JP2010179670A - Rolling bearing unit for supporting wheel - Google Patents

Rolling bearing unit for supporting wheel Download PDF

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Publication number
JP2010179670A
JP2010179670A JP2009022210A JP2009022210A JP2010179670A JP 2010179670 A JP2010179670 A JP 2010179670A JP 2009022210 A JP2009022210 A JP 2009022210A JP 2009022210 A JP2009022210 A JP 2009022210A JP 2010179670 A JP2010179670 A JP 2010179670A
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Prior art keywords
flange
outer ring
ring member
hub
axial direction
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JP2009022210A
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Japanese (ja)
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Hideshi Shibuya
英志 渋谷
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NSK Ltd
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NSK Ltd
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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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0005—Hubs with ball bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0047—Hubs characterised by functional integration of other elements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/02—Hubs adapted to be rotatably arranged on axle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B2900/00—Purpose of invention
    • B60B2900/10—Reduction of
    • B60B2900/111—Weight
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B2900/00—Purpose of invention
    • B60B2900/30—Increase in
    • B60B2900/311—Rigidity or stiffness
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B2900/00—Purpose of invention
    • B60B2900/70—Adaptation for
    • B60B2900/711—High loads, e.g. by reinforcements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/185—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with two raceways provided integrally on a part other than a race ring, e.g. a shaft or housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii
    • F16C2240/80—Pitch circle diameters [PCD]
    • 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

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

Abstract

<P>PROBLEM TO BE SOLVED: To attain a structure, that is an outer ring rotation type structure, for compatibly reducing weight and securing strength of an outer ring member rotating together with wheels at a high level. <P>SOLUTION: A flange support 8 is provided integrally with a hub 4a so as to be stretched over an axially inner end of the hub 4a, that is the outer ring member, and a radially outer end of the flange 7a supporting the wheel and a rotation member for braking. The flange support 8 is a conical sleeve shape and is slant in a direction to increase the inner and outer diameters as going outward in the axial direction. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

この発明は、自動車の車輪及びブレーキディスク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使用する車輪支持用転がり軸受ユニットの改良に関する。特に、本発明は、外輪回転型の車輪支持用転がり軸受ユニットに関し、車輪と共に回転する外輪部材の軽量化と強度確保とを高次元で両立させるものである。   The present invention relates to an improvement of a rolling bearing unit for supporting a wheel used for rotatably supporting a rotating member for braking such as a wheel and a brake disk of an automobile with respect to a suspension device. In particular, the present invention relates to a wheel bearing rolling bearing unit of an outer ring rotating type, which achieves both a reduction in weight and securing of strength of an outer ring member that rotates together with a wheel at a high level.

自動車の車輪を構成するホイール、及び、制動用回転部材であるディスク或いはドラムを、懸架装置を構成するナックルに回転自在に支持する為に、車輪支持用転がり軸受ユニットが広く使用されている。この様な車輪支持用転がり軸受ユニットとして一般的には、内輪回転型のものが広く使用されているが、例えば従動輪用として、特許文献１等に記載されている様な、外輪回転型のものも使用されている。図７は、この特許文献１に記載された構造を示している。この外輪回転型の車輪支持用転がり軸受ユニット１は、それぞれの外周面に内輪軌道２、２形成した１対の内輪３、３の周囲にハブ４を、複数個の転動体５、５を介して回転自在に支持している。使用状態では上記両内輪３、３を、懸架装置に設けた車軸に外嵌固定し、上記ハブ４に車輪及び制動用回転部材を支持固定する。上記両内輪３、３が合わさったものが特許請求の範囲に記載した内輪部材に相当し、上記ハブ４が同じく外輪部材に相当する。   2. Description of the Related Art A wheel bearing rolling bearing unit is widely used to rotatably support a wheel constituting a wheel of an automobile and a disk or drum which is a rotating member for braking on a knuckle constituting a suspension device. In general, an inner ring rotating type is widely used as such a wheel-supporting rolling bearing unit. For example, an outer ring rotating type as described in Patent Document 1 is used for a driven wheel. Things are also used. FIG. 7 shows the structure described in Patent Document 1. The outer ring rotating type wheel bearing rolling bearing unit 1 includes an inner ring raceway 2 and a pair of inner rings 3 and 3 formed on each outer peripheral surface, and a hub 4 around a plurality of rolling elements 5 and 5. And is supported rotatably. In use, both the inner rings 3 and 3 are externally fitted and fixed to an axle provided in the suspension device, and the wheel and the braking rotating member are supported and fixed to the hub 4. A combination of the inner rings 3 and 3 corresponds to the inner ring member recited in the claims, and the hub 4 also corresponds to the outer ring member.

上記ハブ４の内周面の２個所位置に複列の外輪軌道６、６を、外周面の軸方向外寄り部分（軸方向に関して外とは、使用状態で車体の幅方向外側となる側を言い、図１〜７の左側。反対に、使用状態で車体の幅方向中央側となる、図１〜７の右側を、軸方向に関して内と言う。本明細書及び特許請求の範囲全体で同じ。）に、上記車輪及び制動用回転部材を支持する為のフランジ７を、それぞれ形成している。そして、上記両列の内輪軌道２、２と上記両列の外輪軌道６、６との間に、両列毎に複数個ずつの上記転動体５、５を配置して、上記両内輪３、３の外径側での上記ハブ４の回転を自在としている。尚、図示の例では、転動体５、５として玉を示したが、重量の嵩む車両用の車輪支持用転がり軸受ユニットの場合には、転動体として円すいころを使用する場合もある。   Two rows of outer ring raceways 6 and 6 are disposed at two positions on the inner peripheral surface of the hub 4, and the axially outer peripheral portion of the outer peripheral surface (outside with respect to the axial direction is the side on the outer side in the width direction of the vehicle body in use. 1 to 7. On the other hand, the right side of FIGS.1 to 7 which is the center side in the width direction of the vehicle body in use is referred to as the inside in the axial direction. )), Flanges 7 for supporting the wheel and the brake rotating member are formed respectively. Then, a plurality of rolling elements 5, 5 are arranged for each row between the inner ring raceways 2, 2 in both rows and the outer ring raceways 6, 6 in both rows, The hub 4 can be freely rotated on the outer diameter side of 3. In the illustrated example, balls are shown as the rolling elements 5 and 5. However, in the case of a rolling bearing unit for supporting a wheel for a heavy vehicle, a tapered roller may be used as the rolling element.

ところで、上述の様な外輪回転型の車輪支持用転がり軸受ユニット１の場合には、車輪と共に回転する回転輪が、内輪部材（内輪３、３）よりも径が大きい外輪部材（ハブ４）となり、この径が大きくなる分、イナーシャ（慣性）が大きくなり易い。この為、この様な外輪回転型の車輪支持用転がり軸受ユニット１の場合、内輪回転型のものに比べると、そのままでは動力性能や燃費性能の面で不利になる可能性がある。この様なイナーシャ（慣性）に基づく不都合を防止する為には、回転輪である上記外輪部材（ハブ４）の軽量化を図る事が好ましい。   By the way, in the case of the rolling bearing unit 1 of the outer ring rotating type wheel support as described above, the rotating wheel rotating together with the wheel becomes the outer ring member (hub 4) having a larger diameter than the inner ring members (inner rings 3, 3). As the diameter increases, inertia (inertia) tends to increase. For this reason, in the case of such a wheel bearing rolling bearing unit 1 of the outer ring rotating type, there is a possibility that it is disadvantageous in terms of power performance and fuel consumption performance as compared with the inner ring rotating type. In order to prevent such inconvenience due to inertia (inertia), it is preferable to reduce the weight of the outer ring member (hub 4) which is a rotating wheel.

