筒部
３８ 段差部
３９、３９ａ、３９ｂ 傾斜面部
４０、４０ａ サポート治具
４１、４１ａ、４１ｂ、４１ｃ、４１ｄ 抑え治具
４２ 雄スプライン部
４３ かしめ治具
４４ 円筒面部
４５、４５ａ 支え鍔部
４６ 外径側抑え素子
４７ 内径側抑え素子
４８ スリット
４９ 大径円筒面部
５０ 円筒面部
５１ 内径側テーパ係合部
５２ 外径側テーパ係合部
５３ 通孔
５４ ねじ孔
５５ ボルト
５６ 係止凹孔
５７ 圧縮ばね
５８ 凹溝
５９ 圧縮ばね
６０ 支持筒部 [0001]
BACKGROUND OF THE INVENTION
  The present invention relates to a drive wheel {an FF vehicle (front engine front wheel drive vehicle) front wheel, an FR vehicle (front engine rear wheel drive vehicle) and an RR vehicle (rear engine rear wheel drive vehicle) supported by an independent suspension type suspension. ) Rear wheels, all wheels of 4WD vehicles (four-wheel drive vehicles)} are rotatably supported with respect to the suspension device, and are used for driving wheel rolling bearing units used for rotationally driving the drive wheels.Manufacturing methodRegarding improvements.
[0002]
[Prior art]
In order to rotatably support the wheel with respect to the suspension device, various types of driving wheel rolling bearing units in which an outer ring and an inner ring are rotatably combined via a rolling element are used. Further, the driving wheel rolling bearing unit for supporting the driving wheel on the independent suspension and rotating the driving wheel must be structured to be coupled to the constant velocity joint on the wheel side. This wheel side constant velocity joint smoothly rotates the transmission shaft for transmitting the driving force with respect to the driving wheel regardless of the displacement of the driving wheel and the rudder angle given to the driving wheel (constant velocity property). Necessary to communicate). FIG. 10 shows a structure that has been generally implemented conventionally, in which the driving wheel rolling bearing unit 1 and the wheel side constant velocity joint 2 are combined for such a purpose.
[0003]
Among them, the drive wheel rolling bearing unit 1 is configured such that a hub 4 and an inner ring 5 are rotatably supported via a plurality of rolling elements 6 on the inner diameter side of an outer ring 3. Of these, the outer ring 3 is coupled and fixed to a knuckle (not shown) constituting the suspension device by a first flange 7 provided on the outer peripheral surface thereof, and does not rotate during use. Further, double row outer ring raceways 8, 8 are provided on the inner peripheral surface of the outer ring 3, and the hub 4 and the inner ring 5 are rotatably supported concentrically with the outer ring 3 on the inner diameter side of the outer ring 3. ing.
[0004]
Of these, the hub 4 is the outer end of the outer peripheral surface (outside in the axial direction is the outer side in the width direction of the vehicle in the assembled state in the automobile, on the left side of FIGS. The lower side is the same throughout the present specification.) A second flange 9 for supporting the wheel is provided on the side portion. Further, the first inner ring raceway 10 is formed in the intermediate portion of the outer peripheral surface of the hub 4 and is also the inner end (inside with respect to the axial direction, the inner side is the central side in the width direction of the vehicle in the assembled state in the automobile, The right side of FIGS. 10 to 13 and the upper side of FIGS. 1 to 7 and 9 (the same applies to the entire specification)), the outer periphery of the small diameter step portion 11 corresponding to the fitting cylindrical surface portion according to claim 1 The inner ring 5 having the second inner ring raceway 12 formed on the surface is externally fitted and fixed. A spline hole 13 is provided at the center of the hub 4.
[0005]
On the other hand, the wheel side constant velocity joint 2 includes a constant velocity joint outer ring 14, a constant velocity joint inner ring 15, a plurality of balls 16 and 16, and a spline shaft 17. The outer ring 14 for the constant velocity joint is provided concentrically with the spline shaft 17 at the inner end portion of the spline shaft 17. Outer diameter side engaging grooves 18 and 18 are formed at right angles to the circumferential direction at a plurality of locations in the circumferential direction on the inner circumferential surface of the constant velocity joint outer ring 14. The inner ring 15 for the constant velocity joint has a second spline hole 19 at the center, and inner diameter side engaging grooves 20, 20 at the outer peripheral surface aligned with the outer diameter side engaging grooves 18, 18. Are formed at right angles to the circumferential direction. Then, in a state where the balls 16, 16 are held by the cage 21 between the inner diameter side engagement grooves 20, 20 and the outer diameter side engagement grooves 18, 18, the engagement grooves 20 and 18 are provided so as to be freely rollable. The shape of each component of the wheel side constant velocity joint 2 is the same as that of a well-known Zepper type or Barfield type constant velocity joint, and is not related to the gist of the present invention. Detailed description is omitted.
[0006]
The wheel side constant velocity joint 2 and the driving wheel rolling bearing unit 1 as described above are inserted through the spline shaft 17 through the spline hole 13 of the hub 4 from the inside to the outside. Then, a nut 23 is screwed into a male screw portion 22 provided at a portion protruding from the outer end surface of the hub 4 at the outer end portion of the spline shaft 17, and further tightened to be coupled and fixed to each other. In this state, the inner end surface of the inner ring 5 is in contact with the outer end surface of the constant velocity joint outer ring 14, so that the inner ring 5 is not displaced in the direction of coming out of the small diameter step portion 11. At the same time, an appropriate preload is applied to each of the rolling elements 6 and 6.
[0007]
Further, in the state of being assembled to the suspension device of the automobile, the male spline portion 25 provided at the outer end portion of the transmission shaft 24 is connected to the second spline hole 19 provided at the center portion of the inner ring 15 for the constant velocity joint. In combination, the transmission shaft 24 is coupled to the constant velocity joint inner ring 15 so as to be able to transmit the rotational force. Further, the inner end portion of the transmission shaft 24 is coupled to the central portion of a trunnion 27 (see FIG. 13 described later) which is an output portion of a tripod type differential side constant velocity joint 26 provided on the output shaft portion of the differential gear. Fix it. Therefore, the transmission shaft 24 rotates at a constant speed when the automobile is running.
