JP5476178B2 - Wheel bearing device - Google Patents

Wheel bearing device Download PDF

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JP5476178B2
JP5476178B2 JP2010077968A JP2010077968A JP5476178B2 JP 5476178 B2 JP5476178 B2 JP 5476178B2 JP 2010077968 A JP2010077968 A JP 2010077968A JP 2010077968 A JP2010077968 A JP 2010077968A JP 5476178 B2 JP5476178 B2 JP 5476178B2
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wheel
bearing device
hub
pilot
flange
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JP2010254292A (en
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清武 柴田
孝幸 乗松
光 梅木田
浩志 河村
靖史 柴田
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NTN Corp
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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
    • F16C33/588—Races of sheet metal
    • 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
    • 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
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • 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)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)
  • Rolling Contact Bearings (AREA)

Description

本発明は、自動車等の車両の駆動車輪を回転自在に支承する車輪用軸受装置、詳しくは、軽量・コンパクト化と共に、軸受の強度・耐久性の向上を図った車輪用軸受装置に関するものである。   BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a wheel bearing device that rotatably supports a drive wheel of a vehicle such as an automobile, and more particularly to a wheel bearing device that is light and compact and improves the strength and durability of a bearing. .

従来から自動車等の車輪を支持する車輪用軸受装置は、車輪を取り付けるためのハブ輪を複列の転がり軸受を介して回転自在に支承するもので、駆動輪用と従動輪用とがある。構造上の理由から、駆動輪用では内輪回転方式が、従動輪用では内輪回転と外輪回転の両方式が一般的に採用されている。この車輪用軸受装置には、懸架装置を構成するナックルとハブ輪との間に複列アンギュラ玉軸受等からなる車輪用軸受を嵌合させた第１世代と称される構造から、外方部材の外周に直接車体取付フランジまたは車輪取付フランジが形成された第２世代構造、また、ハブ輪の外周に一方の内側転走面が直接形成された第３世代構造、あるいは、ハブ輪と等速自在継手の外側継手部材の外周にそれぞれ内側転走面が直接形成された第４世代構造とに大別されている。   2. Description of the Related Art Conventionally, a wheel bearing device for supporting a wheel of an automobile or the like supports a hub wheel for mounting a wheel rotatably via a double row rolling bearing, and includes a drive wheel and a driven wheel. For structural reasons, an inner ring rotation method is generally used for driving wheels, and an inner ring rotation method and an outer ring rotation method are generally used for driven wheels. This wheel bearing device has a structure called a first generation in which a wheel bearing composed of a double-row angular ball bearing or the like is fitted between a knuckle and a hub wheel constituting a suspension device, and is an outer member. 2nd generation structure with body mounting flange or wheel mounting flange formed directly on the outer periphery of the wheel, 3rd generation structure with one inner rolling surface formed directly on the outer periphery of the hub wheel, or constant speed with the hub wheel It is roughly classified into a fourth generation structure in which the inner rolling surface is directly formed on the outer periphery of the outer joint member of the universal joint.

従来、製造コストを低減する目的から、ハブ輪や複列アンギュラ玉軸受について、板材を用いて深絞り加工により製作することが考えられている。このように、ハブ輪や複列アンギュラ玉軸受を深絞り加工で製作する場合、母材として充分な強度を確保するために肉厚の厚い板材を用いると、加工がし難く、曲げ部分の形状・精度が低下し易いので、精度を向上させるための精密技術が要求され、プレス加工であるにもかかわらず、生産効率が悪くなってしまう。   Conventionally, for the purpose of reducing manufacturing costs, it has been considered to manufacture a hub ring and a double row angular ball bearing by deep drawing using a plate material. In this way, when manufacturing hub rings and double row angular contact ball bearings by deep drawing, if a thick plate is used to ensure sufficient strength as the base material, processing is difficult and the shape of the bent part・ Since the accuracy tends to decrease, a precision technique for improving the accuracy is required, and the production efficiency deteriorates despite the press working.