一方、操作性向上やブレーキジャダー防止の為に、転がり軸受の剛性を確保する事とフランジ（フランジ７）の振れを低減する事とが求められている。この様な転がり軸受の剛性確保やフランジ（フランジ７）の振れの低減を図る為には、上記回転輪である上記外輪部材（ハブ４）の強度を確保する事が好ましい。例えば、この様な強度を確保をすべく、上記外輪部材（ハブ４）の径方向に関する肉厚や、フランジ（フランジ７）の軸方向に関する肉厚を大きくする事が考えられる。但し、この様に単に肉厚を大きくするだけでは、強度確保に基づく操作性向上とブレーキジャダーの低減とを図れたとしても、上記イナーシャ（慣性）の増大が避けられず、このイナーシャ（慣性）の増大に伴う不都合（動力性能及び燃費性能の低下）を防止できない。   On the other hand, in order to improve operability and prevent brake judder, it is required to ensure the rigidity of the rolling bearing and to reduce the deflection of the flange (flange 7). In order to ensure the rigidity of such a rolling bearing and reduce the deflection of the flange (flange 7), it is preferable to ensure the strength of the outer ring member (hub 4) which is the rotating wheel. For example, in order to ensure such strength, it is conceivable to increase the thickness of the outer ring member (hub 4) in the radial direction and the thickness of the flange (flange 7) in the axial direction. However, even if the wall thickness is simply increased in this way, even if the operability is improved and the brake judder is reduced based on the strength, the increase in the inertia (inertia) cannot be avoided. Inconvenience (decrease in power performance and fuel consumption performance) due to the increase of the engine cannot be prevented.

特開２００８−１２８２５６号公報JP 2008-128256 A

本発明の車輪支持用転がり軸受ユニットは、上述の様な事情に鑑みて、外輪回転型の構造で、車輪と共に回転する外輪部材の軽量化と強度確保とを高次元で両立させられる構造を実現すべく発明したものである。   The wheel bearing rolling bearing unit of the present invention is an outer ring rotating structure in view of the above-described circumstances, and realizes a structure that can achieve both a reduction in weight and securing strength of an outer ring member that rotates with a wheel at a high level. Invented as much as possible.

本発明の車輪支持用転がり軸受ユニットは、内輪部材（例えば内輪）と、外輪部材（例えばハブ）と、複数個の転動体（例えば玉、円すいころ等）とを備える。
このうちの内輪部材は、外周面に複列の内輪軌道を有し、使用時に懸架装置に支持固定された状態で回転しない。
又、上記外輪部材は、軸方向外端寄り部分に車輪を支持する為のフランジを、内周面に複列の外輪軌道を、それぞれ有し、使用時に上記車輪と共に回転する。
又、上記各転動体は、上記各内輪軌道と上記各外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。 The wheel support rolling bearing unit of the present invention includes an inner ring member (for example, an inner ring), an outer ring member (for example, a hub), and a plurality of rolling elements (for example, balls, tapered rollers, etc.).
Of these, the inner ring member has a double-row inner ring raceway on the outer peripheral surface, and does not rotate while being supported and fixed to the suspension device during use.
The outer ring member has a flange for supporting the wheel near the outer end in the axial direction and a double row outer ring raceway on the inner peripheral surface, and rotates together with the wheel during use.
Further, a plurality of each rolling element is provided between each inner ring raceway and each outer ring raceway so as to be freely rollable.

特に、本発明の車輪支持用転がり軸受ユニットに於いては、上記外輪部材の軸方向内端部と上記フランジの径方向外端部とを掛け渡す状態でフランジ支持部を、上記外輪部材と一体に設ける。尚、この様なフランジ支持部を一体に設けた外輪部材は、例えば、この外輪部材となるべき素材に鍛造加工（塑性加工）等を施す事により、中心軸を含む仮想平面に関する断面形状を、例えば略Ｖ字状又は略Ｕ字状に形成する事により構成できる。そして、この様なフランジ支持部を一体に設けた外輪部材とは別体（で例えば円輪状）に形成された上記フランジを、この外輪部材の軸方向外端部と上記フランジ支持部の軸方向外端部とに結合固定する。言い換えれば、上記外輪部材のうちで内周面に上記複列の外輪軌道を形成した部分と、上記フランジ支持部と、上記フランジとにより、軸方向の断面がトラス構造の如き形状（略三角形状）となる様に構成している。   In particular, in the rolling bearing unit for wheel support of the present invention, the flange support portion is integrated with the outer ring member in a state where the inner end portion in the axial direction of the outer ring member and the outer end portion in the radial direction of the flange are spanned. Provided. In addition, the outer ring member integrally provided with such a flange support part, for example, by performing forging (plastic processing) or the like on the material to be the outer ring member, the cross-sectional shape relating to the virtual plane including the central axis, For example, it can comprise by forming in a substantially V shape or a substantially U shape. The flange formed separately from the outer ring member integrally provided with such a flange support portion (for example, an annular shape) is connected to the axial outer end portion of the outer ring member and the axial direction of the flange support portion. Connect and fix to the outer end. In other words, the portion of the outer ring member in which the double-row outer ring raceway is formed on the inner peripheral surface, the flange support portion, and the flange have an axial cross-section shaped like a truss structure (substantially triangular) ).

尚、これらフランジと外輪部材との結合固定は、例えばこれらフランジと外輪部材との径方向並びに軸方向の位置決めが図られた状態で、これらフランジと外輪部材とを溶接する事により行なう事ができる。より具体的には、例えば円輪状の上記フランジの軸方向内端部内周面と上記外輪部材の軸方向外端部外周面との嵌合に基づいて、これらフランジと外輪部材との径方向に関する位置決めを図る。尚、このフランジの軸方向内側面にこの内側面から軸方向外側に凹入する状態で嵌合支持部を設け、この嵌合支持部の内周面と、上記外輪部材の軸方向外端部外周面との嵌合に基づいて、径方向の位置決めを図る事もできる。   The flange and the outer ring member can be coupled and fixed, for example, by welding the flange and the outer ring member while the flange and the outer ring member are positioned in the radial direction and the axial direction. . More specifically, for example, based on the fitting between the inner circumferential surface of the annular inner end portion of the flange and the outer circumferential surface of the outer circumferential end portion of the outer ring member, the radial direction of the flange and the outer ring member is related. Position it. In addition, a fitting support portion is provided on the inner side surface in the axial direction of the flange so as to be recessed axially outward from the inner side surface, and the inner peripheral surface of the fitting support portion and the outer end portion in the axial direction of the outer ring member. Positioning in the radial direction can also be achieved based on the fitting with the outer peripheral surface.

又、上記フランジと上記外輪部材との軸方向に関する位置決めは、例えば、このフランジに設けられた、このフランジの中心軸と直交する方向に存在する側面（フランジの軸方向内側面又は嵌合支持部の側面）と、上記外輪部材の軸方向外端部に設けられた、この外輪部材の中心軸と直交する方向に存在する側面（外輪部材の外端面又は外輪部材の軸方向外端部外周面に設けた段差面）との当接に基づいても行える。そして、この様にフランジと外輪部材との位置決めが図られた状態で、これらフランジと外輪部材とを溶接する事により、これら外輪部材とフランジとの結合を行う。   The positioning of the flange and the outer ring member in the axial direction is performed by, for example, a side surface (an axial inner surface of the flange or a fitting support portion) provided in the flange and present in a direction perpendicular to the center axis of the flange. ) And the side surface (the outer end surface of the outer ring member or the outer peripheral surface of the outer ring member in the axial direction) that exists in the direction orthogonal to the central axis of the outer ring member, provided at the outer end of the outer ring member in the axial direction. It can also be performed based on contact with the step surface provided on the surface. Then, in a state where the flange and the outer ring member are positioned as described above, the flange and the outer ring member are welded to connect the outer ring member and the flange.

