JP2005082105A - Hub with stud and wheel support hub unit - Google Patents

Hub with stud and wheel support hub unit Download PDF

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Publication number
JP2005082105A
JP2005082105A JP2003319447A JP2003319447A JP2005082105A JP 2005082105 A JP2005082105 A JP 2005082105A JP 2003319447 A JP2003319447 A JP 2003319447A JP 2003319447 A JP2003319447 A JP 2003319447A JP 2005082105 A JP2005082105 A JP 2005082105A
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Prior art keywords
mounting flange
hub
bulging
mounting
studs
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JP2003319447A
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Japanese (ja)
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Takeo Okuma
健夫 大熊
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NSK Ltd
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NSK Ltd
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Priority to JP2003319447A priority Critical patent/JP2005082105A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
    • 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
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/64—Special methods of manufacture

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To materialize a structure capable of suppressing wobbling of a brake rotor supported and fixed on an outer side surface irrespective of existence of bulge parts 24, 24 formed at circumference parts of attachment holes 14, 14 of the outer surface of an attachment flange 13b accompanying with press-fitting of studs which are not illustrated in the attachment holes 14, 14. <P>SOLUTION: A center part of the attachment flange 13b in a radial direction is bent after the studs which are not illustrated are press-fitted and fixed in the attachment holes 14, 14. Consequently, a problem mentioned above is solved by positioning a tip surface of the bulge parts 24, 24 on a same plane as an inner part of an outer surface of the attachment flange 13b in the radial direction. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

この発明に係るスタッド付ハブ及び車輪支持用ハブユニットは、自動車の車輪、並びに、ロータやドラム等の制動用回転部材を、懸架装置に対して回転自在に支持する為に利用する。   A hub with a stud and a hub unit for supporting a wheel according to the present invention are used for rotatably supporting a vehicle wheel and a braking rotating member such as a rotor and a drum with respect to a suspension device.

自動車の車輪を構成するホイール１、及び、制動用回転部材であって制動装置であるディスクブレーキを構成するロータ２は、例えば図４に示す様な構造により、懸架装置を構成するナックル３に回転自在に支持している。即ち、このナックル３に形成した円形の支持孔４部分に、車輪支持用ハブユニット５を構成する外輪６を、複数本のボルト７により固定している。一方、この車輪支持用ハブユニット５を構成するハブ８に上記ホイール１及びロータ２を、複数本のスタッド９とナット１０とにより結合固定している。   A wheel 1 constituting a wheel of an automobile and a rotor 2 constituting a disc brake as a braking device and a braking device rotate to a knuckle 3 constituting a suspension device, for example, by a structure as shown in FIG. Supports freely. That is, the outer ring 6 constituting the wheel support hub unit 5 is fixed to the circular support hole 4 formed in the knuckle 3 by a plurality of bolts 7. On the other hand, the wheel 1 and the rotor 2 are coupled and fixed to a hub 8 constituting the wheel support hub unit 5 by a plurality of studs 9 and nuts 10.

上記外輪６の内周面には複列の外輪軌道１１ａ、１１ｂを、外周面には結合フランジ１２を、それぞれ形成している。この様な外輪６は、この結合フランジ１２を上記ナックル３に、上記各ボルト７で結合する事により、このナックル３に対し固定している。これに対し、上記ハブ８の外周面の一部で、上記外輪６の外端開口（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、図１、２の下側、図３〜８の左側を言う。反対に、自動車への組み付け状態で車両の幅方向中央側となる、図１、２の上側、図３〜８の右側を「内」と言う。本明細書全体で同じ。）から突出した部分には、取付フランジ１３を形成している。上記ホイール１及びロータ２はこの取付フランジ１３の外側面に、上記各スタッド９とナット１０とにより、結合固定している。   Double row outer ring raceways 11a and 11b are formed on the inner peripheral surface of the outer ring 6, and a coupling flange 12 is formed on the outer peripheral surface. Such an outer ring 6 is fixed to the knuckle 3 by connecting the connecting flange 12 to the knuckle 3 with the bolts 7. On the other hand, in the part of the outer peripheral surface of the hub 8, the outer end opening of the outer ring 6 ("outside" with respect to the axial direction is the outer side in the width direction of the vehicle when assembled in an automobile. 3 and 8 is the left side of Fig. 3 and 8. On the contrary, the upper side of Figs. A mounting flange 13 is formed in a portion protruding from the same in this specification. The wheel 1 and the rotor 2 are coupled and fixed to the outer surface of the mounting flange 13 by the studs 9 and the nuts 10.

この為に具体的には、上記取付フランジ１３の外周寄り部分の円周方向複数個所に円形の取付孔１４を、それぞれこの取付フランジ１３を軸方向に貫通する状態で形成している。そして、これら各取付孔１４に上記各スタッド９を、上記取付フランジ１３の内側面側から挿入する事により、これら各スタッド９の基端（図４の右端）寄り部外周面に設けたセレーションやローレット溝等の凹凸面部１５を、上記各取付孔１４に圧入嵌合させている（高周波焼き入れ等の硬化処理を施した上記凹凸面部１５を、上記各取付孔１４の内周面に食い込ませている）。これと共に、上記各スタッド９の基端部に設けた鍔部２５を、上記取付フランジ１３の内側面に当接させている。これにより、上記各スタッド９を上記取付フランジ１３に結合固定した状態で、これら各スタッド９の先端（図４の左端）側部分に設けた雄ねじ部１６を上記取付フランジ１３の外側面から突出させている。そして、これら各スタッド９のうちこの取付フランジ１３の外側面から突出した部分を、上記ロータ２及びホイール１の内周寄り部分に設けた複数の通孔に挿通させると共に、上記ロータ２の内側面を上記取付フランジ１３の外側面に、上記ホイール１の内側面を上記ロータ２の外側面に、それぞれ重ね合わせている。そして更に、上記各雄ねじ部１６のうち上記ホイール１の外側面から突出した部分に、それぞれ上記ナット１０を螺合し、更に緊締する事により、上記ホイール１及びロータ２を上記取付フランジ１３の外側面に結合固定している。   For this purpose, specifically, circular mounting holes 14 are formed in a plurality of locations in the circumferential direction near the outer periphery of the mounting flange 13 so as to penetrate the mounting flange 13 in the axial direction. Then, by inserting the studs 9 into the mounting holes 14 from the inner surface side of the mounting flange 13, serrations provided on the outer peripheral surfaces near the base ends (right ends in FIG. 4) of the studs 9 An uneven surface portion 15 such as a knurled groove is press-fitted into each mounting hole 14 (the uneven surface portion 15 subjected to a hardening process such as induction hardening is bitten into the inner peripheral surface of each mounting hole 14. ing). At the same time, a flange 25 provided at the base end of each stud 9 is brought into contact with the inner surface of the mounting flange 13. As a result, in a state where the studs 9 are coupled and fixed to the mounting flanges 13, the male screw portions 16 provided on the tip (left end in FIG. 4) side portions of the studs 9 are protruded from the outer surface of the mounting flange 13. ing. And the part which protruded from the outer surface of this attachment flange 13 among these studs 9 is inserted in the several through-hole provided in the inner peripheral part of the said rotor 2 and the wheel 1, and the inner surface of the said rotor 2 Are superimposed on the outer surface of the mounting flange 13 and the inner surface of the wheel 1 is superimposed on the outer surface of the rotor 2, respectively. Further, the nut 10 is screwed into each of the male threaded portions 16 protruding from the outer surface of the wheel 1 and further tightened, whereby the wheel 1 and the rotor 2 are attached to the outside of the mounting flange 13. It is fixed to the side.