こうした課題を解決したものとして、図１８に示すような車輪用軸受装置が知られている。この車輪用軸受装置５０は第３世代構造と呼称され、ハブ輪５１と複列アンギュラ玉軸受５２とを備え、ハブ輪５１は、中空の軸部５３の一方の軸端側に、径方向外方に延出する複数の切り起し片５４と、軸方向に沿って延出する複数の舌片５５とが周方向交互に設けられた構造である。複列アンギュラ玉軸受５２は、軸部５３に外装され、切り起し片５４の一側面に対して図示しない車輪やブレーキロータが軸方向に位置決めされた状態で装着され、切り起し片５４に貫通固定されるハブボルト５６によって固定される。また、各舌片５５において、付根側には、径方向外向きの膨出部５５ａが設けられ、パイロット部が形成されている。   As a solution to these problems, a wheel bearing device as shown in FIG. 18 is known. This wheel bearing device 50 is referred to as a third generation structure, and includes a hub ring 51 and a double-row angular ball bearing 52. The hub ring 51 is disposed radially outward on one shaft end side of the hollow shaft portion 53. A plurality of cut and raised pieces 54 extending in the direction and a plurality of tongue pieces 55 extending along the axial direction are provided alternately in the circumferential direction. The double-row angular ball bearing 52 is mounted on the shaft 53 and mounted with a wheel or brake rotor (not shown) positioned axially on one side of the cut-and-raised piece 54. It is fixed by a hub bolt 56 that is fixed through. Further, each tongue piece 55 is provided with a radially outwardly bulging portion 55a on the root side to form a pilot portion.

複列アンギュラ玉軸受５２は、内周に複列の外側転走面５７ａ、５７ａが形成された外方部材５７と、外周に一方の内側転走面５１ａが形成されたハブ輪５１と、このハブ輪５１の軸部５３の小径段部５３ａに外嵌され、外周に内側転走面５８ａが形成された内輪５８と、保持器５９を介して配列された複列のボール６０、６０とを備えている。   The double row angular contact ball bearing 52 includes an outer member 57 in which double row outer rolling surfaces 57a and 57a are formed on the inner periphery, a hub wheel 51 in which one inner rolling surface 51a is formed on the outer periphery, An inner ring 58 that is externally fitted to the small-diameter stepped portion 53a of the shaft portion 53 of the hub wheel 51 and has an inner rolling surface 58a formed on the outer periphery, and double rows of balls 60 and 60 arranged via a cage 59 are provided. I have.

外方部材５７の一方の軸端側には、径方向外方に延出する複数の切り起し片６１と、軸方向に沿って延出する複数の舌片６２とが周方向交互に設けられている。この切り起し片６１の一側に対して図示しないナックルが軸方向に位置決めされた状態で装着され、図示しない固定ボルトにより固定されている。また、各舌片５５とナックルの貫通孔内周面とを密に接触させるように互いの寸法関係を規定することにより、ナックルに対して複列アンギュラ玉軸受５２の芯出しが行われる。そして、ハブ輪５１の軸部５３の小径段部５３ａの端部がローリング加締により径方向外方に屈曲され、内輪５８が軸方向に固定されている。   A plurality of cut-and-raised pieces 61 extending radially outward and a plurality of tongue pieces 62 extending along the axial direction are provided alternately on one axial end side of the outer member 57 in the circumferential direction. It has been. A knuckle (not shown) is attached to one side of the cut and raised piece 61 in a state of being positioned in the axial direction and is fixed by a fixing bolt (not shown). In addition, the double row angular ball bearings 52 are centered with respect to the knuckle by defining the dimensional relationship so that each tongue piece 55 and the inner peripheral surface of the through hole of the knuckle are in close contact with each other. The end portion of the small diameter step portion 53a of the shaft portion 53 of the hub wheel 51 is bent radially outward by rolling caulking, and the inner ring 58 is fixed in the axial direction.

ハブ輪５１および複列アンギュラ玉軸受５２の外方部材５７は、円筒管を母材として、冷間鍛造加工、切り込み加工、曲げ加工を経て製作されているので、精密技術を必要とせずに済むと共に、芯出しのための部品を後付けする必要がないので、製造コストを低減することができる。   The outer member 57 of the hub wheel 51 and the double-row angular ball bearing 52 is manufactured through a cold forging process, a cutting process, and a bending process using a cylindrical tube as a base material, so that it does not require a precision technique. At the same time, it is not necessary to retrofit parts for centering, so that the manufacturing cost can be reduced.