尚、上記溶接は、例えば円輪状に形成されたフランジの内周縁と、上記外輪部材の軸方向外端部外周面との間と、このフランジの外周縁とフランジ支持部の軸方向外端部外周縁との間との、一方又は双方に施す事ができる。この様に溶接により結合固定する場合には、上記フランジと上記外輪部材とを同種の金属により構成する事で、この溶接の容易化を図れる。但し、この溶接が多少面倒になっても、例えばチタン合金（チタニウム合金）等の軽量金属を用いる事で、更なる軽量化、イナーシャ（慣性）の低減を図る事もできる。又、上記フランジを構成する素材として、上記チタン合金或はステンレス鋼等の耐食性を有する金属材料を用いれば、車輪を構成するアルミニウム合金製のホイールや制動用回転部材であるロータとの当接部で、ガルバニックコロージョン（異種金属間腐食）が生じる事を防止できる。又、上記フランジは、車両に組み付けた状態で軸方向外側から目視できる可能性がある為、見栄えを良くする点で、上記チタン合金やステンレス鋼等を採用しても良い。   The welding is performed between, for example, the inner peripheral edge of the flange formed in an annular shape and the outer peripheral surface of the outer ring member in the axial direction, and the outer peripheral edge of the flange and the outer peripheral edge of the flange support portion. It can be applied to one side or both sides with the outer periphery. In this way, when the coupling and fixing are performed by welding, the welding can be facilitated by configuring the flange and the outer ring member with the same kind of metal. However, even if this welding is somewhat troublesome, the weight can be further reduced and the inertia (inertia) can be reduced by using a light metal such as a titanium alloy (titanium alloy). In addition, if a metal material having corrosion resistance such as the titanium alloy or stainless steel is used as a material constituting the flange, a contact portion with an aluminum alloy wheel constituting a wheel or a rotor which is a braking rotating member. Thus, the occurrence of galvanic corrosion (corrosion between different metals) can be prevented. In addition, since the flange may be visible from the outside in the axial direction in a state where it is assembled to a vehicle, the titanium alloy, stainless steel, or the like may be adopted from the viewpoint of improving the appearance.

又、上記フランジと上記外輪部材とを結合固定した状態で、このフランジの取付面（車輪及びブレーキディスク等の制動用回転部材を取り付ける側の面）の仕上げ加工を行えば、この取付面を、上記外輪部材の回転中心軸に直交する方向に、精度良く形成する事ができる。又、上記フランジには、上記車輪及び制動用回転部材を結合する為の、ボルト又はスタッドを取り付ける必要がある。この様なボルト又はスタッドは、上記フランジを上記外輪部材に結合固定してから取り付ける事もできるし、これとは逆に、予めフランジにボルト又はスタッドを取り付けた状態で、このフランジを上記外輪部材に結合固定する事もできる。   Further, when the flange and the outer ring member are coupled and fixed, if the finishing surface of the mounting surface of the flange (the surface on which the braking rotary member such as a wheel and a brake disk is mounted) is finished, the mounting surface is The outer ring member can be formed with high accuracy in a direction perpendicular to the rotation center axis of the outer ring member. Further, it is necessary to attach bolts or studs for connecting the wheel and the brake rotating member to the flange. Such a bolt or stud can be attached after the flange is joined and fixed to the outer ring member. Conversely, the bolt or stud is attached to the flange in advance and the flange is attached to the outer ring member. It can also be fixed to the joint.

尚、上記フランジと上記外輪部材とを結合固定してから、このフランジに上記ボルト又はスタッドを取り付ける場合には、後述する、フランジ支持部に設けた通孔を通じて、或は、フランジ支持部を構成する柱部同士の間から、上記ボルト又はスタッドを上記フランジに設けたねじ孔や通孔に螺合又は圧入する。この様に構成すれば、これらボルト又はスタッドを、予め上記外輪部材に結合固定した上記フランジに、軸方向内側から取り付ける事ができる。
又、上記車輪及び制動用回転部材の位置決めを行う為の円筒部（パイロット部）は、上記外輪部材に設ける事もできるし、上記フランジに設ける事もできる。何れにするかは、例えば必要な強度、性能、組み立て易さ等を考慮して、設計的に決める。 In addition, when attaching the bolt or the stud to the flange after the flange and the outer ring member are coupled and fixed, the flange support portion is configured through a through hole provided in the flange support portion, which will be described later. The bolts or studs are screwed or press-fitted into the screw holes or through-holes provided in the flange from between the column parts. If comprised in this way, these volt | bolts or studs can be attached to the said flange previously couple | bonded and fixed to the said outer ring member from the axial direction inner side.
Further, the cylindrical portion (pilot portion) for positioning the wheel and the braking rotating member can be provided on the outer ring member or on the flange. Which one is selected is determined by design in consideration of, for example, necessary strength, performance, and ease of assembly.

又、上述の様な本発明の車輪支持用転がり軸受ユニットを実施する場合に、例えば、上記フランジ支持部を、軸方向外側に向かう程、内径並びに外径が大きくなる方向に傾斜した円錐筒状のものとする。又、必要に応じて、この円錐筒状のフランジ支持部の内外両周面を貫通する状態で、このフランジ支持部に、このフランジ支持部（延いては外輪部材全体として）の軽量化を図る為の通孔を設ける事もできる。尚、この様なフランジ支持部の厚さや上記通孔の大きさ、位置、個数等は、必要な強度、剛性、加わる応力等に応じて設計的に定める。   Further, when the rolling bearing unit for supporting a wheel of the present invention as described above is implemented, for example, a conical cylindrical shape in which the flange support portion is inclined in a direction in which the inner diameter and the outer diameter increase toward the outer side in the axial direction. Shall be. If necessary, the flange support portion (and the entire outer ring member as a whole) can be reduced in weight while being penetrated through both the inner and outer peripheral surfaces of the conical cylindrical flange support portion. A through hole can be provided. The thickness of such a flange support part and the size, position, number, etc. of the through holes are determined by design according to the required strength, rigidity, applied stress, and the like.

又、例えば、上記フランジ支持部を、複数本の柱部により構成する事もできる。即ち、これら各柱部を、上記フランジの周方向に関して等間隔に配置した状態で、それぞれこのフランジの径方向外端部と上記外輪部材の軸方向内端部との間に掛け渡す事により、上記フランジ支持部を構成する事もできる。尚、これら各柱部は、必要な強度を確保すべく、例えばこれら各柱部に加わる応力に応じて、厚さ（太さ）を軸方向に亙り変化させる事ができる。又、この様に各柱部によりフランジ支持部を構成する場合には、上記フランジの径方向外周縁で、これら各柱部と整合する位置に、これら各柱部の外端部と凹凸係合する切り欠きを設ける事が好ましい。勿論、上記フランジ支持部を円錐筒状に形成した場合でも、このフランジ支持部の軸方向外端部に円周方向に間欠的に凸部を設け、この凸部と、上記フランジに設けた各切り欠きとを凹凸係合させる事もできる。   Further, for example, the flange support portion can be constituted by a plurality of column portions. That is, by placing each of these column parts at an equal interval with respect to the circumferential direction of the flange, respectively, between the radial outer end of the flange and the axial inner end of the outer ring member, The said flange support part can also be comprised. In addition, in order to ensure the required strength, the thickness (thickness) of each of these column portions can be changed in the axial direction according to, for example, the stress applied to each of these column portions. Further, when the flange support portion is constituted by each column portion in this way, the outer end portion of each column portion is engaged with the concave and convex portions at the position aligned with each column portion at the radially outer peripheral edge of the flange. It is preferable to provide a notch. Of course, even when the flange support portion is formed in a conical cylinder shape, a convex portion is provided intermittently in the circumferential direction at the axially outer end portion of the flange support portion, and each of the convex portion and each flange provided on the flange is provided. It is also possible to engage the notch with an uneven surface.