又、上記ハブ８の中間部外周面で、前記複列の外輪軌道１１ａ、１１ｂのうちの外側の外輪軌道１１ａに対向する部分には、内輪軌道１７ａを形成している。更に、上記ハブ８の内端部に形成した小径段部１８に、内輪１９を外嵌固定している。そして、この内輪１９の外周面に形成した内輪軌道１７ｂを、上記複列の外輪軌道１１ａ、１１ｂのうちの内側の外輪軌道１１ｂに対向させている。そして、これら各外輪軌道１１ａ、１１ｂと各内輪軌道１６ａ、１６ｂとの間に転動体２０、２０を、それぞれ複数個ずつ、転動自在に設けている。尚、図示の例では、これら各転動体２０、２０として玉を使用しているが、重量が嵩む自動車用のハブユニットの場合には、テーパころを使用する場合もある。   Further, an inner ring raceway 17a is formed on the outer peripheral surface of the intermediate portion of the hub 8 at a portion of the double row outer ring raceways 11a, 11b facing the outer outer raceway 11a. Further, an inner ring 19 is fitted and fixed to a small diameter step portion 18 formed at the inner end portion of the hub 8. The inner ring raceway 17b formed on the outer peripheral surface of the inner ring 19 is opposed to the inner outer ring raceway 11b of the double row outer ring raceways 11a and 11b. A plurality of rolling elements 20, 20 are provided between the outer ring raceways 11a, 11b and the inner ring raceways 16a, 16b, respectively, so as to freely roll. In the example shown in the figure, balls are used as the rolling elements 20 and 20, but in the case of a hub unit for an automobile having a heavy weight, tapered rollers may be used.

更に、図示の例は、駆動輪（ＦＦ車の前輪、ＦＲ車及びＲＲ車の後輪、４ＷＤ車の全輪）用の車輪支持用ハブユニット５である為、上記ハブ８の中心部に、スプライン孔２１を形成している。そして、このスプライン孔２１に、等速ジョイント２２のスプライン軸２３を挿入している。又、この様に構成する車輪支持装置の使用時には、上記ロータ２と、前記ナックル３に固定した図示しないサポート及びキャリパとを組み合わせて、制動用のディスクブレーキを構成する。制動時には、上記ロータ２を挟んで設けた１対のパッドを、このロータ２の両側面に押し付ける。   Furthermore, since the illustrated example is a wheel support hub unit 5 for driving wheels (front wheels of FF vehicles, rear wheels of FR and RR vehicles, all wheels of 4WD vehicles), A spline hole 21 is formed. The spline shaft 23 of the constant velocity joint 22 is inserted into the spline hole 21. Further, when the wheel support device configured as described above is used, a disc brake for braking is configured by combining the rotor 2 and a support and a caliper (not shown) fixed to the knuckle 3. During braking, a pair of pads provided across the rotor 2 are pressed against both side surfaces of the rotor 2.

次に、図５は、車輪支持用ハブユニットの従来構造の第２例を示している。この第２例の車輪支持用ハブユニットの場合には、外側の内輪軌道１７ａを、ハブ８ａの中間部に外嵌した別体の内輪１９ａの外周面に形成している。その他の部分の構造及び作用は、上述の図４に示した従来構造の第１例の場合と同様である。   Next, FIG. 5 shows a second example of a conventional structure of a wheel supporting hub unit. In the case of the wheel supporting hub unit of the second example, the outer ring race 17a on the outer side is formed on the outer peripheral surface of a separate inner ring 19a that is externally fitted to the intermediate part of the hub 8a. The structure and operation of the other parts are the same as those of the first example of the conventional structure shown in FIG.

次に、図６は、車輪支持用ハブユニットの従来構造の第３例を示している。この第３例の車輪支持用ハブユニットは、従動輪（ＦＦ車の後輪、ＦＲ車及びＲＲ車の前輪）を支持する為に使用するものである。この為、ハブ８ｂの中心部には、スプライン軸を挿入する為のスプライン孔を設けていない。その他の部分の構造及び作用は、上述の図４に示した従来構造の第１例の場合と同様である。   Next, FIG. 6 shows a third example of a conventional structure of a wheel supporting hub unit. The wheel support hub unit of the third example is used to support driven wheels (rear wheel of FF vehicle, front wheel of FR vehicle and RR vehicle). For this reason, the spline hole for inserting a spline shaft is not provided in the center part of the hub 8b. The structure and operation of the other parts are the same as those of the first example of the conventional structure shown in FIG.

次に、図７は、車輪支持用ハブユニットの従来構造の第４例を示している。この第４例の車輪支持用ハブユニットも、従動輪を支持する為に使用するものである。この第４例の車輪支持用ハブユニットの場合、１対の内輪１９、１９ａを、それぞれ懸架装置に結合固定する静止輪とすると共に、ハブ８ｃを、車輪及び制動用回転部材を支持固定して回転する外輪としている。この為に、このハブ８ｃの内周面に、複列の外輪軌道１１ａ、１１ｂを形成している。   Next, FIG. 7 shows a fourth example of a conventional structure of a wheel supporting hub unit. The wheel support hub unit of the fourth example is also used to support the driven wheel. In the case of the wheel supporting hub unit of the fourth example, the pair of inner rings 19 and 19a are stationary wheels that are coupled and fixed to the suspension system, respectively, and the hub 8c is supported and fixed to the wheel and the brake rotating member. The outer ring rotates. For this purpose, double-row outer ring raceways 11a and 11b are formed on the inner peripheral surface of the hub 8c.