特開２００３−２５８０３号公報JP 2003-25803 A

然しながら、この従来の車輪用軸受装置５０では、ハブ輪５１や外方部材５７の切り起し片５４、６１に大きなモーメント荷重が負荷された場合、切り起し片５４、６１が１枚の板材を径方向外方に延出させて形成しているだけのため、強度・剛性が不足し、所望の耐久性が得られないと言った課題がある。   However, in this conventional wheel bearing device 50, when a large moment load is applied to the cut and raised pieces 54 and 61 of the hub wheel 51 and the outer member 57, the cut and raised pieces 54 and 61 are a single plate. However, there is a problem that strength and rigidity are insufficient and desired durability cannot be obtained.

ここで、母材として充分な強度を確保するために肉厚の厚い板材を用いると、加工がし難く、曲げ部分の形状・精度が低下し易いので、精度を向上させるための精密技術が要求される。これでは、プレス加工であるにもかかわらず、生産効率が悪くなってしまい製造コストがアップするだけでなく、軽量化を達成することが難しくなる。   Here, if a thick plate material is used to ensure sufficient strength as the base material, it is difficult to process and the shape and accuracy of the bent part are likely to deteriorate, so precision technology to improve accuracy is required. Is done. In this case, in spite of the press working, not only the production efficiency is deteriorated and the manufacturing cost is increased, but also it is difficult to achieve the weight reduction.

本発明は、このような事情に鑑みてなされたもので、軽量・コンパクト化と共に、軸受の強度・耐久性の向上を図った車輪用軸受装置を提供することを目的としている。   The present invention has been made in view of such circumstances, and an object of the present invention is to provide a wheel bearing device in which the strength and durability of the bearing are improved together with reduction in weight and size.

係る目的を達成すべく、本発明のうち請求項１に記載の発明は、内周に複列の円弧状の外側転走面が一体に形成された外方部材と、アウター側の端部に車輪を取り付けるための車輪取付フランジを一体に有し、外周に前記複列の転走面の一方に対向する円弧状の内側転走面と、この内側転走面から軸方向に延びる円筒状の小径段部が形成されたハブ輪、およびこのハブ輪の小径段部に所定のシメシロを介して圧入され、外周に前記複列の外側転走面の他方に対向する円弧状の内側転走面が形成された内輪からなる内方部材と、この内方部材と前記外方部材の両転走面間に保持器を介して転動自在に収容された複列のボールと、前記外方部材と内方部材との間に形成された環状空間の開口部に装着されたシールとを備え、前記小径段部の端部を径方向外方に塑性変形させて形成した加締部によって、前記ハブ輪に対して前記内輪が軸方向に固定された車輪用軸受装置において、前記ハブ輪が板材またはパイプ材から塑性加工によって形成され、前記車輪取付フランジが、径方向外方に延出して形成されたフランジ部と、円板状に形成され、前記車輪およびブレーキロータをガイドするパイロット部が軸方向に延出して形成された別体のパイロット部材とで構成されると共に、前記フランジ部とパイロット部材の周方向等配にボルト挿通孔が形成され、これらボルト挿通孔にハブボルトが圧入されて前記パイロット部材が前記フランジ部に一体に接合され、かつ、前記外方部材が板材またはパイプ材から塑性加工によって形成され、インナー側の端部にナックルに取り付けられるための車体取付フランジを一体に有し、この車体取付フランジが、径方向外方に延出して形成されたフランジ部と、円板状に形成され、前記ナックルに内嵌されるパイロット部が軸方向に延出して形成された別体のパイロット部材とで構成され、前記フランジ部とパイロット部材の周方向等配にボルト挿通孔が形成されている。 In order to achieve such an object, the invention described in claim 1 of the present invention includes an outer member in which a double-row arc-shaped outer rolling surface is integrally formed on the inner periphery, and an outer end portion. A wheel mounting flange for mounting a wheel is integrally formed, and an arcuate inner rolling surface facing one of the double-row rolling surfaces on the outer periphery, and a cylindrical shape extending in the axial direction from the inner rolling surface A hub ring formed with a small-diameter step portion, and an arc-shaped inner rolling surface that is press-fitted into the small-diameter step portion of the hub ring via a predetermined shimiro and faces the other of the outer rolling surfaces of the double row on the outer periphery. An inner member formed of an inner ring formed with an inner ring, a double row of balls accommodated between the rolling surfaces of the inner member and the outer member via a cage, and the outer member. And a seal attached to the opening of the annular space formed between the inner member and the inner member, and the end of the small-diameter stepped portion In a wheel bearing device in which the inner ring is fixed in the axial direction with respect to the hub ring by a caulking portion formed by plastic deformation outward in the direction, the hub ring is formed by plastic working from a plate material or a pipe material. The wheel mounting flange has a flange portion formed to extend radially outward, and is formed in a disc shape, and a pilot portion that guides the wheel and the brake rotor is formed to extend in the axial direction. A bolt insertion hole is formed at equal intervals in the circumferential direction of the flange portion and the pilot member, and a hub bolt is press-fitted into the bolt insertion hole so that the pilot member is integrated with the flange portion. They are joined, and the outer member is formed by plastic working a plate material or a pipe material, for attached to the knuckle to the end portion of the inner side The body mounting flange is integrally formed, and the vehicle body mounting flange is formed in a disk shape with a flange portion that extends radially outward, and a pilot portion that is fitted into the knuckle in the axial direction. It is comprised with the separate pilot member formed by extending, The bolt insertion hole is formed in the circumferential direction equal distribution of the said flange part and a pilot member .