[0008]
Further, in Japanese Patent Laid-Open No. 11-5404, as shown in FIG. 11, a cylindrical portion that exists in a portion projecting inwardly from the inner ring 5 fitted on the small-diameter step portion 11 at the inner end portion of the hub 4a is provided. A structure is described in which the inner ring 5 is pressed against the step surface 29 of the small diameter step portion 11 by a caulking portion 28 formed by caulking and expanding (plastic deformation) outward in the diameter direction. In the case of the second example of the conventional structure, a preload is applied to the rolling elements 6 and 6 by the pressing force by the caulking portion 28. In the case of the structure described in the above publication, the spline shaft 17 is connected to the driving wheel rolling bearing unit 1a and the wheel side constant velocity joint 2 in the same manner as in the first example of the conventional structure described above. This is performed by screwing and tightening a male screw portion 22 and a nut 23 provided at the outer end portion of the nut. Japanese Patent Laid-Open No. 2000-87979 also describes a similar structure.
[0009]
However, as shown in FIG. 11, in the case of using the caulking portion 28 to fix the inner ring 5 to the hub 4a, the rolling elements 6, 6 are formed by forming the caulking portion 28. Preloading to is completed. Therefore, it is possible to reduce the size and weight of the wheel drive rolling bearing unit formed by combining the drive wheel rolling bearing unit and the wheel side constant velocity joint by omitting the male screw portion 22 and the nut 23. . FIG. 12 shows an example of a wheel drive rolling bearing unit 30 configured from such a viewpoint.
[0010]
In this wheel drive rolling bearing unit 30, the spline shaft 17 inserted into the spline hole 13 formed at the center of the hub 4b is prevented from coming off by a retaining ring 31 made of an elastic material. For this purpose, an outer diameter side locking portion such as a locking step 32 is provided at the outer end portion of the spline hole 13, and an inner diameter side locking portion such as a locking groove 33 is provided on the outer peripheral surface of the outer end portion of the spline shaft 17. Are provided. Then, the retaining ring 31 whose diameter is made elastically expandable / contractable by forming a spring steel wire rod in an annular shape is spanned between the locking step portion 32 and the locking groove 33. ing. In this manner, the retaining ring 31 prevents the spline shaft 17 from coming off from the spline hole 13, and the driving wheel rolling bearing unit 1b and the wheel side constant velocity joint 2 are coupled to each other, According to the structure in which is omitted, the wheel drive rolling bearing unit 30 can be reduced in size and weight.
[0011]
The wheel drive rolling bearing unit 30 as described above constitutes a wheel drive unit 34 in combination with the transmission shaft 24 and the differential side constant velocity joint 26 as shown in FIG. Among these, the differential side constant velocity joint 26 is coupled to an output portion of a differential gear (not shown) in a state of being assembled to an automobile. The transmission shaft 24 is connected to the inner end portion of the trunnion 27 which is an output portion of the differential side constant velocity joint 26 and to the inner ring 15 for the constant velocity joint which is an input portion of the wheel side constant velocity joint 2. The outer ends are joined to each other. By such a wheel drive unit 34, a rotational force is transmitted from the output portion of the differential gear to the drive wheel supported by the hub 4b, and the drive wheel is rotationally driven.
[0012]
In the case of the structure in which the inner ring 5 is fixed to the hubs 4a and 4b by the caulking portion 28 as shown in FIGS. 11 to 13 described above, by omitting the male screw portion 22 and the nut 23 from the structure shown in FIG. Not only can the cost be reduced, but also the wheel drive rolling bearing unit 30 and thus the wheel drive unit 34 can be reduced in size and weight. Of these, the rolling bearing unit 30 for driving the wheel is a so-called unsprung load that exists on the wheel side of the spring incorporated in the suspension device, so that a slight weight reduction can be achieved with a focus on ride comfort and running stability. Contributes to improved performance.
[0013]
[Problems to be solved by the invention]
It is necessary to secure sufficient strength of the caulking portion 28 for fixing the inner ring 5 to the hubs 4a and 4b constituting the driving wheel rolling bearing units 1a and 1b used for a long period of time. Therefore, the load required to form the caulking portion 28 is considerably large even if a method that can keep the load applied during processing, such as swing caulking, relatively low. Such a load is applied as a thrust load directed outward in the axial direction to the inner ends of the hubs 4a and 4b. For this reason, if no measures are taken, a part of the spline hole 13 formed in the center of the hubs 4a and 4b (particularly the portion near the inner end) is deformed inward in the radial direction although it is slight. This has been found as a result of experiments conducted by the present inventors.
[0014]
  That is, conventionally, a cylindrical portion 37 (described later) provided at the inner ends of the hubs 4a and 4b.A reference example1-2) is processed into the caulking portion 28, the cylindrical portion 37 is caulked outward in the radial direction, so that the inner end of the spline hole 13 located in the vicinity of the caulking portion 28 is It was thought to be deformed radially outward. However, as described above, since the thrust load applied during the processing of the caulking portion 28 is large and the influence of lateral strain on the thrust load is larger than previously thought, the spline in the vicinity of the caulking portion 28 is used. The inventors have found that the inner end of the hole 13 is deformed radially inward. In any case, when even a part of the spline hole 13 is deformed radially inward, it becomes difficult to insert the spline shaft 17 into the spline hole 13, and the assembly operation of the wheel drive rolling bearing unit 30 is performed. It becomes difficult to do.
[0015]
  In order to facilitate the insertion of the spline shaft 17 into the spline hole 13 regardless of the deformation of the spline hole 13, the inner diameter dimension of the spline hole 13 is set to the outer diameter dimension of the spline shaft 17. It is conceivable that the spline hole 13 is re-processed after the caulking portion 28 is processed. Of these, increasing the inner diameter of the spline hole 13 leads to an increase in backlash at the spline engaging portion between the spline hole 13 and the spline shaft 17 and may cause significant noise during driving of the automobile. Therefore, it is not preferable. Further, reworking the spline hole 13 is not preferable because it causes the manufacturing cost of the driving wheel rolling bearing units 1a and 1b to increase.