尚、上記通孔或は上記各柱部同士の間部分は、上述した様に、上記フランジに上記ボルト又はスタッドを取り付ける際の、これらボルト又はスタッドを挿通する（通過させる）為の孔として用いる事ができる。この場合には、上記フランジを上記外輪部材に結合固定した状態で、上記通孔或は上記各柱部同士の間部分が、上記フランジに設けた、上記ボルトを螺合する為のねじ孔、又は、上記スタッドを圧入する為の支持孔と、軸方向に重畳する様にする。
又、必要に応じて、上記フランジ支持部の軸方向外端部に、上記フランジと平行に、このフランジの径方向外端部と軸方向に重畳する支持板部を設ける事もできる。更に、この場合には、これらフランジ支持部の支持板部と上記フランジの軸方向内側面とを全周に亙り当接させる事もできる。 As described above, the through hole or the portion between the pillars is used as a hole for inserting (passing) the bolt or stud when the bolt or stud is attached to the flange. I can do things. In this case, in a state where the flange is coupled and fixed to the outer ring member, the through hole or a portion between the pillar portions is provided in the flange, and a screw hole for screwing the bolt, Alternatively, the stud is overlapped with the support hole for press-fitting the stud in the axial direction.
In addition, if necessary, a support plate portion that overlaps the radial outer end portion of the flange in the axial direction can be provided in parallel with the flange at the axial outer end portion of the flange support portion. Furthermore, in this case, the support plate portion of the flange support portion and the axially inner side surface of the flange can be brought into contact over the entire circumference.

上述の様に構成する本発明の車輪支持用転がり軸受ユニットによれば、車輪と共に回転する外輪部材の軽量化と強度確保とを高次元で両立させられる。
即ち、この外輪部材の軸方向内端部とフランジの径方向外端部との間に掛け渡されたフランジ支持部が、これら外輪部材とフランジとの間で突っ張ったり、或は、引っ張り方向の力を支承する。この為、これら外輪部材の剛性及びフランジの支持剛性を確保して、転がり軸受の剛性の確保に基づく操作性向上と、このフランジの軸方向の振れの低減に基づくブレーキジャダーの低減とを図れる。しかも、この様な外輪部材の剛性及びフランジの支持剛性の確保は、これら外輪部材とフランジとの間に設けた上記フランジ支持部により確保できる為、これら外輪部材及びこの外輪部材とは別体に形成された上記フランジの軽量化（例えば肉厚の低減）も図れる。この様な外輪部材及びフランジの軽量化の程度は、上記フランジ支持部を設ける事による重量増大分を大きく超える為、上記フランジを結合固定した外輪部材全体として軽量に構成でき、イナーシャ（慣性）の低減に基づく動力性能及び燃費性能の向上を図れる。 According to the rolling bearing unit for supporting a wheel of the present invention configured as described above, it is possible to achieve both a reduction in weight and securing of strength of the outer ring member rotating together with the wheel at a high level.
That is, the flange support portion spanned between the inner end portion in the axial direction of the outer ring member and the outer end portion in the radial direction of the flange is stretched between the outer ring member and the flange, or in the pulling direction. Support the power. Therefore, it is possible to secure the rigidity of the outer ring member and the support rigidity of the flange, improve the operability based on securing the rigidity of the rolling bearing, and reduce the brake judder based on the reduction of the axial deflection of the flange. In addition, since the rigidity of the outer ring member and the flange support rigidity can be ensured by the flange support portion provided between the outer ring member and the flange, the outer ring member and the outer ring member are separated from each other. The formed flange can be reduced in weight (for example, reduced in thickness). Since the degree of weight reduction of the outer ring member and the flange greatly exceeds the weight increase due to the provision of the flange support portion, the entire outer ring member to which the flange is coupled and fixed can be reduced in weight, and inertia (inertia) can be configured. It is possible to improve power performance and fuel consumption performance based on the reduction.

尚、本発明の場合には、上記フランジ支持部と外輪部材とを一体に形成している為、例えばこれらフランジ支持部と外輪部材とを別体に形成した場合に比べ、これらフランジ支持部と外輪部材との結合強度を確保し易くできる。又、これらフランジ支持部及び外輪部材と上記フランジとの結合強度に関しても、これらフランジとフランジ支持部及び外輪部材とを嵌合や凹凸係合によりがたつきなく支持でき、しかも、上記フランジを上記フランジ支持部及び外輪部材に押さえ付けつつ溶接する事ができる為、同じく結合強度を確保し易くできる。この為、その分（結合強度を確保し易くできる分）、これらフランジ支持部及び外輪部材、フランジの更なる軽量化を図れ、このフランジを結合固定した状態での外輪部材全体としての軽量化並びに強度確保を、高次元で両立させられる。更に、上記フランジ支持部を一体に形成した上記外輪部材は、鍛造加工（塑性加工）により容易に造る事ができる為、この様なフランジ支持部を一体に形成した外輪部材の製造コストが増大する事も防止できる。   In the case of the present invention, since the flange support portion and the outer ring member are integrally formed, for example, compared to a case where the flange support portion and the outer ring member are formed separately, these flange support portion and It is easy to ensure the bonding strength with the outer ring member. Further, regarding the coupling strength between the flange support portion and the outer ring member and the flange, the flange, the flange support portion and the outer ring member can be supported without looseness by fitting or uneven engagement, and the flange is Since welding can be performed while pressing against the flange support portion and the outer ring member, it is also easy to ensure the coupling strength. For this reason, it is possible to further reduce the weight of the flange support portion, the outer ring member, and the flange by that amount (to facilitate securing the coupling strength), and to reduce the weight of the outer ring member as a whole in a state where the flange is coupled and fixed. Ensuring strength can be achieved at a high level. Furthermore, since the outer ring member formed integrally with the flange support portion can be easily manufactured by forging (plastic processing), the manufacturing cost of the outer ring member formed integrally with the flange support portion increases. Things can also be prevented.

又、例えば、上記フランジ支持部を円錐筒状のものとすると共に、この円錐筒状のフランジ支持部に通孔を設ければ、更なる軽量化を図れる。又、上記フランジ支持部を複数本の柱部により構成した場合にも、同じく更なる軽量化を図れる。又、上記通孔やこれら柱部同士の間を通じて、上記フランジにボルト又はスタッドを取り付ける事もできる。更に、上記フランジ支持部の軸方向外端部に設けた支持板部と上記フランジの軸方向内側面とを当接させれば、これらフランジ支持部とフランジとの結合強度を確保し易くできる。何れの場合にも、上記フランジ支持部を、必要な強度、剛性、加わる応力等に応じて、最適な形状並びに寸法に規制する事で、車輪と共に回転する外輪部材の軽量化と強度確保とを高次元で両立させられる。   Further, for example, if the flange support portion is formed in a conical cylinder shape and a through hole is provided in the conical tube flange support portion, further weight reduction can be achieved. Further, when the flange support portion is constituted by a plurality of pillar portions, the weight can be further reduced. Moreover, a bolt or a stud can be attached to the flange through the through hole or between the pillar portions. Furthermore, if the support plate part provided in the axial direction outer end part of the said flange support part and the axial direction inner surface of the said flange are contacted, it can be easy to ensure the coupling strength of these flange support parts and a flange. In any case, the outer ring member that rotates with the wheel can be reduced in weight and ensure strength by restricting the flange support portion to the optimum shape and size according to the required strength, rigidity, applied stress, etc. It is compatible at a high level.