このように、ハブ輪の小径段部の端部を径方向外方に塑性変形させて形成した加締部によって、ハブ輪に対して内輪が軸方向に固定された車輪用軸受装置において、ハブ輪が板材またはパイプ材から塑性加工によって形成され、車輪取付フランジが、径方向外方に延出して形成されたフランジ部と、円板状に形成され、車輪およびブレーキロータをガイドするパイロット部が軸方向に延出して形成された別体のパイロット部材とで構成されると共に、フランジ部とパイロット部材の周方向等配にボルト挿通孔が形成され、これらボルト挿通孔にハブボルトが圧入されてパイロット部材がフランジ部に一体に接合され、かつ、外方部材が板材またはパイプ材から塑性加工によって形成され、インナー側の端部にナックルに取り付けられるための車体取付フランジを一体に有し、この車体取付フランジが、径方向外方に延出して形成されたフランジ部と、円板状に形成され、ナックルに内嵌されるパイロット部が軸方向に延出して形成された別体のパイロット部材とで構成され、フランジ部とパイロット部材の周方向等配にボルト挿通孔が形成されているので、軽量・コンパクト化と共に、軸受の強度・耐久性の向上を図った車輪用軸受装置を提供することができる。 Thus, in the wheel bearing device in which the inner ring is fixed in the axial direction with respect to the hub ring by the caulking portion formed by plastically deforming the end of the small-diameter stepped portion of the hub ring radially outward, the hub A wheel is formed by plastic working from a plate material or a pipe material, a wheel mounting flange is formed by extending radially outward, and a pilot portion that is formed in a disk shape and guides the wheel and the brake rotor It is composed of a separate pilot member that extends in the axial direction, and bolt insertion holes are formed at equal intervals in the circumferential direction of the flange portion and the pilot member, and hub bolts are press-fitted into these bolt insertion holes and pilots member is joined integrally with the flange portion, the outer member is formed by plastic working a plate material or a pipe material, for attached to the knuckle to the end portion of the inner side The body mounting flange is integrated, and the body mounting flange has a flange portion that is formed to extend radially outward, and a pilot portion that is formed in a disk shape and is fitted into the knuckle extends in the axial direction. It is composed of a separate pilot member formed and a bolt insertion hole is formed in the circumferential direction equidistant between the flange part and the pilot member, so that the strength and durability of the bearing are improved with light weight and compactness It is possible to provide a wheel bearing device that achieves the above.

また、請求項２に記載の発明のように、前記フランジ部とパイロット部材の合せ面が前記インナー側のシールのアウター側に配置されると共に、前記フランジ部とパイロット部材の合せ面のうちどちらか一方の合せ面に環状溝が形成され、この環状溝に弾性部材が装着されていれば、軸受内部に封入されたグリースの外部への漏洩と、外部から雨水やダスト等が軸受内部に侵入するのを防止できると共に、外方部材を軸方向に一層軽量・コンパクト化することができる。 Further, as in the invention described in claim 2 , the mating surface of the flange portion and the pilot member is disposed on the outer side of the seal on the inner side, and one of the mating surfaces of the flange portion and the pilot member If an annular groove is formed on one mating surface and an elastic member is attached to this annular groove, leakage of grease sealed inside the bearing and rainwater, dust, etc. enter the bearing from the outside. And the outer member can be made lighter and more compact in the axial direction.