  Of the rolling bearing unit for driving wheels of the present inventionThe manufacturing method isInvented in view of such circumstances.
[0016]
[Means for Solving the Problems]
  Of the rolling bearing unit for driving wheels of the present inventionDepending on the manufacturing methodThe drive wheel rolling bearing unit to be manufactured includes an outer ring, a hub, an inner ring, and a plurality of rolling elements, like the conventionally known drive wheel rolling bearing unit.
  Of these, the outer ring has a first flange for coupling and fixing to the suspension device on the outer peripheral surface, and a double row outer ring raceway on the inner peripheral surface.
  The hub has a spline hole at the center, a second flange for supporting and fixing the drive wheel near the outer end of the outer peripheral surface, and a direct or separate inner ring at the intermediate portion of the outer peripheral surface. The first inner ring raceway has a fitting cylindrical surface portion at a portion near the inner end of the outer peripheral surface.
  The inner ring has a second inner ring raceway on the outer peripheral surface, and the cylindrical portion formed on the inner end portion of the hub is plastically deformed radially outward in a state of being externally fitted to the fitting cylindrical surface portion. The inner end face is held down by the caulking portion formed in this manner, and is fixed to the hub.
  Further, each of the rolling elements is provided so as to be capable of rolling plurally between the double row outer ring raceway and the first and second inner ring raceways.
[0017]
  In particular, in the method for manufacturing a driving wheel rolling bearing unit of the present invention, when the cylindrical portion is plastically deformed radially outward to form the caulking portion, a holding jig is provided on the inner diameter side of the hub.Insert only the inner end of the holding jig, the inner end of the spline hole, the outer end of the inner peripheral surface of the cylindrical part, the inner end of the spline hole and the inner periphery of the cylindrical part. A spline hole is formed in the outer end surface of the hub by engaging with at least one of the portions between the outer end portion of the surface and the front end surface of the hollow cylindrical support tube portion provided in the support jig. Only support the surrounding area ofBy placing the spline hole along with the caulking portion,Inner edge ofIs prevented from deforming to the inner diameter side.
[0019]
[Action]
  According to the method for manufacturing a rolling bearing unit for a drive wheel and the drive unit for a wheel of the present invention configured as described above, in particular, the inner diameter of the spline hole is increased or the spline hole is reworked after the caulking portion is formed. The spline shaft can be easily inserted into the spline hole even if it is not necessary.
  That is, when forming the caulking portion, a holding jig is inserted on the inner diameter side of the hub.Only the inner end portion of the holding jig is connected to the inner end portion of the spline hole, the outer end portion of the inner peripheral surface of the cylindrical portion, the inner end portion of the spline hole and the outer peripheral surface of the cylindrical portion. Engage with at least one of the parts between the endsBy placing the spline hole along with the caulking portion,Inner edge ofTherefore, the deformation of the spline hole can be suppressed regardless of the load applied to the hub when the cylindrical portion is plastically deformed to form the caulking portion.
  In addition, when forming the caulking portion, only the peripheral portion of the spline hole is supported on the outer end surface of the hub by the front end surface of the hollow cylindrical supporting cylinder portion provided in the support jig. It can prevent that a 2nd flange deform | transforms with a process. In other words, it is conceivable that the support jig has a large diameter and the upper end surface of the support jig supports the outer surface of the second flange formed on the outer peripheral surface of the hub. The second flange may be deformed. This deformation of the second flange increases the runout of the rotor that constitutes the disc brake, and increases the vibration and noise generated during braking. On the other hand, if the peripheral portion of the spline hole is supported on the outer end surface of the hub by the front end surface of the hollow cylindrical support cylinder portion provided in the support jig, such a problem does not occur.
[0020]
DETAILED DESCRIPTION OF THE INVENTION
  1 and 2 show the present invention.Example of reference exampleIs shown. still,Reference exampleThe feature of this is that when the caulking portion 28 is formed at the inner end portion of the hub 4c so as to suppress the inner end surface of the inner ring 5 fitted on the small diameter step portion 11 at the inner end portion of the hub 4c, In order to prevent deformation of the spline hole 13 formed in the central portion, the caulking portion 28 is processed with the restraining jig 41 inserted on the inner diameter side of the hub 4c. Regarding the basic structure and operation of the other parts, the second example of the conventional structure shown in FIG. 11 described above, or the structure of the second example shown in FIGS. Therefore, the same parts are denoted by the same reference numerals, and redundant description is omitted or simplified.Reference exampleThe description will focus on the features of the above and the portions different from those in the above examples.
[0021]
The inner peripheral surface and the inner end surface of the inner ring 5 are smoothly continuous by a chamfered portion 35 having a convex arc shape in cross section. Further, a stepped portion 36 is formed over the entire circumference at the inner end portion of the inner ring 5 and located on the radially outer side of the chamfered portion 35, and the thickness of the chamfered portion 35 portion in the radial direction is determined. This part is smaller than the thickness of the outer part. With this configuration, the second inner ring raceway formed on the outer peripheral surface of the intermediate part of the inner ring 5 regardless of the large force applied radially outward to the inner end part of the inner ring 5 with the work of forming the caulking part 28. The shape of 12 is prevented from being distorted.
[0022]
In order to form the caulking portion 28, the cylindrical portion 37 formed at the inner end portion of the hub 4c has an outer peripheral surface as a cylindrical surface, and the inner peripheral surface is slightly increased in a direction in which the inner diameter increases toward the inner end opening. (For example, the bus is about 0 to 5 degrees with respect to the central axis) and the tapered surface is inclined. In the illustrated example, a stepped portion 38 having a concave arc shape in cross section is formed at the boundary between the outer peripheral surface of the cylindrical portion 37 and the outer peripheral surface of the small-diameter stepped portion 11 for fitting the inner ring 5 externally. A slight step (for example, about 0.01 to 0.5 mm) is provided between the two outer peripheral surfaces. Such a stepped portion 38 becomes a base point of deformation when the cylindrical portion 37 is plastically deformed radially outward in order to form the caulking portion 28, and the caulking portion 28 extends from the cylindrical portion 37 to the caulking portion 28. Processing is provided to enable smooth processing without causing defects such as cracks and excessive voids. For this reason, the axial position of the boundary portion between the stepped portion 38 and the small diameter stepped portion 11 is substantially matched with the axial position of the outer end portion of the chamfered portion 35. Further, the outer peripheral edge portion of the front end surface (inner end surface) of the cylindrical portion 37 is chamfered, and the outer peripheral edge portion is free of cracks or the like regardless of the tensile force applied to the outer peripheral edge portion in the process. Damage is less likely to occur.