［実施の形態の第１例］
図１は、本発明の実施の形態の第１例を示している。尚、本例の特徴は、外輪回転型の車輪支持用転がり軸受ユニット１ａで、車輪と共に回転する、特許請求の範囲に記載した外輪部材に相当するハブ４ａの軽量化と強度確保とを高次元で両立させるべく、このハブ４ａの構造を工夫した点にある。その他の部分の構造及び作用は、前述の図７に示した従来構造の場合と同様である為、同等部分には同一符号を付して、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。 [First example of embodiment]
FIG. 1 shows a first example of an embodiment of the present invention. The feature of this example is that the outer ring rotating type rolling bearing unit 1a for wheel support rotates together with the wheel, and the hub 4a corresponding to the outer ring member described in the claims is reduced in weight and secured in high dimensions. In order to achieve both, the structure of the hub 4a is devised. Since the structure and operation of the other parts are the same as those of the conventional structure shown in FIG. 7, the same reference numerals are given to the equivalent parts, and overlapping illustrations and explanations are omitted or simplified. The description will focus on the features of this example.

本例の場合には、上記ハブ４ａの軸方向内端部と、車輪及び制動用回転部材を支持する為のフランジ７ａの径方向外端部とに掛け渡す状態でフランジ支持部８を、このハブ４ａと一体に設けている。このフランジ支持部８は、軸方向外側に向かう程、内径並びに外径が大きくなる方向に傾斜した円錐筒状のものとしている。尚、図示は省略するが、必要に応じて、このフランジ支持部８の内外両周面を貫通する状態で、このフランジ支持部８に、このフランジ支持部８、延いては、ハブ４ａ全体としての軽量化を図る為の通孔を（例えば円周方向に間欠的に複数）設ける事ができる。   In the case of this example, the flange support portion 8 is connected to the inner end portion in the axial direction of the hub 4a and the outer end portion in the radial direction of the flange 7a for supporting the wheel and the braking rotary member. It is provided integrally with the hub 4a. The flange support portion 8 has a conical cylindrical shape that is inclined in a direction in which the inner diameter and the outer diameter increase toward the outer side in the axial direction. In addition, although illustration is abbreviate | omitted, as needed, this flange support part 8 and the hub 4a whole are made into this flange support part 8 in the state which penetrates both the inner and outer peripheral surfaces of this flange support part 8. Can be provided (for example, a plurality of intermittently in the circumferential direction).

この様なハブ４ａは、このハブ４ａとなるべき素材に鍛造加工（塑性加工）等を施す事により、軸方向の断面が略Ｖ字状となる様に形成する事により、上記フランジ支持部８と一体に構成している。そして、この様なフランジ支持部８を一体に設けたハブ４ａとは別体の上記フランジ７ａを、このハブ４ａの軸方向外端部と上記フランジ支持部８の軸方向外端部との間に結合固定している。本例の場合、上記フランジ７ａは、円輪状のフランジ部９の内周縁部に、このフランジ部９から軸方向外側に突出する状態で円筒状のパイロット部１０を設けて成る。尚、このパイロット部１０は、上記車輪及び制動用回転部材を外嵌して、これら車輪及び制動用回転部材の径方向に関する位置決め図る為のものである。   Such a hub 4a is formed by subjecting the material to be the hub 4a to forging (plastic processing) or the like so that the axial cross-section is substantially V-shaped. It is composed integrally with. The flange 7a, which is separate from the hub 4a integrally provided with such a flange support portion 8, is disposed between the outer end portion in the axial direction of the hub 4a and the outer end portion in the axial direction of the flange support portion 8. It is fixed to the joint. In the case of this example, the flange 7a is formed by providing a cylindrical pilot portion 10 on the inner peripheral edge portion of the annular flange portion 9 so as to protrude outward from the flange portion 9 in the axial direction. The pilot unit 10 is for externally fitting the wheel and the braking rotary member to position the wheel and the braking rotary member in the radial direction.

又、この様なフランジ７ａと上記ハブ４ａとの結合固定は、これらフランジ７ａとハブ４ａとの径方向並びに軸方向の位置決めを図った状態で、これらフランジ７ａとハブ４ａとを溶接する事により行う。本例の場合には、上記フランジ７ａの軸方向内側面にこの内側面から軸方向外側に凹入する状態で嵌合支持部１１を設け、この嵌合支持部１１の内周面に、上記ハブ４ａの軸方向外端部を嵌合する事により、これらフランジ７ａとハブ４ａとの径方向並びに軸方向の位置決めを図っている。そして、この様に位置決めを図った状態で、上記フランジ支持部８の軸方向外端部外周縁と上記フランジ７ａの外周縁との間、及び、このフランジ７ａの内周縁と上記ハブ４ａの外端部内周縁との間に溶接１９、１９を、それぞれ全周に亙り施す事により、これらフランジ７ａとハブ４ａとを結合固定している。   In addition, the flange 7a and the hub 4a are connected and fixed by welding the flange 7a and the hub 4a in a state where the flange 7a and the hub 4a are positioned in the radial direction and the axial direction. Do. In the case of this example, the fitting support portion 11 is provided on the inner side surface in the axial direction of the flange 7a so as to be recessed from the inner side surface in the axial direction, and the inner peripheral surface of the fitting support portion 11 By fitting the outer end of the hub 4a in the axial direction, the flange 7a and the hub 4a are positioned in the radial direction and the axial direction. In this state of positioning, between the outer peripheral edge of the flange support portion 8 in the axial direction and the outer peripheral edge of the flange 7a, and between the inner peripheral edge of the flange 7a and the hub 4a. These flanges 7a and the hub 4a are coupled and fixed by applying welds 19 and 19 to the entire inner periphery of the end portion.

又、この様にフランジ７ａとハブ４ａとを結合固定した状態で、このフランジ７ａの軸方向外側面である、上記車輪及びブレーキディスク等の制動用回転部材を取り付ける為の取付面１４の仕上げ加工を行う。この様にフランジ７ａを結合固定した状態で取付面１４の仕上げ加工を行えば、この取付面１４を、上記ハブ４ａの回転中心軸に直交する方向に、精度良く形成する事ができる。又、上記フランジ７ａには、このフランジ７ａから軸方向外側に突出する状態で、上記車輪及び制動用回転部材を結合する為のスタッド１２を取り付けている。この様なスタッド１２は、上記フランジ７ａとハブ４ａとを結合固定する前に、このフランジ７ａに設けた支持孔１３に圧入固定しておく。   Further, in the state where the flange 7a and the hub 4a are coupled and fixed in this manner, the finishing process of the mounting surface 14 for mounting the braking rotary member such as the wheel and the brake disk, which is the outer surface in the axial direction of the flange 7a. I do. If the mounting surface 14 is finished with the flange 7a coupled and fixed in this manner, the mounting surface 14 can be accurately formed in a direction perpendicular to the rotation center axis of the hub 4a. The flange 7a is provided with a stud 12 for connecting the wheel and the brake rotating member so as to protrude outward in the axial direction from the flange 7a. Such a stud 12 is press-fitted and fixed in a support hole 13 provided in the flange 7a before the flange 7a and the hub 4a are coupled and fixed.