また、請求項３に記載の発明のように、前記外方部材の外径の軸方向中央部を凹ませて環状凹部が形成され、内周に環状凸部がフラット形状に形成されると共に、前記外径と環状凹部の繋ぎ部が所定の曲率半径からなる円弧状に形成され、この部位が略均等な肉厚に設定されていれば、肩部に亀裂が発生するのを防止し、かつ、旋回モーメント負荷時にボールの接触楕円が肩部を乗り上げてエッジロードが発生するのを防止することができ、軸受の耐久性を向上させることができる。 Further, as in the invention according to claim 3 , an annular concave portion is formed by denting the axial central portion of the outer diameter of the outer member, and the annular convex portion is formed in a flat shape on the inner periphery, If the connecting portion between the outer diameter and the annular recess is formed in an arc shape having a predetermined radius of curvature, and this portion is set to a substantially uniform thickness, it prevents the shoulder from cracking, and Further, it is possible to prevent the contact ellipse of the ball from climbing over the shoulder portion when the turning moment is applied and the occurrence of an edge load, thereby improving the durability of the bearing.

好ましくは、請求項４に記載の発明のように、前記繋ぎ部の曲率半径Ｒが、前記ボールの半径をＲｗとした時、Ｒ＝１．５〜２．５Ｒｗの範囲になるように設定されていれば、肉厚が薄くなり剛性が低下することもなく、また、肉厚が厚くなり塑性加工の加工性が低下することもない。 Preferably, as in the invention described in claim 4 , the curvature radius R of the joint portion is set to be in a range of R = 1.5 to 2.5Rw when the radius of the ball is Rw. In this case, the thickness is not reduced and the rigidity is not lowered, and the thickness is increased and the workability of the plastic working is not lowered.

また、請求項５に記載の発明のように、前記フランジ部が環状の基部から放射状に延び、前記ボルト挿通孔の近傍を除く部分を切欠いて４〜６つに分割されて形成されていれば、軽量化を一層図ることができる。 Further, as in the invention according to claim 5 , if the flange portion extends radially from the annular base portion and is divided into 4 to 6 parts by cutting out a portion excluding the vicinity of the bolt insertion hole. Further, the weight can be further reduced.

また、請求項６に記載の発明のように、前記パイロット部材の前記フランジ部に対応する位置の外縁部にインロウ部が一体に形成され、当該フランジ部に所定の嵌合すきまを介して外嵌されていれば、インロウ部によってフランジ部とパイロット部材との組立精度を良くすることができる。 Further, as in the invention described in claim 6 , an in-row portion is integrally formed on the outer edge portion of the pilot member at a position corresponding to the flange portion, and the flange portion is externally fitted through a predetermined fitting clearance. If so, the assembly accuracy of the flange portion and the pilot member can be improved by the inrow portion.

好ましくは、請求項７に記載の発明のように、前記インロウ部が前記フランジ部の外縁部の形状に沿った円弧状に形成されていれば、フランジ部とパイロット部材との組立精度を一層良くすることができる。 Preferably, as in the invention described in claim 7 , if the inrow portion is formed in an arc shape along the shape of the outer edge portion of the flange portion, the assembly accuracy between the flange portion and the pilot member is further improved. can do.

また、請求項８に記載の発明のように、前記フランジ部とパイロット部材に貫通孔が打ち抜き加工によって穿設され、これら貫通孔に連結ピンが圧入されていれば、この連結ピンによってフランジ部とパイロット部材とを強固に一体化することができ、強度・剛性を高めて耐久性を向上させることができる。 Further, as in the invention described in claim 8 , if through holes are punched in the flange portion and the pilot member and a connecting pin is press-fitted into the through holes, the connecting pin and the flange portion are The pilot member can be firmly integrated, and the durability can be improved by increasing the strength and rigidity.