ところで、上述した様な各構造の車輪支持用ハブユニットを製造する際、前述した様に各スタッド９の凹凸面部１５を取付フランジ１３の各取付孔１４に圧入すると、圧入した部分でこれら各取付孔１４の内周面が押し広げられ、且つ、圧入方向に押される。この結果、図８に誇張して示す様に、これら各取付孔１４の周囲部分の肉が圧入方向前方に流動し、上記取付フランジ１５の外側面のうち上記各取付孔１６の周囲部分に膨出部２４が形成される。この様にして形成された各膨出部２４の膨出量は、同図に示す様に、上記取付フランジ１５の径方向内側部分よりも径方向外側部分で大きくなる。この理由は、上記取付フランジ１５のうち、上記各取付孔１４よりも径方向外側部分の剛性（径方向の肉厚）が、同じく径方向内側部分の剛性（径方向の肉厚）に比べて小さい為であり、結果として上記肉の流動量が径方向外側部分で径方向内側部分よりも多くなる為である。更に、上記各膨出部２４の膨出量は、一般的には、これら各膨出部２４同士で不均一になっている。従って、上述の様に各膨出部２４が形成された状態で、これら各膨出部２４の先端面（先端部の全周面）同士は、互いに同一平面上に位置していない。ところが、この様に同一平面上に位置していないままの状態にしておくと、上記取付フランジ１５の外側面に前記ロータ２を支持固定した場合に、このロータ２の制動用摩擦面（外径側部分の両側面）の回転振れ精度を良好にする事が難しくなる。そして、この回転振れ精度を良好にできなくなった場合には、回転時に上記各制動用摩擦面が軸方向に振れる様になる。この結果、前記パッドと上記各制動用摩擦面とが偏摩耗したり、更には制動時にジャダーと呼ばれる異音が発生する様になる。   By the way, when manufacturing the wheel support hub unit having each structure as described above, when the concave and convex surface portion 15 of each stud 9 is press-fitted into each mounting hole 14 of the mounting flange 13 as described above, each of these attachments is made at the press-fitted portion. The inner peripheral surface of the hole 14 is expanded and pressed in the press-fitting direction. As a result, as shown in an exaggerated manner in FIG. 8, the meat around the mounting holes 14 flows forward in the press-fitting direction, and bulges around the mounting holes 16 on the outer surface of the mounting flange 15. A protruding portion 24 is formed. The bulging amount of each bulging portion 24 formed in this way is larger at the radially outer portion than at the radially inner portion of the mounting flange 15 as shown in FIG. The reason for this is that the rigidity (diameter thickness) of the mounting flange 15 in the radially outer portion of each mounting hole 14 is also compared to the rigidity of the radially inner portion (diameter thickness). This is because the flow amount of the meat is larger at the radially outer portion than at the radially inner portion. Further, the bulging amount of the bulging portions 24 is generally nonuniform between the bulging portions 24. Therefore, in the state where the bulging portions 24 are formed as described above, the tip surfaces (the entire peripheral surfaces of the tip portions) of the bulging portions 24 are not located on the same plane. However, if the rotor 2 is supported and fixed on the outer surface of the mounting flange 15, the braking friction surface (outer diameter) of the rotor 2 is maintained when the rotor 2 is not positioned on the same plane. It becomes difficult to improve the rotational runout accuracy of both side surfaces of the side portion. When the rotational runout accuracy cannot be improved, the braking friction surfaces swing in the axial direction during rotation. As a result, the pads and the braking friction surfaces are partially worn, and abnormal noise called judder is generated during braking.

そこで、この様な不都合が発生するのを防止すべく、特許文献１には、取付孔にスタッドを圧入嵌合させた後、この圧入嵌合に伴って取付フランジの外側面に形成された膨出部を、旋削加工や研削加工により削り取る発明が記載されている。又、特許文献２には、取付孔にスタッドを圧入嵌合するのに先立って、取付フランジの外側面のうちこの取付孔の周囲部分に凹部を形成する事により、上記圧入嵌合に伴って上記取付フランジの外側面に膨出部が形成されるのを防止する発明が記載されている。これらの発明によれは、取付フランジの外側面にロータを支持固定した状態で、このロータの制動用摩擦面の回転振れ精度を良好にする事ができる。   Therefore, in order to prevent the occurrence of such inconvenience, Patent Document 1 discloses that a stud is press-fitted into a mounting hole, and then a bulge formed on the outer surface of the mounting flange as a result of the press-fitting. An invention is described in which the protruding portion is scraped off by turning or grinding. Further, in Patent Document 2, prior to press-fitting and fitting the stud into the mounting hole, a recess is formed in the peripheral portion of the mounting hole on the outer surface of the mounting flange. An invention for preventing the bulging portion from being formed on the outer surface of the mounting flange is described. According to these inventions, the rotational runout accuracy of the braking friction surface of the rotor can be improved in a state where the rotor is supported and fixed to the outer surface of the mounting flange.

ところが、上記特許文献１に記載された発明の場合には、上記取付フランジの外側面に形成された膨出部を削り取るべく、旋削加工や研削加工を施す際に、上記取付フランジの外側面から突出したスタッドの一部が邪魔になる為、製造作業を効率良く行なえない。又、上記特許文献２に記載された発明の場合には、上記取付フランジの外側面に凹部を設ける為、この取付フランジの強度が低下する。   However, in the case of the invention described in Patent Document 1, when turning or grinding is performed to scrape off the bulging portion formed on the outer surface of the mounting flange, the outer surface of the mounting flange is used. Since part of the protruding stud gets in the way, the manufacturing work cannot be performed efficiently. Further, in the case of the invention described in Patent Document 2, since the concave portion is provided on the outer surface of the mounting flange, the strength of the mounting flange is lowered.

米国特許第６，４１５，５０８号明細書US Pat. No. 6,415,508 特開２００２−４６４０８号公報JP 2002-46408 A

本発明のスタッド付ハブ及び車輪支持用ハブユニットは、上述の様な事情に鑑み、取付フランジの外側面に制動用回転部材を支持固定した状態で、制動用摩擦面の回転振れ精度を良好にでき、しかも製造作業を効率良く行なえると共に、上記取付フランジの強度を低下させない構造を実現すべく発明したものである。   The hub with a stud and the hub unit for supporting a wheel according to the present invention have improved rotational runout accuracy of the frictional surface for braking in a state where the rotating member for braking is supported and fixed to the outer surface of the mounting flange in view of the above situation. In addition, the present invention has been invented to realize a structure capable of efficiently performing a manufacturing operation and not reducing the strength of the mounting flange.

本発明のスタッド付ハブ及び車輪支持用ハブユニットのうち、請求項１に記載したスタッド付ハブは、外周面に取付フランジを形成すると共に、この取付フランジの円周方向複数個所に取付孔を、それぞれこの取付フランジを貫通する状態で形成したハブと、これら各取付孔に上記取付フランジの片側面側から圧入嵌合させた複数本のスタッドとを備える。
特に、本発明のスタッド付ハブに於いては、上記圧入嵌合に伴って上記取付フランジの他側面のうち上記各取付孔の周囲部分に形成された膨出部の先端面を、この取付フランジに施した塑性加工により同一平面上に位置させている。 Of the hub with studs and the hub unit for supporting wheels according to the present invention, the hub with studs according to claim 1 forms mounting flanges on the outer peripheral surface, and mounting holes at a plurality of locations in the circumferential direction of the mounting flanges. Each hub includes a hub formed so as to pass through the mounting flange, and a plurality of studs press-fitted into the mounting holes from one side of the mounting flange.
In particular, in the hub with studs of the present invention, the front end surface of the bulging portion formed in the peripheral portion of each mounting hole in the other side surface of the mounting flange in accordance with the press-fitting is connected to the mounting flange. It is located on the same plane by the plastic working applied to.