そして、この様にスタッド１２を圧入固定したフランジ７ａを、上述の様にハブ４ａに結合固定し、このフランジ７ａの取付面１４に仕上げ加工を施す。尚、この仕上げ加工は、上記フランジ７ａに上記スタッド１２を取り付けた状態で行う為、例えば上記取付面１４のうちで上記支持孔１３の開口周縁部を挟む部分に全周に亙り、この取付面１４から軸方向内側に凹入する状態で、環状の凹部を設ける事が好ましい。この様に取付面１４のうちで支持孔１３の周囲（開口周縁部）に凹部を設ければ、上記仕上げ加工を行う為の工具と上記スタッド１２との干渉を防止しつつ、この取付面１４の必要箇所に仕上げ加工を施す事ができる。   Then, the flange 7a in which the stud 12 is press-fitted and fixed in this manner is coupled and fixed to the hub 4a as described above, and the mounting surface 14 of the flange 7a is finished. In addition, since this finishing process is performed with the stud 12 attached to the flange 7a, for example, the mounting surface 14 extends over the entire periphery of a portion of the mounting surface 14 that sandwiches the peripheral edge of the opening of the support hole 13. It is preferable to provide an annular recess in a state of being recessed inward in the axial direction from 14. Thus, if a recessed part is provided in the circumference (opening peripheral part) of support hole 13 among attachment surfaces 14, this attachment surface 14 is prevented, preventing interference with the tool for performing the above-mentioned finishing, and the above-mentioned stud 12. Finishing can be applied to the necessary parts.

上述の様に構成する本例の場合には、車輪と共に回転するハブ４ａの軽量化と強度確保とを高次元で両立させられる。
即ち、このハブ４ａの軸方向内端部とフランジ７ａの径方向外端部との間に掛け渡されたフランジ支持部８が、これらハブ４ａとフランジ７ａとの間で突っ張ったり、引っ張り方向の力を支承する。この為、これらハブ４ａの剛性及びフランジ７ａの支持剛性を確保して、転がり軸受の剛性の確保に基づく操作性向上と、このフランジ７ａの軸方向の振れの低減に基づくブレーキジャダーの低減とを図れる。しかも、この様なハブ４ａの剛性及びフランジ７ａの支持剛性の確保は、これらハブ４ａとフランジ７ａとの間に設けた上記フランジ支持部８により確保できる為、これらハブ４ａ及びこのハブ４ａとは別体に形成された上記フランジ７ａの軽量化（例えば肉厚の低減）も図れる。この様なハブ４ａ及びフランジ７ａの軽量化の程度は、上記フランジ支持部８を設ける事による重量増大分を大きく超える為、上記フランジ７ａを結合固定したハブ４ａ全体として軽量に構成でき、イナーシャ（慣性）の低減に基づく動力性能及び燃費性能の向上を図れる。 In the case of this example configured as described above, it is possible to achieve both weight reduction and securing of strength of the hub 4a rotating together with the wheels at a high level.
In other words, the flange support portion 8 spanned between the axial inner end portion of the hub 4a and the radial outer end portion of the flange 7a may be stretched between the hub 4a and the flange 7a or in the pulling direction. Support the power. For this reason, the rigidity of the hub 4a and the support rigidity of the flange 7a are secured, and the operability is improved based on securing the rigidity of the rolling bearing, and the brake judder is reduced based on the reduction of the axial deflection of the flange 7a. I can plan. In addition, since the rigidity of the hub 4a and the support rigidity of the flange 7a can be ensured by the flange support portion 8 provided between the hub 4a and the flange 7a, the hub 4a and the hub 4a are It is also possible to reduce the weight of the flange 7a formed separately (for example, to reduce the thickness). Since the degree of weight reduction of the hub 4a and the flange 7a greatly exceeds the weight increase due to the provision of the flange support portion 8, the entire hub 4a to which the flange 7a is coupled and fixed can be configured to be lightweight. It is possible to improve the power performance and the fuel efficiency based on the reduction of inertia.

又、本例の場合には、上記フランジ支持部８とハブ４ａとを一体に形成している為、例えばこれらフランジ支持部８とハブ４ａとを別体に形成した場合に比べ、これらフランジ支持部８とハブ４ａとの剛性（結合強度）を確保し易くできる。又、これらフランジ支持部８及びハブ４ａと上記フランジ７ａとの結合強度に関しても、これらフランジ７ａとハブ４ａとを嵌合によりがたつきなく支持でき、しかも、このフランジ７ａをハブ４ａに押さえ付けつつ溶接する事ができる為、同じく結合強度を確保し易くできる。この為、その分（結合強度を確保し易くできる分）、これらフランジ支持部８及びハブ４ａ、フランジ７ａの更なる軽量化を図れ、このフランジ７ａを結合固定したハブ４ａ全体としての軽量化並びに強度確保を高次元で両立させられる。更に、上記フランジ支持部８を一体に形成した上記ハブ４ａは、鍛造加工（塑性加工）により容易に造る事ができる為、この様なフランジ支持部８を一体に形成したハブ４ａの製造コストが増大する事も防止できる。   In the case of this example, since the flange support portion 8 and the hub 4a are integrally formed, for example, the flange support portion 8 and the hub 4a are supported in a flange as compared with the case where the flange support portion 8 and the hub 4a are formed separately. The rigidity (coupling strength) between the portion 8 and the hub 4a can be easily ensured. Further, regarding the coupling strength between the flange support portion 8 and the hub 4a and the flange 7a, the flange 7a and the hub 4a can be supported without looseness by fitting, and the flange 7a is pressed against the hub 4a. Since it can be welded, it is easy to ensure the bonding strength. For this reason, it is possible to further reduce the weight of the flange support portion 8, the hub 4a, and the flange 7a by that amount (to facilitate the securing of the coupling strength), and to reduce the weight of the hub 4a as a whole to which the flange 7a is coupled and fixed. Ensuring strength can be achieved at a high level. Furthermore, since the hub 4a formed integrally with the flange support portion 8 can be easily manufactured by forging (plastic working), the manufacturing cost of the hub 4a formed integrally with the flange support portion 8 is reduced. It can also be prevented from increasing.

［実施の形態の第２例］
図２〜３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、フランジ支持部８ａを、複数本の柱部１５により構成している。即ち、これら各柱部１５を、フランジ７ｂ並びにハブ４ｂの周方向に関して等間隔に配置した状態で、それぞれこれらフランジ７ｂの径方向外端部とハブ４ｂの軸方向内端部との間に掛け渡す事により、上記フランジ支持部８ａを構成している。本例の場合には、上記フランジ７ｂの径方向外周縁で、上記各柱部１５と整合する位置に、これら各柱部１５の端部と凹凸係合する切り欠き１６を設けている。そして、これら各柱部１５の軸方向外端部と上記各切り欠き１６の内面との間、及び、上記フランジ７ｂの内周縁と上記ハブ４ｂの外周面との間に、それぞれ溶接１９、１９を施す事により、上記フランジ７ｂと上記ハブ４ｂとを結合固定している。尚、上記各柱部１５は、必要な強度を確保すべく、例えばこれら各柱部１５に加わる応力に応じて、厚さ（太さ）を軸方向に亙り変化させる事もできる。 [Second Example of Embodiment]
2 to 3 show a second example of the embodiment of the present invention. In the case of this example, the flange support portion 8 a is configured by a plurality of column portions 15. In other words, in a state where these pillar portions 15 are arranged at equal intervals in the circumferential direction of the flange 7b and the hub 4b, they are respectively hung between the radially outer end portion of the flange 7b and the axially inner end portion of the hub 4b. By passing, the flange support portion 8a is configured. In the case of this example, a notch 16 that engages with the end portions of each column portion 15 is provided at a position that aligns with each column portion 15 at the radially outer peripheral edge of the flange 7b. The welds 19 and 19 are provided between the outer ends of the pillars 15 in the axial direction and the inner surfaces of the notches 16 and between the inner peripheral edge of the flange 7b and the outer peripheral surface of the hub 4b, respectively. By doing so, the flange 7b and the hub 4b are coupled and fixed. In addition, in order to ensure the required strength, the thickness (thickness) of each of the column portions 15 can be changed in the axial direction according to, for example, the stress applied to each of the column portions 15.