[0023]
Between the axial outer end portion of the inner peripheral surface of the cylindrical portion 37 as described above and the axial inner end portion of the spline hole 13 formed in the center portion of the hub 4c, a conical concave inclined surface portion is formed. 39 is formed. The inclined surface portion 39 has a conical concave shape inclined in a direction in which the diameter increases toward the inner side in the axial direction. The generatrix of the inclined surface portion 39 is inclined larger than the inner peripheral surface of the cylindrical portion 37 (for example, 20 to 70 degrees, more preferably 25 to 65 degrees) with respect to the central axis of the hub 4c. Such an inclined surface portion 39 functions as a guide surface for inserting, for example, a spline shaft 17 (see FIGS. 10 to 13) constituting the wheel side constant velocity joint 2 into the spline hole 13 by an automobile manufacturer. The insertion operation of the shaft 17 can be easily performed. The boundary portion between the inclined surface portion 39 and the inner peripheral surface of the cylindrical portion 37 is preferably slightly (eg, 0 to 2 mm) axially outward from the axially outer end position of the chamfered portion 35. Position.
[0024]
  When the cylindrical portion 37 having the above-described shape is plastically deformed radially outward to form the caulking portion 28, the hub 4c is placed in a state where the central axis of the hub 4c is arranged in the vertical direction. The outer end surface (lower surface) is supported by the support jig 40.The support jig 40 has a hollow cylindrical support cylinder portion 60, and supports the peripheral portion of the spline hole 13 on the outer end surface of the hub 4c on the upper end surface of the support cylinder portion 60.Further, the upper end portion of the holding jig 41 is inserted into the spline hole 13. A male spline portion 42 is formed at the upper end portion of the holding jig 41, and the male spline portion 42 extends from the outer end to the inner end (from the lower end) of the spline hole 13 during the work of the caulking portion 28. Until the upper end), the spline engagement is maintained without rattling over the entire length. The shape of the male spline portion 42 is a male spline portion formed on the outer peripheral surface of the spline shaft 17 that is inserted into the spline hole 13 in a state where the wheel drive unit 34 (see FIG. 13) is assembled. (See FIGS. 10 to 13).
[0025]
In the operation of plastically deforming the cylindrical portion 37 radially outward to form the caulking portion 28, the outer end surface of the hub 4c is supported by the support jig 40 as described above, and the restraining treatment is performed in the spline hole 13. In a state where the male spline part 42 of the tool 41 is inserted, the cylindrical part 37 is held down by a caulking jig 43 set on a ram (not shown) of the swing press device. The caulking jig 43 is supported in a state where the central axis is slightly inclined (for example, about 1 to 3 degrees) with respect to the vertical axis, and the cylinder is based on the swinging motion (swinging motion) based on this tilting. A large force directed outward in the axial direction is applied to a part of the portion 37 in the circumferential direction. Since the portion to which this force is applied continuously changes in the circumferential direction of the cylindrical portion 37, the cylindrical portion 37 is plastically deformed in the axial direction and radially outward over the entire circumference. The caulking portion 28 as shown in FIG.
[0026]
  In this way, when the cylindrical portion 37 is processed into the caulking portion 28, the inner end portion of the spline hole 13 tends to be deformed radially inward. However, since the male spline portion 42 of the holding jig 41 is inserted into the spline hole 13 up to the inner end portion, the inner end portion of the spline hole 13 is deformed radially inward. There is little to do. For this reasonReference exampleIf a rolling bearing unit for a drive wheel is manufactured by the manufacturing method described above, the spline hole 13 can be obtained without particularly increasing the inner diameter of the spline hole 13 or reworking the spline hole 13 after the caulking portion 28 is formed. The operation of inserting the spline shaft 17 (see FIGS. 10 to 13) into the hole 13 can be easily performed. In the state where the caulking portion 28 has been processed, the inner peripheral surface of the inner end portion of the spline hole 13 and the outer peripheral surface of the upper end portion of the male spline portion 42 may come into strong contact. However, the holding jig 41 provided with the male spline portion 42 can be extracted from the spline hole 13 with a large force by an actuator such as a hydraulic cylinder installed in a factory. Therefore, the operation of removing the holding jig 41 from the hub 4c after the caulking portion 28 is processed does not become particularly troublesome.
[0027]
  Next, FIG. 3 shows an embodiment of the present invention.First exampleIs shown. In the case of this example, on the inner peripheral surface of the portion near the inner end of the hub 4d, an inclined surface portion is provided between the outer end portion (lower end portion) of the cylindrical portion 37 and the inner end portion (upper end portion) of the spline hole 13. 39a and 39b are provided in two stages. A cylindrical surface portion 44 is formed between the inclined surface portions 39a and 39b. Of these, the inclined surface portion 39a near the spline hole 13 serves as a guide surface for inserting a spline shaft 17 (see FIGS. 10 to 13) constituting the wheel side constant velocity joint 2 into the spline hole 13 by an automobile manufacturer, for example. This function is used to facilitate the insertion work of the spline shaft 17. Accordingly, the bus bar of the inclined surface portion 39a near the spline hole 13 is inclined with respect to the central axis of the hub 4d, for example, about 0 to 60 degrees, more preferably about 0 to 45 degrees.
[0028]
On the other hand, the inclined surface portion 39b close to the cylindrical portion 37 has a role of continuing the cylindrical surface portion 44 and the inner peripheral surface of the cylindrical portion 37, and does not have a role as a guide surface. That is, the inclined surface portion 39b deforms only the cylindrical portion 37 when the caulking portion 28 is processed, so that the deformation of the cylindrical portion 37 does not reach the inner end portion of the spline hole 13. This is provided to increase the thickness of the portion adjacent to the inner end portion of 13. Therefore, the inclination angle of the bus bar of the inclined surface portion 39b near the cylindrical portion 37 with respect to the central axis of the hub 4d can be set to a large value of, for example, about 60 to 90 degrees. Of course, a smaller inclination angle may be used.