又、請求項４に記載した車輪支持用ハブユニットは、上記請求項１に記載したスタッド付ハブを回転輪として使用する。   A hub unit for supporting a wheel described in claim 4 uses the hub with a stud described in claim 1 as a rotating wheel.

上述の様に、本発明のスタッド付ハブ及び車輪支持用ハブユニットの場合には、取付フランジの他側面に形成された各膨出部の先端面を同一平面上に位置させている。この為、この取付フランジの他側面に制動用回転部材を支持固定した状態で、この制動用回転部材の制動用摩擦面の回転振れ精度を良好にする事ができる。従って、この制動用摩擦面とパッドとが偏摩耗するのを防止できると共に、制動時にジャダーが発生するのを防止できる。又、本発明の場合には、上記各膨出部の先端面を同一平面上に位置させる為に、上記取付フランジにプレス等による塑性加工を施す。前述した旋削加工や研削加工の場合と異なり、塑性加工の場合には、上記取付フランジの他側面からスタッドの一部が突出している場合でも、押し型を突き当てる位置やこの押し型の形状を工夫する等により、加工作業を容易に行なう事ができる。従って、製造作業を効率良く行なう事ができる。更に、本発明の場合には、上記取付フランジに凹部を形成しない為、この取付フランジの強度が低下すると言った不都合が生じる事はない。   As described above, in the case of the hub with a stud and the hub unit for supporting a wheel according to the present invention, the front end surface of each bulging portion formed on the other side surface of the mounting flange is positioned on the same plane. For this reason, in a state where the braking rotary member is supported and fixed to the other side surface of the mounting flange, the rotational runout accuracy of the braking friction surface of the braking rotary member can be improved. Therefore, it is possible to prevent the braking friction surface and the pad from being unevenly worn and to prevent judder from being generated during braking. Further, in the case of the present invention, the mounting flange is subjected to plastic working by pressing or the like in order to position the front end surface of each bulging portion on the same plane. Unlike the case of turning and grinding described above, in the case of plastic working, even if a part of the stud protrudes from the other side of the mounting flange, the position where the pressing die is abutted and the shape of this pressing die The processing work can be easily performed by devising. Therefore, the manufacturing operation can be performed efficiently. Further, in the case of the present invention, since the concave portion is not formed in the mounting flange, there is no inconvenience that the strength of the mounting flange is lowered.

本発明のスタッド付ハブ及び車輪支持用ハブユニットを実施する場合に好ましくは、請求項２に記載した様に、各膨出部の先端面を同一平面上に位置させる為、これら各膨出部を取付フランジの軸方向に圧縮する事により、この取付フランジの軸方向に関する、これら各膨出部の高さを均一にする（これら各膨出部の高さを、これら各膨出部の全周に亙り、且つ、これら各膨出部同士で均一にする）。
この場合に、より好ましくは、上記各膨出部の高さを総てゼロにする（これら各膨出部を消失させる）。この様にすれば、取付フランジの他側面に対する制動用回転部材の接触面積を十分に確保できる為、この制動用回転部材の支持剛性を十分に確保できる。 When implementing the hub with a stud and the hub unit for supporting a wheel of the present invention, preferably, as described in claim 2, in order to position the front end surface of each bulging portion on the same plane, Is compressed in the axial direction of the mounting flange, so that the height of each bulging portion in the axial direction of the mounting flange is made uniform (the height of each bulging portion is the total height of each bulging portion. It goes around the circumference and is uniform between these bulges).
In this case, more preferably, the height of each of the bulges is set to zero (the bulges are eliminated). In this way, since the contact area of the braking rotary member with the other side surface of the mounting flange can be sufficiently ensured, the support rigidity of the braking rotary member can be sufficiently ensured.

或は、請求項３に記載した様に、上記各膨出部の先端面を同一平面上に位置させる為、これら各膨出部の先端面のうち少なくとも取付フランジの径方向外側部分を、同一平面上に配置した治具の押し付け面によりこの取付フランジの軸方向に押圧する事で、この取付フランジの径方向中間部を湾曲させて、この取付フランジのうちこの湾曲させた部分よりも径方向外側部分を、径方向外側に向かう程軸方向片側に向かう方向に傾斜させる。
この場合に、より好ましくは、上記各膨出部の先端面を、上記取付フランジの他側面のうちこれら各膨出部より径方向内側の部分と同一平面上に位置させる。この様にすれば、上記取付フランジの他側面に対する制動用回転部材の接触面積を十分に確保できて、この制動用回転部材の支持剛性を十分に確保できる。 Alternatively, as described in claim 3, in order to position the tip surfaces of the bulges on the same plane, at least the radially outer portion of the mounting flange is the same among the tip surfaces of the bulges. By pressing in the axial direction of the mounting flange by the pressing surface of the jig placed on a flat surface, the radial intermediate portion of the mounting flange is curved, and the radial direction of the mounting flange is more radial than the curved portion. The outer portion is inclined in the direction toward one axial side as it goes radially outward.
In this case, more preferably, the front end surface of each of the bulging portions is positioned on the same plane as the portion of the other side surface of the mounting flange that is radially inward from the bulging portions. In this way, a sufficient contact area of the braking rotary member with the other side surface of the mounting flange can be ensured, and a supporting rigidity of the braking rotary member can be sufficiently ensured.

図１は、請求項１、２、４に対応する、本発明の実施例１を示している。尚、本例の特徴は、ハブ８ａ′を構成する取付フランジ１３ａ部分の構造にある。その他、このハブ８ａ′を含んで構成するスタッド付ハブ並びに車輪支持用ハブユニットの構造及び作用に就いては、前述の図５に示した従来構造の第２例の場合と同様であるから、重複する図示並びに説明は省略若しくは簡略にし、以下、本例の特徴部分を中心に説明する。   FIG. 1 shows a first embodiment of the present invention corresponding to claims 1, 2 and 4. The feature of this example is the structure of the mounting flange 13a constituting the hub 8a '. In addition, the structure and operation of the hub with stud and the hub unit for supporting the wheel that includes the hub 8a ′ are the same as those in the second example of the conventional structure shown in FIG. The overlapping illustrations and descriptions will be omitted or simplified, and the following description will focus on the features of this example.