この様な各柱部１５によりフランジ支持部８ａを構成した本例の場合には、上記フランジ７ｂと上記ハブ４ｂとを結合固定した状態で、このフランジ７ｂに、車輪及び制動用回転部材を結合する為のスタッド１２を取り付ける事ができる。即ち、本例の構造を組み立てる場合には、これら各スタッド１２を上記フランジ７ｂの支持孔１３内に圧入固定する以前の、このスタッド１２を取り付けていないフランジ７ｂを、上記ハブ４ｂに結合固定する。そして、この様にフランジ７ｂをハブ４ｂに結合固定した状態で、上記各柱部１５同士の間部分を通じて上記スタッド１２を、上記支持孔１３に圧入固定する。この様に本例の場合には、上記各スタッド１２を、上記ハブ４ｂに結合固定したフランジ７ｂの軸方向内側から取り付けられる。尚、前述した実施の形態の第１例の場合にも、例えばフランジ支持部８（図１参照）に通孔を設ける事で、本例の場合と同様に、この通孔を通じてスタッド１２を取り付ける事もできる。   In the case of this example in which the flange support portion 8a is constituted by such each column portion 15, the wheel and the brake rotating member are coupled to the flange 7b in a state where the flange 7b and the hub 4b are coupled and fixed. Stud 12 can be attached. That is, when assembling the structure of this example, the flange 7b to which these studs 12 are not attached before the respective studs 12 are press-fitted and fixed into the support holes 13 of the flange 7b is coupled and fixed to the hub 4b. . Then, with the flange 7b coupled and fixed to the hub 4b in this way, the stud 12 is press-fitted and fixed to the support hole 13 through the portion between the column portions 15. Thus, in the case of this example, each stud 12 is attached from the inner side in the axial direction of the flange 7b fixedly coupled to the hub 4b. Also in the case of the first example of the above-described embodiment, for example, by providing a through hole in the flange support portion 8 (see FIG. 1), the stud 12 is attached through this through hole, as in this example. You can also do things.

又、本例の場合には、上記フランジ７ｂを円輪状のものとし、この様な円輪状のフランジ７ｂを、上記ハブ４ｂの軸方向外端寄り部分で、軸方向外側の外輪軌道６よりも軸方向外方に突出した部分に外嵌している。そして、このハブ４ｂの軸方向外端部で、上記フランジ７ｂよりも軸方向外側に突出した部分を、車輪及び制動用回転部材の径方向に関する位置決め図る為のパイロット部１０ａとしている。
その他の構成及び作用は、前述した実施の形態の第１例と同様であるから、重複する説明は省略する。 In the case of this example, the flange 7b is in the shape of a ring, and such a ring-shaped flange 7b is located closer to the outer end in the axial direction of the hub 4b than the outer ring raceway 6 on the outer side in the axial direction. It is externally fitted to a portion protruding outward in the axial direction. The portion of the hub 4b that protrudes outward in the axial direction from the flange 7b is used as a pilot portion 10a for positioning in the radial direction of the wheel and the braking rotary member.
Other configurations and operations are the same as those in the first example of the above-described embodiment, and thus redundant description is omitted.

［実施の形態の第３例］
図４は、本発明の実施の形態の第３例を示している。本例の場合には、車輪支持用転がり軸受ユニット１ｂを構成する複列の転がり軸受のうちの、軸方向に関して内側の列の転動体５のピッチ円直径を、同じく外側の列の転動体５ピッチ円直径よりも大きくしている。そして、この様な構成を採用する事により、車輪支持用転がり軸受ユニット１ｂのモーメント剛性の向上を図っている。又、本例の場合には、ハブ４ｃの軸方向外端部外周面と、フランジ支持部８の軸方向外端部内周面とに、フランジ７ａの内外両周縁部を嵌合支持する為の段部１７ａ、１７ｂを全周に亙って設けている。そして、これら両段部１７ａ、１７ｂに、上記フランジ７ａの内外両周縁部をがたつきなく嵌合支持した状態で、上記ハブ４ｃの軸方向外端部外端面、並びに、上記フランジ支持部８の軸方向外端部外端面と、上記フランジ７ａの内周面並びに外周縁部との間に、溶接１９、１９を施している。本例の場合には、これら両部に溶接１９、１９を施す作業を、上記フランジ７ａを上記両段部１７ａ、１７ｂに押し付けた状態で行える為、この溶接１９、１９に基づく結合強度を確保し易くできる。 [Third example of embodiment]
FIG. 4 shows a third example of the embodiment of the present invention. In the case of this example, of the double row rolling bearings constituting the wheel supporting rolling bearing unit 1b, the pitch circle diameter of the rolling elements 5 in the inner row with respect to the axial direction is the same as the rolling elements 5 in the outer row. It is larger than the pitch circle diameter. By adopting such a configuration, the moment rigidity of the wheel bearing rolling bearing unit 1b is improved. In the case of this example, the outer peripheral edge of the flange 7a is fitted and supported on the outer peripheral surface of the hub 4c in the axial outer end and the inner peripheral surface of the flange outer support 8 in the axial direction. Steps 17a and 17b are provided over the entire circumference. Then, in the state in which both the inner and outer peripheral edges of the flange 7a are fitted and supported on these stepped portions 17a and 17b without rattling, the outer end surface of the hub 4c in the axial direction and the flange support portion 8 The welds 19 and 19 are applied between the outer end surface in the axial direction and the inner peripheral surface and the outer peripheral edge of the flange 7a. In the case of this example, since the work of applying welds 19 and 19 to these both parts can be performed with the flange 7a pressed against the both stepped parts 17a and 17b, the bonding strength based on the welds 19 and 19 is ensured. Easy to do.

尚、本例の場合は、前述した実施の形態の第１例と同様に、上記フランジ７ａの内周縁部に、車輪及び制動用回転部材の径方向に関する位置決め図る為の円筒状のパイロット部１０ａを設けている。
その他の構成及び作用は、前述した実施の形態の第１例と同様であるから、重複する説明は省略する。 In the case of this example, similarly to the first example of the above-described embodiment, the cylindrical pilot portion 10a for positioning the wheel and the braking rotary member in the radial direction is arranged on the inner peripheral edge of the flange 7a. Is provided.
Other configurations and operations are the same as those in the first example of the above-described embodiment, and thus redundant description is omitted.