[0029]
  In the case of this example, when the cylindrical portion 37 is plastically deformed radially outward to form the caulking portion 28, the outer end surface of the hub 4d is placed with the central axis of the hub 4d arranged in the vertical direction. (Lower surface) is supported by the support jig 40. Further, a holding jig 41a is inserted into the spline hole 13 outwardly from the inner end opening of the spline hole 13 (from the top to the bottom in FIG. 3). The upper end portion of the holding jig 41a used in the implementation of this example is described above.Reference exampleSuch a male spline portion 42 (see FIG. 1) is not formed. Instead, an outward flange-shaped support collar portion 45 is formed at the upper end portion of the holding jig 41a. The support flange 45 has a shape and a size that can be fitted into the inclined surface portion 39a near the spline hole 13 and the cylindrical surface portion 44 so that the inner surface is substantially free of rattling. It is the same as or slightly smaller than the inner diameter of the surface portion 44.
[0030]
The holding jig 41a as described above continues to be pulled downward by a pulling device (not shown) during the processing operation for plastically deforming the cylindrical portion 37 into the caulking portion 28, so that the support flange 45 is fixed to the cylindrical portion. It is set to be located on the inner diameter side of the surface portion 44. In this state, the caulking jig 43 (see FIG. 1) is strongly pressed against the cylindrical portion 37, and the cylindrical portion 37 is plastically deformed radially outward to form the caulking portion 28. In this way, when the cylindrical portion 37 is processed into the caulking portion 28, the inner end portion of the spline hole 13 tends to be deformed radially inward. However, the supporting flange portion 45 of the holding jig 41a is fitted into the cylindrical surface portion 44 adjacent to the inside (upper side in FIG. 3) of the spline hole 13 by a slight interference fit or a gap fit with a very small gap. Therefore, the inner end portion of the spline hole 13 is not deformed inward in the radial direction so as to cause a practical problem.
[0031]
It should be noted that during the working operation of the caulking portion 28, the force for pulling down the holding jig 41a is a small value that can prevent the engagement between the cylindrical surface portion 44 and the support flange portion 45 (for example, Several hundred N). The reason for this is that if the force is increased too much and the hub 4d is compressed in the axial direction based on this force, each rolling element 6, as the hub 4d is elastically restored by releasing the force. This is because the preload applied to 6 is reduced or lost.
[0032]
  In addition, this pointReference example(And laterSecond to sixth examples), The maximum radius R of the point of application of the thrust load applied from the caulking jig 43 (see FIG. 1) to the caulking portion 28 as the caulking portion 28 is processed is determined by the support jig 40. The radial dimension of the support jig 40 and the caulking portion 28 is regulated so that the outer diameter D is less than or equal to 1/2 (R ≦ D / 2). The reason is to prevent the posture of the hub 4d from becoming unstable at the time of caulking even when the swaging caulking is employed, which can process the caulking portion 28 with a relatively light load.
[0033]
That is, swing caulking, in which a caulking load is applied only to a part in the circumferential direction and the position where the load is applied is moved in the circumferential direction, is compared to general caulking that deforms the entire circumference at once. While the load required for the caulking process can be made much smaller, the load applied to the workpiece becomes non-uniform in the circumferential direction. Therefore, when R> D / 2, and the processing load protrudes radially outward from the outer peripheral edge of the support surface of the support jig 40, the posture of the hub 4d placed on the support jig 40 is It becomes unstable and it becomes difficult to obtain a high-quality caulking portion 28. In order to stabilize the posture of the hub 4d, it can be considered that the force for pulling the holding jig 41a downward is increased, but it is difficult to adopt for the reasons described above. It is also conceivable that the support jig has a large diameter and the outer surface (lower surface) of the second flange 9 formed on the outer peripheral surface of the hub 4d is supported by the upper end surface of the support jig. The second flange 9 may be deformed with the processing. This deformation of the second flange 9 increases the runout of the rotor that constitutes the disc brake and increases the vibration and noise generated during braking, and therefore is difficult to adopt. On the other hand, if the maximum radius R is ½ or less of the outer diameter D (R ≦ D / 2), all these problems can be solved.
[0034]
  Next, FIG. 4 shows an embodiment of the present invention.Second exampleIs shown. In the case of this example, as shown in FIGS.Reference exampleUsing the same hub 4c as in the case ofFirst exampleThe inclined surface portion 39 existing between the inner end portion of the spline hole 13 and the outer end portion of the cylindrical portion 37 is supported from the inner diameter side by the support flange portion 45 of the holding jig 41a similar to the above. Even in the structure of this example, if the inclination angle of the inclined surface portion 39 is not extremely high, the inclined surface portion 39 is supported from the inner diameter side, and the inner end portion of the spline hole 13 has a diameter as the caulking portion is processed. It is possible to prevent deformation inward in the direction. The configuration and operation of other parts are as described above.First exampleIt is the same as the case of.
[0035]
  Next, FIG. 5 shows an embodiment of the present invention.Third exampleIs shown. The aboveReference example, first example of embodimentAnd aboveSecond exampleIn the case of this structure, the first inner ring raceway 10 is formed directly on the outer peripheral surface of the intermediate portion of the hubs 4c, 4d, whereas in this example, the first inner ring raceway 10 is provided on the outer peripheral surface. The formed inner ring 5a is externally fitted to the intermediate part of the hub 4e. The outer end surface of the inner ring 5 having the second inner ring raceway 12 formed on the outer peripheral surface is abutted against the inner end surface of the inner ring 5a. In the case of this example, the above-mentionedFirst exampleAnd aboveSecond exampleThe outer end portion of the cylindrical portion 37 is supported from the inner diameter side by the support flange portion 45 of the holding jig 41a similar to the case of. That is, the cylindrical portion 37 is processed into a caulking portion in a state in which the support flange portion 45 is fitted to the outer end portion of the cylindrical portion 37 by an interference fit or a gap fit with a very small gap. The structure and operation of other parts are described above.Second exampleIt is the same as the case of.