本例のスタッド付ハブを造る場合には、先ず、前述した従来構造の場合と同様、上記取付フランジ１３ａに形成した複数の取付孔１４、１４にスタッド９、９を、それぞれこの取付孔１４、１４の内側面側から挿入する事により、これら各スタッド９、９の基端寄り部外周面に設けた凹凸面部１５を、上記各取付孔１４、１４に圧入嵌合させる。これと共に、上記各スタッド９、９の基端部に設けた鍔部２５、２５を、上記取付フランジ１３の内側面３０に当接させる。この結果、上記圧入嵌合に伴い、上記取付フランジ１３ａの外側面のうち上記各取付孔１４、１４の周囲部分に、それぞれ膨出部２４、２４（詳しくは図８参照）が形成される。前述した様に、これら各膨出部２４、２４の膨出量は、上記取付フランジ１３ａの径方向内側部分よりも径方向外側部分で大きくなっている。言い換えれば、これら各膨出部２４、２４は、上記取付フランジ１３ａの径方向内側部分の高さＨ1 よりも、径方向外側部分の高さＨ2 （図８参照）の方が大きく（Ｈ1 ＜Ｈ2 ）なっている。更に、上記各膨出部２４、２４の膨出量は、一般的には、これら各膨出部２４、２４同士で不均一になっている。従って、上述の様に各膨出部２４、２４が形成された状態で、これら各膨出部２４、２４の先端面（先端部の全周面）同士は、互いに同一平面上に位置していない。但し、本例の場合には、次述する製造工程により、上記各膨出部２４、２４の先端面同士を互いに同一平面上に位置させる。 When manufacturing the hub with studs of this example, first, as in the case of the conventional structure described above, the studs 9 and 9 are respectively provided in the plurality of mounting holes 14 and 14 formed in the mounting flange 13a. By inserting from the inner surface side of 14, the uneven surface portion 15 provided on the outer peripheral surface near the proximal end of each stud 9, 9 is press-fitted into the mounting holes 14, 14. At the same time, the flange portions 25, 25 provided at the base end portions of the studs 9, 9 are brought into contact with the inner side surface 30 of the mounting flange 13. As a result, bulging portions 24 and 24 (refer to FIG. 8 for details) are formed in the peripheral portions of the mounting holes 14 and 14 on the outer surface of the mounting flange 13a with the press-fitting. As described above, the bulging amount of each of the bulging portions 24, 24 is larger at the radially outer portion than at the radially inner portion of the mounting flange 13a. In other words, each of the bulging portions 24, 24 has a height H 2 (see FIG. 8) of the radially outer portion larger than the height H 1 of the radially inner portion of the mounting flange 13a (H 1 <H 2 ). Furthermore, the bulging amounts of the bulging portions 24 and 24 are generally nonuniform between the bulging portions 24 and 24. Therefore, in the state where the bulging portions 24, 24 are formed as described above, the tip surfaces (the entire peripheral surfaces of the tip portions) of the bulging portions 24, 24 are located on the same plane. Absent. However, in the case of this example, the front end surfaces of the bulging portions 24 and 24 are positioned on the same plane by the manufacturing process described below.

即ち、上記各膨出部２４、２４の先端面同士を互いに同一平面上に位置させる為に、本例の場合には、図１に示す様に、基台２６に固定した円筒状の下側治具２７と、有底円筒状の上側治具２８とにより、上記各膨出部２４、２４を軸方向に圧縮する。具体的には、上記下側治具２７の上面に形成した凹部３１の内側に、上記取付フランジ１３ａの外半部をがたつきなく挿入する事により、前記ハブ８ａ′の径方向の位置決めを図る。そして、この状態で、上記凹部３１の底面（上記ハブ８ａ′の中心軸と直交する平坦面）に、上記各膨出部２４、２４（実際には、他の部分に比べて膨出量が大きくなっている、一部の膨出部２４、２４）の先端面のうち、上記取付フランジ１３ａの外径側部分を当接させる。この際に、上記取付フランジ１３ａの外側面から突出した上記各スタッド９、９の先端側部分は、それぞれ上記下側治具２７に形成した円孔２９、２９内に進入させる。これと共に、上記上側治具２８の中心部に形成した凹部３２の内側に、上記ハブ８ａ′の内端部をがたつきなく挿入する事により、上記下側治具２７と上記上側治具２８との互いの中心軸同士を一致させる。そして、この状態で、この上側治具２８の下面（この上側治具２８の中心軸と直交する平坦面）を、上記取付フランジ１３ａの内側面３０のうち、前記各取付孔１４、１４のピッチ円よりも径方向内側部分（更に上記各スタッド９、９から外れた部分）に当接させる。これにより、上記下側治具２７の上面と上記上側治具２８の下面との間で上記各膨出部２４、２４を挟持する。そして、この状態で、上記上側治具２８に軸方向下向きの荷重Ｆ（例えば１〜１０トン程度）を加える事により、上記各膨出部２４、２４を軸方向に圧縮する。そして、これら各膨出部２４、２４の高さを、これら各膨出部２４、２４の全周に亙って均一（Ｈ1 ＝Ｈ2 ）にし、且つ、これら各膨出部２４、２４同士の間でも均一にする。この結果、これら各膨出部２４、２４の先端面が同一平面上に位置する。尚、本例の場合、上記下側治具２７の上面と上記上側治具２８の下面とには、それぞれ焼き入れ等の硬化処理を施している。 That is, in order to position the front end surfaces of the bulging portions 24, 24 on the same plane, in this example, as shown in FIG. 1, the cylindrical lower side fixed to the base 26 is used. The bulging portions 24 and 24 are compressed in the axial direction by the jig 27 and the bottomed cylindrical upper jig 28. Specifically, the outer half of the mounting flange 13a is inserted into the recess 31 formed on the upper surface of the lower jig 27 without rattling, thereby positioning the hub 8a 'in the radial direction. Plan. In this state, the bulging amount of each of the bulging portions 24 and 24 (actually, compared with other portions) on the bottom surface of the concave portion 31 (a flat surface perpendicular to the central axis of the hub 8a '). The outer diameter side portion of the mounting flange 13a is brought into contact with the front end surface of some of the enlarged bulging portions 24, 24). At this time, the tip side portions of the studs 9 and 9 protruding from the outer surface of the mounting flange 13 a are respectively inserted into the circular holes 29 and 29 formed in the lower jig 27. At the same time, the lower jig 27 and the upper jig 28 are inserted into the recess 32 formed in the center of the upper jig 28 by inserting the inner end of the hub 8a ′ without rattling. The center axes of each other are matched. In this state, the lower surface of the upper jig 28 (a flat surface orthogonal to the central axis of the upper jig 28) is the pitch of the mounting holes 14 and 14 in the inner surface 30 of the mounting flange 13a. It is made to contact | abut to the radial inside part (part further removed from each said studs 9 and 9) rather than a circle. Accordingly, the bulging portions 24 and 24 are sandwiched between the upper surface of the lower jig 27 and the lower surface of the upper jig 28. In this state, the bulging portions 24, 24 are compressed in the axial direction by applying an axial downward load F (for example, about 1 to 10 tons) to the upper jig 28. And the height of each bulging part 24, 24 is made uniform (H 1 = H 2 ) over the entire circumference of each bulging part 24, 24, and each of these bulging parts 24, 24. Make even between each other. As a result, the tip surfaces of the bulging portions 24 and 24 are located on the same plane. In the case of this example, the upper surface of the lower jig 27 and the lower surface of the upper jig 28 are each subjected to hardening treatment such as quenching.