また、請求項９に記載の発明のように、前記内輪が板材またはパイプ材から塑性加工によって形成され、前記内側転走面の大径側から軸方向に延び、前記インナー側のシールの嵌合部または摺接部となる円筒状の肩部と、この肩部から径方向内方に屈曲して形成された大端部、および前記内側転走面の小径側から軸方向に延びる円筒状の小端部を備え、この小端部が前記ハブ輪の肩部に突合せ状態で前記小径段部に圧入されると共に、当該内輪が前記加締部によって所定の軸受予圧が付与された状態で軸方向に固定されていれば、内輪を均一な肉厚で精度良く形成することができ、強度・剛性を高めることができると共に、所望の軸受予圧を容易に付与することができる。 According to a ninth aspect of the present invention, the inner ring is formed by plastic working from a plate material or a pipe material, extends in the axial direction from the large diameter side of the inner rolling surface, and fits the seal on the inner side A cylindrical shoulder that becomes a contact portion or a sliding contact portion, a large end formed by bending inward in the radial direction from the shoulder, and a cylindrical shape extending in the axial direction from the small diameter side of the inner rolling surface A small end portion is provided, and the small end portion is pressed into the small-diameter step portion in a state of abutting against the shoulder portion of the hub wheel, and the inner ring is shaft-mounted in a state where a predetermined bearing preload is applied by the crimping portion. If it is fixed in the direction, the inner ring can be formed with a uniform wall thickness with high accuracy, the strength and rigidity can be increased, and a desired bearing preload can be easily applied.

また、請求項１０に記載の発明のように、前記板材またはパイプ材が、塑性加工前にＡ１変態点以下の温度で加熱され、組織の板状のパーライトを分断して球状化焼鈍されていれば、素材が軟化して塑性加工がし易くなり、高精度に仕上げることができる。 Further, as in the invention described in claim 10 , the plate material or pipe material is heated at a temperature equal to or lower than the A1 transformation point before plastic working, and the plate-like pearlite of the structure is divided and spheroidized annealing is performed. In this case, the material is softened to facilitate plastic working and finish with high accuracy.

また、請求項１１に記載の発明のように、前記ハブ輪が、熱処理前に所定の温度へ加熱または均熱した後、所定の速度で冷却する応力除去焼きなましが実施されていれば、塑性加工により発生した内部応力を減らすことができるため、熱処理による変形を抑えることができると共に、その後の研削等の取代を小さくすることができる。 Further, as in the invention described in claim 11 , if the hub ring is heated or soaked to a predetermined temperature before heat treatment and then subjected to stress relief annealing for cooling at a predetermined speed, plastic working is performed. The internal stress generated by the above can be reduced, so that deformation due to heat treatment can be suppressed and the machining allowance for subsequent grinding or the like can be reduced.

また、請求項１２に記載の発明のように、前記ハブ輪の少なくともアウター側の端部が閉塞されていれば、外部から雨水やダスト等が中空のハブ輪の内部に侵入するのを防止でき、発錆するのを防止して耐久性を向上させることができる。 In addition, as in the invention described in claim 12 , if at least the end portion on the outer side of the hub wheel is closed, it is possible to prevent rainwater and dust from entering the hollow hub wheel from the outside. It can prevent rusting and improve durability.

また、請求項１３に記載の発明のように、前記ハブ輪のパイロット部材のパイロット部に、防錆能を有する鋼鈑からプレス加工によって形成されたエンドキャップが内嵌されていても良い。 Further, as in the invention described in claim 13 , an end cap formed by press working from a steel plate having rust prevention ability may be fitted into the pilot portion of the pilot member of the hub wheel .

好ましくは、請求項１４に記載の発明のように、前記エンドキャップの少なくとも外部の露出した表面に合成ゴムが被着されていれば、発錆をさらに防止することができると共に、高価なステンレス鋼鈑を使用することなく廉価で加工性が良好な冷間圧延鋼鈑を使用することができ、低コスト化を図ることができる。 Preferably, as in the invention described in claim 14 , if synthetic rubber is applied to at least the exposed surface of the end cap, rusting can be further prevented and expensive stainless steel is used. It is possible to use a cold-rolled steel plate that is inexpensive and has good workability without using a plate, and the cost can be reduced.

また、請求項１５に記載の発明のように、前記ハブ輪のパイロット部材がカップ状に形成され、前記パイロット部から径方向内方に延びる底部が一体に形成されていても良い。 As in the invention described in claim 15 , the pilot member of the hub wheel may be formed in a cup shape, and a bottom portion extending radially inward from the pilot portion may be integrally formed.

また、請求項１６に記載の発明のように、前記外方部材のパイロット部材がカップ状に形成され、前記パイロット部から径方向内方に延びる底部が一体に形成されていても良い。 Further, as in the invention described in claim 16 , the pilot member of the outer member may be formed in a cup shape, and a bottom portion extending radially inward from the pilot portion may be integrally formed.