[0036]
  Next, FIG. 6 shows an embodiment of the present invention.Fourth exampleIs shown. In the case of this example, the inner peripheral surface of the cylindrical portion 37 is a tapered surface slightly inclined in a direction in which the inner diameter increases toward the inner end opening (the inclination angle α of the busbar with respect to the central axis is 10 degrees or less). Yes. Further, the outer peripheral surface of the support flange 45a formed at the upper end of the holding jig 41b is inclined by the same angle in the same direction as the inner peripheral surface of the cylindrical portion 37. Then, when the cylindrical portion 37 is plastically deformed to form the caulking portion 28 (see FIG. 2), the support flange portion 45a is fitted into the outer end portion of the cylindrical portion 37 in a wedge shape without a gap.
[0037]
  If the caulking portion 28 is formed by plastic deformation of the cylindrical portion 37 in this state, it is possible to prevent the inner end portion of the spline hole 13 from being deformed radially inward. Further, since the value of the inclination angle α is small, the force for displacing the support rod portion 45a upward is small in accordance with the force for the cylindrical portion 37 to be deformed radially inward. Therefore, during the caulking process, the force for pulling the holding jig 41b downward may be small, and the hydraulic equipment or the like for obtaining this force may be small. The configuration and operation of other parts are as described above.Third exampleIt is the same as the case of.
[0038]
  Next, FIGS. 7 to 8 show the embodiment of the present invention.5th exampleIs shown. In the case of this example, when the cylindrical portion 37 is plastically deformed to form the caulking portion 28, as a restraining jig 41c for preventing the inner end portion of the spline hole 13 from deforming radially inward. A combination of an outer diameter side restraining element 46 and an inner diameter side restraining element 47 is used. Of these, the outer diameter side restraining element 46 is formed in a substantially cylindrical shape as a whole, and a plurality of slits 48 are provided in the upper half (upper and lower indicate the state in which the caulking portion 28 is formed, as shown in FIG. 7). , 48 are formed so as to reach the upper end surface. And the elasticity of the direction which makes an outer diameter small is provided to the upper half part of the said outer diameter side suppression element 46, narrowing the width | variety of each said slit 48,48. Each of the slits 48, 48 is provided as many as 6 to 8 on the circumference so as to increase the diameter expansion / contraction amount of the large-diameter cylindrical surface portion 49 described below based on elastic deformation, and the axial direction The length is as long as possible.
[0039]
  A large-diameter cylindrical surface portion 49 is provided on the upper end portion of the outer-diameter side restraining element 46 to support a portion near the inner end of the inner peripheral surface of the hub 4f from the inner diameter side. In the state where the outer diameter of the upper half portion of the outer diameter side restraining element 46 is elastically contracted, the outer diameter of the large-diameter cylindrical surface portion 49 is equal to or smaller than the diameter of the tip circle of the spline hole 13. Further, in the portion near the inner end of the inner peripheral surface of the hub 4f, the portion adjacent to the inner end of the spline hole 13Large diameter cylindrical surfaceA cylindrical surface portion 50 for abutting 49 is formed. The inner diameter of the cylindrical surface portion 50 is the same as or slightly larger than the diameter of the root circle of the spline hole 13.
[0040]
  On the other hand, on the inner peripheral surface of the upper end portion of the outer diameter side restraining element 46, an inner diameter side taper engagement portion 51 having a partially conical concave shape inclined in a direction in which the inner diameter increases toward the upper end is formed. Accordingly, an outer diameter side taper engaging portion 52 is formed at the upper end portion of the inner diameter side restraining element 47 so that the outer diameter increases toward the upper side. The diameter of the upper end portion of the outer diameter side restraining element 46 is:This outer diameter side restraining elementThe inner diameter side restraining element 47 with respect to 46 expands and contracts due to the engagement between the inner diameter side and outer diameter side engaging portions 51, 52. The outer diameter side restraining element 46 and the inner diameter side restraining element 47 are formed in the lower end portion of the inner diameter side restraining element 47 through the through hole 53 formed in the lower end portion of the outer diameter side restraining element 46. They are coupled by bolts 55 screwed into the screw holes 54. A locking concave hole 56 such as a hexagon hole is formed on the upper end surface of the inner diameter side restraining element 47 for locking a tool such as a hexagon wrench. Further, a compression spring 57 is provided between the outer diameter side restraining element 46 and the inner diameter side restraining element 47, and the inner diameter side restraining element 47 is given elasticity in the direction of coming out of the outer diameter side restraining element 46. ing.
[0041]
  In the case of this example, the cylindrical surface portion 50 is restrained from the inner diameter side by the large diameter cylindrical surface portion 49 of the outer diameter side restraining element 46 prior to the working operation of the caulking portion 28. In order to perform this operation, first, at least the outer diameter side taper engaging portion 52 of the inner diameter side restraining element 47 is not positioned on the inner diameter side of the inner diameter side taper engaging portion 51 of the outer diameter side restraining element 46. . And aboveLarge diameter cylindrical surfaceIn a state where the diameter of 49 is reduced,Large diameter cylindrical surface49 is positioned on the inner diameter side of the cylindrical surface portion 50. This operation is performed by fitting the hub 4f from the upper side to the lower side with respect to the outer diameter side holding element 46.
[0042]
  Next, a tool is locked in the locking concave hole 56 and the bolt 55 is tightened while preventing the rotation of the inner diameter side restraining element 47, and the outer diameter side taper engagement of the inner diameter side restraining element 47 is performed. The portion 52 is pulled into the inner diameter side of the inner diameter side taper engaging portion 51 of the outer diameter side restraining element 46. Along with this drawing, the diameter of the upper half of the outer diameter side restraining element 46 widens,Large diameter cylindrical surface49 is in close contact with the cylindrical surface portion 50. As a result, the inner end portion of the spline hole 13 is restrained so that the inner diameter does not shrink, so that the cylindrical portion 37 formed at the inner end portion of the hub 4f is the same as in each of the above examples. Is crimped radially outward to form the caulking portion 28. After the caulking portion 28 is formed, the tool is again locked in the locking recess 56, and the bolt 55 is loosened while preventing the inner diameter side restraining element 47 from rotating. Then, the inner diameter side restraining element 47 is pushed upward by the compression spring 57 and displaced upward, and the outer diameter side taper engaging portion 52 of the inner diameter side restraining element 47 is engaged with the inner diameter side taper engagement of the outer diameter side restraining element 46. Exit from the joint 51. As a result, the diameter of the upper half portion of the outer diameter side restraining element 46 is reduced, so that the hub 4f is extracted upward. FIG. 7 shows a case where the outer diameter side restraining element 46 and the support jig 40a, which are separated from each other, are fitted and combined, but these outer diameter side restraining element 46 and the support jig 40a. And may be integrated. The structure and operation of the other parts are the same as those in the above examples.