上述の様に、本例のスタッド付ハブ及び車輪支持用ハブユニットの場合には、取付フランジ１３ａの外側面に形成された各膨出部２４、２４の先端面を同一平面上に位置させている。この為、この取付フランジ１３ａの外側面にロータ２（図５参照）等の制動用回転部材を支持固定した状態で、この制動用回転部材の制動用摩擦面の回転振れ精度を良好にする事ができる。従って、この制動用摩擦面とパッドとが偏摩耗するのを防止できると共に、制動時にジャダーが発生するのを防止できる。又、本例の場合には、上記各膨出部２４、２４の先端面を同一平面上に位置させる為に、上記取付フランジ１３ａに圧縮加工（塑性加工）を施すが、この際に、この取付フランジ１３ａの外側面から突出した各スタッド９、９の先端側部分は、下側治具２７に形成した円孔２９、２９に挿入する。この為、上記圧縮加工を行なう際に、上記各スタッド９、９の先端側部分が邪魔になる事はない。従って、製造作業を効率良く行なう事ができる。更に、本例の場合には、上記取付フランジ１３ａに凹部を形成しない為、この取付フランジ１３ａの強度が低下すると言った不都合が生じる事はない。   As described above, in the case of the hub with studs and the hub unit for supporting wheels of the present example, the tip surfaces of the bulging portions 24 and 24 formed on the outer surface of the mounting flange 13a are positioned on the same plane. Yes. For this reason, in a state where the braking rotary member such as the rotor 2 (see FIG. 5) is supported and fixed on the outer surface of the mounting flange 13a, the rotational runout accuracy of the braking friction surface of the braking rotary member is improved. Can do. Therefore, it is possible to prevent the braking friction surface and the pad from being unevenly worn and to prevent judder from being generated during braking. In the case of this example, the mounting flange 13a is subjected to compression processing (plastic processing) in order to position the tip surfaces of the bulging portions 24, 24 on the same plane. The tip end portions of the studs 9 and 9 protruding from the outer surface of the mounting flange 13 a are inserted into circular holes 29 and 29 formed in the lower jig 27. For this reason, when performing the said compression process, the front end side part of each said stud 9 and 9 does not become obstructive. Therefore, the manufacturing operation can be performed efficiently. Furthermore, in the case of this example, since the concave portion is not formed in the mounting flange 13a, there is no inconvenience that the strength of the mounting flange 13a is reduced.

尚、本例を実施する場合、好ましくは、上記各膨出部２４、２４の高さをゼロにする（これら各膨出部２４、２４を消失させる）。この様にすれば、上記取付フランジ１３ａの外側面に対する制動用回転部材の接触面積を十分に確保できる為、この制動用回転部材の支持剛性を十分に確保できる。   In addition, when implementing this example, Preferably, the height of each said bulging part 24 and 24 is made into zero (these bulging parts 24 and 24 are lose | disappeared). In this way, since the contact area of the braking rotary member with the outer surface of the mounting flange 13a can be sufficiently secured, the support rigidity of the braking rotary member can be sufficiently secured.

次に、図２〜３は、請求項１、３、４に対応する、本発明の実施例２を示している。本例の場合も、上述した実施例１の場合と同様、先ず、ハブ８ａ″を構成する取付フランジ１３ｂに形成した各取付孔１４、１４に、それぞれスタッド９、９を圧入固定する。そして、この圧入固定に伴って上記取付フランジ１３ｂの外側面のうち上記各取付孔１４、１４の周囲に形成された膨出部２４、２４の先端面を、次述する製造工程により、同一平面上に位置させる。   Next, FIGS. 2 to 3 show a second embodiment of the present invention corresponding to claims 1, 3 and 4. Also in the case of this example, as in the case of the above-described first embodiment, first, the studs 9 and 9 are press-fitted and fixed in the respective mounting holes 14 and 14 formed in the mounting flange 13b constituting the hub 8a ″. In accordance with the press-fitting and fixing, the front end surfaces of the bulging portions 24 and 24 formed around the mounting holes 14 and 14 in the outer surface of the mounting flange 13b are placed on the same plane by the manufacturing process described below. Position.

即ち、上記各膨出部２４、２４の先端面を同一平面上に位置させる為に、本例の場合には、図２に示す様にして、上記取付フランジ１３ｂの径方向中間部の曲げ加工（塑性加工）を行なう。この曲げ加工を行なう為に、本例の場合も、上述した実施例１の場合と同様、下側治具２７ａの上面に形成した凹部３１の底面（押し付け面）に、上記各膨出部２４、２４（実際には、他の部分に比べて膨出量が大きくなっている、一部の膨出部２４、２４）の先端面のうち、上記取付フランジ１３ｂの径方向外側部分（膨出量が大きくなった部分）を当接させる。尚、この際に本例の場合には、上記取付フランジ１３ｂの外側面から突出した上記各スタッド９、９の先端側部分の一部を、それぞれ上記下側治具２７ｂに形成した断面円弧形の逃げ溝３３、３３内に進入させる。これと共に、上記上側治具２８ａの下面を、上記取付フランジ１３ｂの内側面３０のうち、各取付孔１４、１４のピッチ円よりも径方向内側部分（更に上記各スタッド９、９から外れた部分）に当接させる。但し、本例の場合、上記凹部３１の底面の内径Ｄは、上記上側治具２８ａの下面の外径ｄよりも大きく（Ｄ＞ｄ）している。又、上記下側治具２７ａの上面と上記上側治具２８ａの下面とには、それぞれ焼き入れ等の硬化処理を施している。そして、この状態で、上記上側治具２８ａに軸方向下向きの荷重Ｆ（例えば１〜１０トン程度）を加える。   That is, in order to position the front end surfaces of the bulging portions 24, 24 on the same plane, in the case of this example, as shown in FIG. 2, the bending process of the radial intermediate portion of the mounting flange 13b is performed. (Plastic working) is performed. In order to perform this bending process, also in the case of the present example, each bulging portion 24 is formed on the bottom surface (pressing surface) of the concave portion 31 formed on the upper surface of the lower jig 27a as in the case of the first embodiment. , 24 (actually, the bulging amount of the bulging portions 24, 24, which is larger than the other portions, of the bulging portions 24, 24) is the radially outer portion (bulging portion) of the mounting flange 13b. The part where the amount becomes large is brought into contact. In this case, in the case of this example, a cross-section arc formed by forming a part of the tip side portion of each of the studs 9 and 9 protruding from the outer surface of the mounting flange 13b on the lower jig 27b. It is made to enter into the shape escape grooves 33 and 33. At the same time, the lower surface of the upper jig 28a is positioned on the inner side surface 30 of the mounting flange 13b on the radially inner side of the pitch circles of the mounting holes 14 and 14 (further apart from the studs 9 and 9). ). However, in this example, the inner diameter D of the bottom surface of the concave portion 31 is larger than the outer diameter d of the lower surface of the upper jig 28a (D> d). Further, the upper surface of the lower jig 27a and the lower surface of the upper jig 28a are each subjected to hardening treatment such as quenching. In this state, an axially downward load F (for example, about 1 to 10 tons) is applied to the upper jig 28a.