［実施の形態の第４例］
図５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、フランジ支持部８ｂの軸方向外端部に、フランジ７ａと平行に、このフランジ７ａの径方向外端部と軸方向に重畳する支持板部１８を設けている。そして、これらフランジ支持部８ｂの支持板部１８と上記フランジ７ａの軸方向内側面の外径側部とを、全周に亙り当接させている。又、本例の場合は、ハブ４ｃの軸方向外端面、並びに、上記フランジ支持部８ｂの支持板部１８の外周縁部と、上記フランジ７ａの内周面並びに外周縁部との間に、溶接１９、１９を施している。但し、このうちの支持板部１８の外周縁部とフランジ７ａの外周縁部との溶接を省略して、これら支持板部１８とフランジ７ａの径方向外端部とをボルトにより結合する事もできる。この様なボルトによる結合を採用するか溶接による結合を採用するかは、必要な強度、加工のし易さ、加工コスト等を考慮して最適なものを選ぶ。
その他の構成及び作用は、上述した実施の形態の第３例と同様であるから、重複する説明は省略する。 [Fourth Example of Embodiment]
FIG. 5 shows a fourth example of the embodiment of the present invention. In the case of this example, a support plate portion 18 is provided on the outer end portion in the axial direction of the flange support portion 8b in parallel with the flange 7a so as to overlap the outer end portion in the radial direction of the flange 7a in the axial direction. And the support plate part 18 of these flange support parts 8b and the outer-diameter side part of the axial direction inner side surface of the said flange 7a are contacted over the perimeter. In the case of this example, the axially outer end surface of the hub 4c, the outer peripheral edge portion of the support plate portion 18 of the flange support portion 8b, and the inner peripheral surface and outer peripheral edge portion of the flange 7a, Welds 19 and 19 are applied. However, welding of the outer peripheral edge portion of the support plate portion 18 and the outer peripheral edge portion of the flange 7a may be omitted, and the support plate portion 18 and the radially outer end portion of the flange 7a may be coupled by a bolt. it can. Whether such bolt connection or welding connection is adopted is selected in consideration of necessary strength, ease of processing, processing cost, and the like.
Other configurations and operations are the same as those of the third example of the above-described embodiment, and thus redundant description is omitted.

［実施の形態の第５例］
図６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、フランジ支持部８ｂの支持板部１８と、フランジ７ａの径方向外端部とを、スタッド１２により結合固定している。即ち、上記支持板部１８とフランジ７ａの径方向外端部とに互いに整合する状態でそれぞれ設けた支持孔１３ａ、１３ｂに、上記スタッド１２を圧入固定する事により、これら支持板部１８とフランジ７ａとを結合固定している。
その他の構成及び作用は、上述した実施の形態の第４例と同様であるから、重複する説明は省略する。 [Fifth Example of Embodiment]
FIG. 6 shows a fifth example of the embodiment of the present invention. In the case of this example, the support plate portion 18 of the flange support portion 8 b and the radially outer end portion of the flange 7 a are coupled and fixed by the stud 12. That is, the stud 12 is press-fitted and fixed in the support holes 13a and 13b provided in alignment with the support plate portion 18 and the radially outer end portion of the flange 7a, whereby the support plate portion 18 and the flange 7a. 7a is connected and fixed.
Other configurations and operations are the same as those of the fourth example of the above-described embodiment, and thus redundant description is omitted.

本発明の実施の形態の第１例を示す半部断面図。FIG. 2 is a half sectional view showing a first example of an embodiment of the present invention. 同第２例を示す半部断面図。Sectional sectional drawing which shows the 2nd example. フランジ支持部を径方向外側から見た図。The figure which looked at the flange support part from the radial direction outer side. 本発明の実施の形態の第３例を示す半部断面図。The half part sectional view showing the 3rd example of an embodiment of the invention. 同第４例を示す半部断面図。Sectional sectional drawing which shows the 4th example. 同第５例を示す図５のＡ部に相当する図。The figure equivalent to the A section of FIG. 5 which shows the 5th example. 従来構造の１例を示す断面図。Sectional drawing which shows an example of a conventional structure.

１、１ａ、１ｂ 車両支持用転がり軸受ユニット
２ 内輪軌道
３ 内輪
４、４ａ、４ｂ、４ｃ ハブ
５ 転動体
６ 外輪軌道
７、７ａ、７ｂ フランジ
８、８ａ、８ｂ フランジ支持部
９ フランジ部
１０、１０ａ パイロット部
１１ 嵌合支持部
１２ スタッド
１３、１３ａ、１３ｂ 支持孔
１４ 取付面
１５ 柱部
１６ 切り欠き
１７ａ、１７ｂ 段部
１８ 支持板部
１９ 溶接 DESCRIPTION OF SYMBOLS 1, 1a, 1b Rolling bearing unit for vehicle support 2 Inner ring track 3 Inner ring 4, 4a, 4b, 4c Hub 5 Rolling element 6 Outer ring track 7, 7a, 7b Flange 8, 8a, 8b Flange support part 9 Flange part 10, 10a Pilot part 11 Fitting support part 12 Stud 13, 13a, 13b Support hole 14 Mounting surface 15 Column part 16 Notch 17a, 17b Step part 18 Support plate part 19 Welding

Claims (1)

外周面に複列の内輪軌道を有し、使用時に懸架装置に支持固定された状態で回転しない内輪部材と、軸方向外端寄り部分に車輪を支持する為のフランジを、内周面に複列の外輪軌道を、それぞれ有し、使用時に上記車輪と共に回転する外輪部材と、上記各内輪軌道と上記各外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た転動体とを備えた
車輪支持用転がり軸受ユニットに於いて、
上記外輪部材の軸方向内端部と上記フランジの径方向外端部とを掛け渡す状態でフランジ支持部を、上記外輪部材と一体に設けると共に、この外輪部材と別体に形成された上記フランジを、この外輪部材の軸方向外端部と上記フランジ支持部の軸方向外端部とに結合固定した
事を特徴とする車輪支持用転がり軸受ユニット。 A double row inner ring raceway is provided on the outer peripheral surface, and an inner ring member that does not rotate while being supported and fixed to the suspension device in use and a flange for supporting the wheel on the outer end in the axial direction are provided on the inner peripheral surface. A plurality of outer ring members each having a row of outer ring raceways and rotating together with the wheels in use; and a plurality of rolling elements provided in a freely rotatable manner between the inner ring raceways and the outer ring raceways. In the wheel bearing rolling bearing unit provided,
The flange formed integrally with the outer ring member in a state where the axial inner end of the outer ring member and the radial outer end of the flange are spanned, and the flange formed separately from the outer ring member A rolling bearing unit for supporting a wheel, wherein the outer ring member is coupled and fixed to the outer end portion in the axial direction of the outer ring member and the outer end portion in the axial direction of the flange support portion.
JP2009022210A 2009-02-03 2009-02-03 Rolling bearing unit for supporting wheel Withdrawn JP2010179670A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2009022210A JP2010179670A (en) 2009-02-03 2009-02-03 Rolling bearing unit for supporting wheel

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2009022210A JP2010179670A (en) 2009-02-03 2009-02-03 Rolling bearing unit for supporting wheel

Publications (1)

Publication Number Publication Date
JP2010179670A true JP2010179670A (en) 2010-08-19

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Family Applications (1)

Application Number Title Priority Date Filing Date
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Country Link
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013032094A (en) * 2011-08-02 2013-02-14 Nsk Ltd Hub bearing, speed reduction mechanism, and in-wheel motor
WO2016125821A1 (en) * 2015-02-05 2016-08-11 Ntn株式会社 Bearing for main electric motor, support structure for main shaft of main electric motor, and main electric motor for railway vehicle

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013032094A (en) * 2011-08-02 2013-02-14 Nsk Ltd Hub bearing, speed reduction mechanism, and in-wheel motor
WO2016125821A1 (en) * 2015-02-05 2016-08-11 Ntn株式会社 Bearing for main electric motor, support structure for main shaft of main electric motor, and main electric motor for railway vehicle

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