[0043]
  In addition, after processing the above caulking portion, if there is a gap between the inner peripheral surface of the inner end of the hub and the outer peripheral surface of the holding jig for the work of removing the holding jig, Based on the gap, it is inevitable that the inner diameter of the hub is reduced by the amount of elastic deformation when the restraining jig is removed after processing. On the other hand, in the case of this example, by using a restraining jig 41c that can be expanded and contracted and adjusting the tightening torque of the bolt 55, the amount of expansion of the inner diameter of the hub 4f when the caulking portion 28 is processed can be increased. The caulking portion 28 can be processed after being controlled in advance. For this reason, the amount of change in the inner diameter dimension of the hub 4f before and after the caulking portion 28 is processed can be minimized. Moreover, as in this example, the method for suppressing the cylindrical surface portion 50 of the hub 4f has been described above.Reference exampleUnlike the method of suppressing the spline hole part as described above, not only is it unnecessary to match the circumferential phase of the holding jig to engage both male and female splines, but also the mold of the holding jig There is an advantage that it is easy to make. However, as a modification of the present example, a portion of the outer peripheral surface of the holding jig that contacts the inner peripheral surface of the hub may be a male spline, and the spline hole 13 may be suppressed by this portion.
[0044]
  Next, FIG. 9 shows an embodiment of the present invention.6th exampleIs shown. In the case of this example, when the cylindrical portion 37 provided at the inner end portion of the hub 4g is plastically deformed radially outward to form the caulking portion 28, the spline hole 13 provided at the center portion of the hub 4g. The holding jig 41d is fitted into the inner end portion. For this purpose, the holding jig 41d used in this example is formed in a truncated cone shape whose outer diameter decreases toward the lower side (upper and lower indicate the state in which the caulking portion 28 is formed, as shown in FIG. 9). ing. Further, on the outer peripheral surface of the holding jig 41d, concave grooves 58 and 58 for allowing the spline teeth formed on the inner peripheral surface of the spline hole 13 to enter are formed in the axial direction. The deformation of the spline hole 13 of the hub 4g due to the processing of the caulking portion 28 occurs locally at the inner end of the spline hole 13 in the axial direction. Using the holding jig 41d, the holding jig 41d and the inner end of the spline hole 13 are engaged with each other without a gap.
[0045]
When the cylindrical portion 37 is plastically deformed radially outward to form the caulking portion 28, the pressing jig 41 d is pressed against the hub 4 g via the compression spring 59 by the lower surface of the caulking jig 43. Meanwhile, the cylindrical portion 37 is plastically deformed by the caulking jig 43. As a result, the crimping portion 28 can be processed while suppressing the inner diameter of the inner end portion of the spline hole 13 from being reduced. If the compression spring 59 has its lower end or upper end joined to the upper surface of the restraining jig 41d or the lower surface of the caulking jig 43, the handleability is improved and the caulking part 28 is processed. Positioning at the time. The structure and operation of the other parts are the same as those in the above examples.
[0046]
【The invention's effect】
  Of the rolling bearing unit for driving wheels of the present inventionThe manufacturing method isSince it is configured and operates as described above, it is possible to realize a structure that is small and lightweight and can contribute to improving the running performance of the automobile at a lower cost.
[Brief description of the drawings]
FIG. 1 shows the present invention.Example of reference exampleSectional drawing which shows this in the state which processes a crimp part.
FIG. 2 is a cross-sectional view showing a state after the caulking portion is processed.
FIG. 3 shows an embodiment of the present invention.First exampleThe figure similar to FIG.
[Figure 4]Second exampleThe figure similar to FIG.
[Figure 5]Third exampleThe figure similar to FIG.
[Fig. 6]Fourth exampleThe figure similar to FIG.
[Figure 7]5th exampleThe figure similar to FIG.
8 is a perspective view showing a state in which an outer diameter side restraining element is taken out and viewed obliquely from below in FIG. 7;
FIG. 9 shows an embodiment of the present invention.6th exampleThe figure similar to FIG.
FIG. 10 is a cross-sectional view showing a first example of a conventional structure.
FIG. 11 is a half sectional view showing the second example.
FIG. 12 is a cross-sectional view showing an improved structure of the second example.
FIG. 13 is a sectional view of a wheel drive unit incorporating the improved structure.