これにより、上記取付フランジ１３ａの一部を塑性変形させて、総ての膨出部２４、２４の先端面のうち、上記取付フランジ１３ｂの径方向外側部分を、それぞれ上記下側治具２７の上面に当接させる。これと共に、図３（図３では、上記各スタッド９、９の図示を省略。）に誇張して示す様に、上記取付フランジ１３ｂの径方向中間部で、上記凹部３１の底面の内周縁と上記上側治具２８ａの下面の外周縁との間に対応する部分（上記各取付孔１４、１４のピッチ円付近）を湾曲させる。これにより、上記取付フランジ１３ｂのうち、この湾曲させた部分よりも径方向外側部分を、径方向外側に向かう程軸方向内側に向かう方向に傾斜させる。そして、この傾斜させる量を、後述する様にして規制する事により、上記各膨出部２４、２４の高さを、これら各膨出部２４、２４の全周に亙って実質的に均一（Ｈ1 ＝Ｈ2 ）にし、且つ、これら各膨出部２４、２４同士の間でも実質的に均一にする。これにより、上記各膨出部２４、２４の先端面を同一平面上に位置させる。尚、実際の場合、上記各膨出部２４、２４の先端面のうち、上記取付フランジ１３ｂの径方向内側部分の高さＨ2 は、無視できる程度に小さい（Ｈ2 ≒０）。従って、この状態で、これら各膨出部２４、２４の先端面と、上記取付フランジ１３ｂの外側面のうちこれら各膨出部２４、２４よりも径方向内側の部分とは、実質的に同一平面上に位置した状態となる。 As a result, a part of the mounting flange 13a is plastically deformed, and the radially outer portion of the mounting flange 13b of the front end surfaces of all the bulging portions 24, 24 is placed on the lower jig 27, respectively. Contact the top surface. At the same time, as shown exaggeratedly in FIG. 3 (the illustration of the studs 9 and 9 is omitted in FIG. 3), the inner peripheral edge of the bottom surface of the recess 31 is the radial intermediate portion of the mounting flange 13b. A corresponding portion (near the pitch circle of each of the mounting holes 14, 14) is curved between the outer peripheral edge of the lower surface of the upper jig 28a. Thereby, the radial direction outer side part is inclined in the direction which goes to an axial direction inner side, so that it goes to a radial direction outer side rather than the curved part among the said mounting flanges 13b. Then, by regulating the amount of inclination as described later, the height of each of the bulging portions 24, 24 is substantially uniform over the entire circumference of each of the bulging portions 24, 24. (H 1 = H 2 ) and substantially uniform between the bulging portions 24 and 24. Thereby, the front end surface of each said bulging part 24 and 24 is located on the same plane. In the actual case, the height H 2 of the radially inner portion of the mounting flange 13b is small enough to be ignored (H 2 ≈0) in the tip surfaces of the bulging portions 24, 24. Therefore, in this state, the front end surface of each of the bulging portions 24 and 24 and the radially inner portion of each of the outer surfaces of the mounting flange 13b from the bulging portions 24 and 24 are substantially the same. It will be in the state located on the plane.

尚、上述の様な位置関係を実現すべく、上記取付フランジ１３ｂの径方向外側部分の傾斜量を規制する為に本例の場合には、この取付フランジ１３ｂの径方向中間部の曲げ加工を行なう際に、この取付フランジ１３ｂの外側面のうち上記各膨出部２４、２４よりも径方向内側部分の軸方向位置を、赤外線レーザ等により検出している。そして、この軸方向位置が、上記凹部３１の底面の軸方向位置と一致するまで（或は弾性復元量を考慮して、この底面の軸方向位置よりも僅かに下方の位置となるまで）、上記曲げ加工を行なう様にしている。尚、上述した様に、図３では、上記各膨出部２４、２４の膨出量と、上記取付フランジ１３ｂの径方向中間部の湾曲量とを、それぞれ誇張して示している。これに対し、実際の場合には、これら膨出量と湾曲量とは非常に小さい為、上述の様に取付フランジ１３ｂを塑性変形させた場合でも、上記各スタッド９、９の中心軸が車輪及び制動用回転部材を支持固定する事に関して不都合を生じる程大きく傾斜する事はない。   In order to realize the positional relationship as described above, in the present example, in order to regulate the amount of inclination of the radially outer portion of the mounting flange 13b, bending of the intermediate portion in the radial direction of the mounting flange 13b is performed. When performing, the axial position of the radially inner portion of the outer surface of the mounting flange 13b relative to the bulging portions 24, 24 is detected by an infrared laser or the like. Until this axial position coincides with the axial position of the bottom surface of the recess 31 (or until the position is slightly lower than the axial position of the bottom surface in consideration of the amount of elastic recovery). The bending process is performed. As described above, in FIG. 3, the bulging amount of each of the bulging portions 24, 24 and the bending amount of the intermediate portion in the radial direction of the mounting flange 13b are exaggerated. On the other hand, in the actual case, since the bulging amount and the bending amount are very small, even when the mounting flange 13b is plastically deformed as described above, the central axis of each stud 9, 9 is a wheel. And the tilting is not so great as to cause inconvenience with respect to supporting and fixing the rotating member for braking.

上述の様に、本例のスタッド付ハブ及び車輪支持用ハブユニットの場合も、取付フランジ１３ｂの外側面に形成された各膨出部２４、２４の先端面を同一平面上に位置させている。この為、この取付フランジ１３ｂの外側面にロータ２（図５参照）等の制動用回転部材を支持固定した状態で、この制動用回転部材の制動用摩擦面の回転振れ精度を良好にする事ができる。従って、この制動用摩擦面とパッドとが偏摩耗するのを防止できると共に、制動時にジャダーが発生するのを防止できる。特に、本例の場合には、上記各膨出部２４、２４の先端面と、上記取付フランジ１３ｂの外側面のうちこれら各膨出部２４、２４よりも径方向内側の部分とを、実質的に同一平面上に位置させている。従って、上記取付フランジ１３ｂの外側面に対する上記制動用回転部材の接触面積を十分に確保できる為、この制動用回転部材の支持剛性を十分に確保できる。その他、上記取付フランジ１３ｂの外側面から突出した上記各スタッド９、９の先端側部分が、この取付フランジ１３ｂに曲げ加工を施す際に邪魔にならない点、並びに、この取付フランジ１３ｂの強度が低下する事がない点は、上述した実施例１の場合と同様である。   As described above, also in the case of the hub with studs and the hub unit for supporting wheels of the present example, the tip surfaces of the bulging portions 24, 24 formed on the outer surface of the mounting flange 13b are located on the same plane. . For this reason, in a state in which a braking rotating member such as the rotor 2 (see FIG. 5) is supported and fixed on the outer surface of the mounting flange 13b, the rotational runout accuracy of the braking friction surface of the braking rotating member is improved. Can do. Therefore, it is possible to prevent the braking friction surface and the pad from being unevenly worn and to prevent judder from being generated during braking. In particular, in the case of this example, the front end surface of each of the bulging portions 24 and 24 and the portion of the outer surface of the mounting flange 13b that is radially inward of the bulging portions 24 and 24 are substantially Are located on the same plane. Therefore, since the contact area of the braking rotary member with the outer surface of the mounting flange 13b can be sufficiently secured, the support rigidity of the braking rotary member can be sufficiently secured. In addition, the point on the tip side of each of the studs 9, 9 protruding from the outer surface of the mounting flange 13b does not get in the way when the mounting flange 13b is bent, and the strength of the mounting flange 13b is reduced. The point which does not do is the same as that of the case of Example 1 mentioned above.