本発明に係る車輪用軸受装置は、内周に複列の円弧状の外側転走面が一体に形成された外方部材と、アウター側の端部に車輪を取り付けるための車輪取付フランジを一体に有し、外周に前記複列の転走面の一方に対向する円弧状の内側転走面と、この内側転走面から軸方向に延びる円筒状の小径段部が形成されたハブ輪、およびこのハブ輪の小径段部に所定のシメシロを介して圧入され、外周に前記複列の外側転走面の他方に対向する円弧状の内側転走面が形成された内輪からなる内方部材と、この内方部材と前記外方部材の両転走面間に保持器を介して転動自在に収容された複列のボールと、前記外方部材と内方部材との間に形成された環状空間の開口部に装着されたシールとを備え、前記小径段部の端部を径方向外方に塑性変形させて形成した加締部によって、前記ハブ輪に対して前記内輪が軸方向に固定された車輪用軸受装置において、前記ハブ輪が板材またはパイプ材から塑性加工によって形成され、前記車輪取付フランジが、径方向外方に延出して形成されたフランジ部と、円板状に形成され、前記車輪およびブレーキロータをガイドするパイロット部が軸方向に延出して形成された別体のパイロット部材とで構成されると共に、前記フランジ部とパイロット部材の周方向等配にハブボルト挿通孔が形成され、これらハブボルト挿通孔にハブボルトが圧入されて前記パイロット部材が前記フランジ部に一体に接合され、かつ、前記外方部材が板材またはパイプ材から塑性加工によって形成され、インナー側の端部にナックルに取り付けられるための車体取付フランジを一体に有し、この車体取付フランジが、径方向外方に延出して形成されたフランジ部と、円板状に形成され、前記ナックルに内嵌されるパイロット部が軸方向に延出して形成された別体のパイロット部材とで構成され、前記フランジ部とパイロット部材の周方向等配にボルト挿通孔が形成されているので、軽量・コンパクト化と共に、軸受の強度・耐久性の向上を図った車輪用軸受装置を提供することができる。 The wheel bearing device according to the present invention has an outer member in which a double-row arc-shaped outer rolling surface is integrally formed on the inner periphery, and a wheel mounting flange for mounting the wheel on the outer end. A hub wheel having an arcuate inner rolling surface facing one of the double-row rolling surfaces on the outer periphery, and a cylindrical small-diameter stepped portion extending in the axial direction from the inner rolling surface, And an inner member formed of an inner ring that is press-fitted into a small-diameter step portion of the hub wheel via a predetermined shimiro and has an arc-shaped inner rolling surface facing the other of the outer rolling surfaces of the double row on the outer periphery. And a double row of balls accommodated between the rolling surfaces of the inner member and the outer member via a cage, and the outer member and the inner member. And a seal attached to the opening of the annular space, and the end of the small diameter step is plastically deformed radially outward. In the wheel bearing device in which the inner ring is fixed in the axial direction with respect to the hub ring by the crimped portion, the hub ring is formed by plastic working from a plate material or a pipe material, and the wheel mounting flange is in the radial direction. The flange portion is formed to extend outward, and the pilot portion that is formed in a disk shape and guides the wheel and the brake rotor is formed by a separate pilot member that extends in the axial direction. In addition, hub bolt insertion holes are formed at equal intervals in the circumferential direction of the flange portion and the pilot member, hub bolts are press-fitted into the hub bolt insertion holes, the pilot member is integrally joined to the flange portion , and the outer member Is formed by plastic working from a plate or pipe material, and a body mounting flange is attached to the end on the inner side to be attached to the knuckle The vehicle body mounting flange is formed in a flange-like shape extending outward in the radial direction and a disc-like pilot portion that is fitted in the knuckle and extends in the axial direction. Since the bolt insertion holes are formed in the circumferential direction equidistant between the flange part and the pilot member , the strength and durability of the bearing are improved with light weight and compactness. A wheel bearing device can be provided.