[Explanation of symbols]
    1, 1a, 1b Driving wheel rolling bearing unit
    2 Wheel side constant velocity joint
    3 outer ring
    4, 4a, 4b, 4c, 4d, 4e, 4f, 4g hub
    5, 5a Inner ring
    6 Rolling elements
    7 First flange
    8 Outer ring raceway
    9 Second flange
  10 First inner ring raceway
  11 Small diameter step
  12 Second inner ring raceway
  13 Spline hole
  14 Outer ring for constant velocity joint
  15 Inner ring for constant velocity joint
  16 balls
  17 Spline shaft
  18 Outer diameter side engaging groove
  19 Second spline hole
  20 Inner diameter side engaging groove
  21 Cage
  22 Male thread
  23 Nut
  24 Transmission shaft
  25 Male spline section
  26 Differential side constant velocity joint
  27 Trunnion
  28 Caulking part
  29 Step surface
  30 Rolling bearing unit for wheel drive
  31 Retaining ring
  32 Locking step
  33 Locking groove
  34 Wheel drive unit
  35 Chamfer
  36 Stepped part
  37 Cylindrical part
  38 steps
  39, 39a, 39b Inclined surface
  40, 40a Support jig
  41, 41a, 41b, 41c, 41d Holding jig
  42 Male spline section
  43 Caulking jig
  44 Cylindrical surface
  45, 45a Support collar
  46 Outer diameter side restraining element
  47 Inner diameter side restraining element
  48 slits
  49 Large diameter cylindrical surface
  50 Cylindrical surface
  51 Inner diameter side taper engagement part
  52 Outer diameter side taper engagement part
  53 through holes
  54 Screw holes
  55 volts
  56 Locking recess
  57 Compression spring
  58 Groove
  59 Compression spring
  60 Support cylinder

Claims (3)

外輪と、ハブと、内輪と、複数の転動体とを備え、
このうちの外輪は、外周面に懸架装置に結合固定する為の第一のフランジを、内周面に複列の外輪軌道を、それぞれ有するものであり、
上記ハブは、中心部にスプライン孔を、外周面の外端寄り部分に駆動輪を支持固定する為の第二のフランジを、外周面の中間部に直接又は別体の内輪を介して第一の内輪軌道を、外周面の内端寄り部分に嵌合円筒面部を、それぞれ有するものであり、
上記内輪は、外周面に第二の内輪軌道を有し、上記嵌合円筒面部に外嵌した状態で、上記ハブの内端部に形成された円筒部を径方向外方に塑性変形させて形成されたかしめ部により内端面を抑え付けられて、上記ハブに固定されたものであり、
上記各転動体は、上記複列の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転動自在に設けられているものである駆動輪用転がり軸受ユニットを製造する為、上記円筒部を径方向外方に塑性変形させて上記かしめ部とする際に、
上記ハブの内径側に抑え治具を挿入し、この抑え治具の内端部のみを、上記スプライン孔の内端部と、上記円筒部の内周面の外端部と、このスプライン孔の内端部とこの円筒部の内周面の外端部との間部分とのうちの少なくとも何れかの部分に係合させると共に、
サポート治具に設けた中空筒状の支持筒部の先端面により、上記ハブの外端面でスプライン孔の周囲部分のみを支承しておく事により、上記かしめ部の加工に伴って上記スプライン孔の内端部が内径側に変形する事を防止する
駆動輪用転がり軸受ユニットの製造方法。An outer ring, a hub, an inner ring, and a plurality of rolling elements;
Of these, the outer ring has a first flange for coupling and fixing to the suspension device on the outer peripheral surface, and a double row outer ring raceway on the inner peripheral surface.
The hub has a spline hole at the center, a second flange for supporting and fixing the drive wheel near the outer end of the outer peripheral surface, and a first flange directly or through a separate inner ring at the intermediate portion of the outer peripheral surface. Each having an inner ring raceway and a fitting cylindrical surface portion on the inner end portion of the outer peripheral surface,
The inner ring has a second inner ring raceway on an outer peripheral surface, and in a state where the inner ring is fitted on the fitting cylindrical surface part, the cylindrical part formed on the inner end part of the hub is plastically deformed radially outward. The inner end face is suppressed by the formed caulking portion, and is fixed to the hub.
Each of the rolling elements manufactures a rolling bearing unit for a drive wheel, in which a plurality of rolling elements are provided between the double row outer ring raceway and the first and second inner ring raceways. Therefore, when the cylindrical portion is plastically deformed radially outward to form the caulking portion,
A holding jig is inserted into the inner diameter side of the hub, and only the inner end of the holding jig is inserted into the inner end of the spline hole, the outer end of the inner peripheral surface of the cylindrical part, and the spline hole. Engaging with at least one of the portion between the inner end and the outer end of the inner peripheral surface of the cylindrical portion;
By supporting only the peripheral portion of the spline hole on the outer end surface of the hub by the front end surface of the hollow cylindrical support cylinder portion provided in the support jig, the spline hole is formed along with the caulking portion . A method for manufacturing a rolling bearing unit for a drive wheel that prevents the inner end from being deformed to the inner diameter side. 抑え治具がスプライン孔に、このスプライン孔の内端側開口部から挿入されるものであり、この抑え治具は、その外径が挿入方向先端側に向かう程小さくなる円すい台状であり、この抑え治具を上記スプライン孔の内端部に隙間なく係合させた状態で円筒部を径方向外方に塑性変形させる、請求項１に記載した駆動輪用転がり軸受ユニットの製造方法。  The holding jig is inserted into the spline hole from the opening on the inner end side of the spline hole, and this holding jig is a truncated cone shape whose outer diameter decreases toward the distal end side in the insertion direction. The method for manufacturing a rolling bearing unit for a drive wheel according to claim 1, wherein the cylindrical portion is plastically deformed radially outward in a state where the holding jig is engaged with the inner end portion of the spline hole without any gap. 抑え治具として、その外周面に、スプライン孔の内周面に形成したスプライン歯を進入させる凹溝を軸方向に形成しているものを使用する、請求項２に記載した駆動輪用転がり軸受ユニットの製造方法。  The rolling bearing for a drive wheel according to claim 2, wherein the holding jig is formed with a groove in the axial direction for allowing the spline teeth formed on the inner peripheral surface of the spline hole to enter the outer peripheral surface thereof. Unit manufacturing method.
JP2002051988A 2001-03-15 2002-02-27 Method for manufacturing rolling bearing unit for driving wheel Expired - Fee Related JP4114368B2 (en)

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DE112005002498T5 (en) 2004-10-08 2007-09-06 Ntn Corp. Wheel support bearing assembly
JP4706242B2 (en) 2004-11-30 2011-06-22 株式会社ジェイテクト Method of manufacturing rolling bearing device and rolling bearing device
JP4519005B2 (en) * 2005-06-02 2010-08-04 Ｎｔｎ株式会社 Wheel bearing device
US7874734B2 (en) 2005-06-02 2011-01-25 Ntn Corporation Wheel support bearing assembly
US20090154856A1 (en) 2005-12-05 2009-06-18 Ntn Corporation Wheel Support Bearing Assembly and Method of Manufacturing the Same
JP2007271045A (en) * 2006-03-31 2007-10-18 Jtekt Corp Wheel rolling bearing device manufacturing method
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