尚、本発明のスタッド付ハブ及び車輪支持用ハブユニットは、上述の各実施例で示したハブに限らず、例えば、前述の図４、６、７に示したハブを含む、各種構造のハブを備えたスタッド付ハブ及び車輪支持用ハブユニットに適用可能である。   In addition, the hub with a stud and the hub unit for supporting a wheel of the present invention are not limited to the hubs shown in the above-described embodiments, but include various hubs including, for example, the hubs shown in FIGS. It can be applied to a hub with a stud and a hub unit for supporting a wheel.

本発明の実施例１を示す、スタッド付ハブの製造工程を示す断面図。Sectional drawing which shows the manufacturing process of the hub with a stud which shows Example 1 of this invention. 同実施例２を示す、図１と同様の図。The figure similar to FIG. 1 which shows the same Example 2. FIG. 取付フランジの曲げ加工後の状態をスタッドを省略して示す断面図。Sectional drawing which abbreviate | omits a stud and shows the state after a bending process of a mounting flange. 車輪支持用ハブユニットの従来構造の１例を、懸架装置に組み付けた状態で示す断面図。Sectional drawing which shows one example of the conventional structure of the hub unit for wheel support in the state assembled | attached to the suspension apparatus. 同第２例を示す、図４と同様の図。The figure similar to FIG. 4 which shows the 2nd example. 同第３例を示す断面図。Sectional drawing which shows the 3rd example. 同第４例を示す断面図。Sectional drawing which shows the 4th example. 取付フランジの部分拡大断面図。The partial expanded sectional view of a mounting flange.

符号の説明Explanation of symbols

１ ホイール
２ ロータ
３ ナックル
４ 支持孔
５ 車輪支持用ハブユニット
６ 外輪
７ ボルト
８、８ａ〜８ｃ、８ａ′、８ａ″ ハブ
９ スタッド
１０ ナット
１１ａ、１１ｂ 外輪軌道
１２ 結合フランジ
１３、１３ａ、１３ｂ 取付フランジ
１４ 取付孔
１５ 凹凸面部
１６ 雄ねじ部
１７ａ、１７ｂ 内輪軌道
１８ 小径段部
１９、１９ａ 内輪
２０ 転動体
２１ スプライン孔
２２ 等速ジョイント
２３ スプライン軸
２４ 膨出部
２５ 鍔部
２６ 基台
２７、２７ａ 下側治具
２８、２８ａ 上側治具
２９ 円孔
３０ 内側面
３１ 凹部
３２ 凹部
３３ 逃げ溝 DESCRIPTION OF SYMBOLS 1 Wheel 2 Rotor 3 Knuckle 4 Support hole 5 Wheel support hub unit 6 Outer ring 7 Bolt 8, 8a-8c, 8a ', 8a "Hub 9 Stud 10 Nut 11a, 11b Outer ring track 12 Coupling flange 13, 13a, 13b Mounting flange DESCRIPTION OF SYMBOLS 14 Mounting hole 15 Uneven surface part 16 Male thread part 17a, 17b Inner ring raceway 18 Small diameter step part 19, 19a Inner ring 20 Rolling element 21 Spline hole 22 Constant velocity joint 23 Spline shaft 24 Swelling part 25 Gutter part 26 Base 27, 27a Lower side Jig 28, 28a Upper jig 29 Circular hole 30 Inner surface 31 Recess 32 Recess 33 Relief groove

Claims (4)

外周面に取付フランジを形成すると共に、この取付フランジの円周方向複数個所に取付孔を、それぞれこの取付フランジを貫通する状態で形成したハブと、これら各取付孔に上記取付フランジの片側面側から圧入嵌合させた複数本のスタッドとを備えたスタッド付ハブに於いて、上記圧入嵌合に伴って上記取付フランジの他側面のうち上記各取付孔の周囲部分に形成された膨出部の先端面を、この取付フランジに施した塑性加工により同一平面上に位置させた事を特徴とするスタッド付ハブ。   A mounting flange is formed on the outer peripheral surface, and mounting holes are formed at a plurality of positions in the circumferential direction of the mounting flange, and the hubs are formed so as to pass through the mounting flanges. In a hub with studs that includes a plurality of studs that are press-fitted and fitted to each other, a bulging portion that is formed in a peripheral portion of each of the mounting holes on the other side surface of the mounting flange along with the press-fitting and fitting A hub with studs, characterized in that the front end surface of is mounted on the same plane by plastic working applied to the mounting flange. 各膨出部の先端面を同一平面上に位置させる為、これら各膨出部を取付フランジの軸方向に圧縮する事により、この取付フランジの軸方向に関する、これら各膨出部の高さを均一にした、請求項１に記載したスタッド付ハブ。   In order to position the tip surface of each bulging part on the same plane, by compressing each bulging part in the axial direction of the mounting flange, the height of each bulging part with respect to the axial direction of the mounting flange can be set. The hub with a stud according to claim 1, which is made uniform. 各膨出部の先端面を同一平面上に位置させる為、これら各膨出部の先端面のうち少なくとも取付フランジの径方向外側部分を、同一平面上に配置した治具の押し付け面によりこの取付フランジの軸方向に押圧する事で、この取付フランジの径方向中間部を湾曲させて、この取付フランジのうちこの湾曲させた部分よりも径方向外側部分を、径方向外側に向かう程軸方向片側に向かう方向に傾斜させた、請求項１に記載したスタッド付ハブ。   In order to position the tip surface of each bulge on the same plane, at least the radially outer portion of the mounting flange on the tip surface of each bulge is attached by the pressing surface of a jig arranged on the same plane. By pressing in the axial direction of the flange, the radial intermediate portion of the mounting flange is curved, and the radially outer portion of the mounting flange is moved more radially outward than the curved portion. The hub with a stud according to claim 1, wherein the hub is studded in a direction toward the head. 請求項１〜３の何れかに記載したスタッド付ハブを回転輪として使用する、車輪支持用ハブユニット。   A hub unit for supporting a wheel, wherein the hub with a stud according to any one of claims 1 to 3 is used as a rotating wheel.
JP2003319447A 2003-09-11 2003-09-11 Hub with stud and wheel support hub unit Pending JP2005082105A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
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Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
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Publication Number Publication Date
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Family Applications (1)

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Country Status (1)

Country Link
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008049790A (en) * 2006-08-23 2008-03-06 Nsk Ltd Bearing unit for wheel and manufacturing method for inner member or outer member with flange in the bearing unit for wheel

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008049790A (en) * 2006-08-23 2008-03-06 Nsk Ltd Bearing unit for wheel and manufacturing method for inner member or outer member with flange in the bearing unit for wheel

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