本発明に係る車輪用軸受装置の第１の実施形態を示す縦断面図である。It is a longitudinal section showing a 1st embodiment of a bearing device for wheels concerning the present invention. 図１の側面図である。It is a side view of FIG. 図１のＡ部拡大図である。It is the A section enlarged view of FIG. （ａ）は、図１のＢ部拡大図である。（ｂ）は、図１のＣ部拡大図である。(A) is the B section enlarged view of FIG. (B) is the C section enlarged view of FIG. 図１のハブ輪単体を示す縦断面図である。It is a longitudinal cross-sectional view which shows the hub ring single-piece | unit of FIG. 図１の外方部材単体を示す縦断面図である。It is a longitudinal cross-sectional view which shows the outer member single-piece | unit of FIG. 本発明に係る車輪用軸受装置の第２の実施形態を示す縦断面図である。It is a longitudinal cross-sectional view which shows 2nd Embodiment of the wheel bearing apparatus which concerns on this invention. 図７のＤ部拡大図である。It is the D section enlarged view of FIG. 図７のＥ部拡大図である。It is the E section enlarged view of FIG. 本発明に係る車輪用軸受装置の第３の実施形態を示す縦断面図である。It is a longitudinal cross-sectional view which shows 3rd Embodiment of the wheel bearing apparatus which concerns on this invention. 図１０のＦ部拡大図である。It is the F section enlarged view of FIG. 図１０のＧ部拡大図である。It is the G section enlarged view of FIG. 図１０のハブ輪単体を示す縦断面図である。It is a longitudinal cross-sectional view which shows the hub ring single-piece | unit of FIG. 図１０の外方部材単体を示す縦断面図である。It is a longitudinal cross-sectional view which shows the outer member single-piece | unit of FIG. 本発明に係る車輪用軸受装置の参考例を示す縦断面図である。It is a longitudinal cross-sectional view which shows the reference example of the wheel bearing apparatus which concerns on this invention. 本発明に係る車輪用軸受装置の第４の実施形態を示す縦断面図である。It is a longitudinal cross-sectional view which shows 4th Embodiment of the wheel bearing apparatus which concerns on this invention. 本発明に係る車輪用軸受装置の第５の実施形態を示す縦断面図である。It is a longitudinal cross-sectional view which shows 5th Embodiment of the wheel bearing apparatus which concerns on this invention. 従来の車輪用軸受装置を示す縦断面図である。It is a longitudinal cross-sectional view which shows the conventional wheel bearing apparatus.

内周に複列の円弧状の外側転走面が一体に形成された外方部材と、アウター側の端部に車輪を取り付けるための車輪取付フランジを一体に有し、外周に前記複列の転走面の一方に対向する円弧状の内側転走面と、この内側転走面から軸方向に延びる円筒状の小径段部が形成されたハブ輪、およびこのハブ輪の小径段部に所定のシメシロを介して圧入され、外周に前記複列の外側転走面の他方に対向する円弧状の内側転走面が形成された内輪からなる内方部材と、この内方部材と前記外方部材の両転走面間に保持器を介して転動自在に収容された複列のボールと、前記外方部材と内方部材との間に形成された環状空間の開口部に装着されたシールとを備え、前記小径段部の端部を径方向外方に塑性変形させて形成した加締部によって、前記ハブ輪に対して前記内輪が軸方向に固定された車輪用軸受装置において、前記ハブ輪が板材またはパイプ材から塑性加工によって形成され、前記車輪取付フランジが、径方向外方に延出して形成されたフランジ部と、円板状に形成され、前記車輪およびブレーキロータをガイドするパイロット部が軸方向に延出して形成された別体のパイロット部材とで構成されると共に、このパイロット部材の前記フランジ部に対応する位置の外縁部にインロウ部が一体に形成され、当該フランジ部に所定の嵌合すきまを介して外嵌され、前記フランジ部とパイロット部材の周方向等配にハブボルト挿通孔が形成され、これらハブボルト挿通孔にハブボルトが圧入されて前記パイロット部材が前記フランジ部に一体に接合されている。   The outer member integrally formed with the outer circumferential rolling surface of the double-row arc shape on the inner periphery and the wheel mounting flange for attaching the wheel to the end portion on the outer side are integrally formed, and the double-row on the outer periphery. A hub ring formed with an arcuate inner rolling surface facing one of the rolling surfaces, a cylindrical small-diameter step portion extending in the axial direction from the inner rolling surface, and a predetermined diameter on the small-diameter step portion of the hub ring. An inner member formed by an inner ring that is press-fitted through an outer periphery and has an arc-shaped inner rolling surface facing the other of the outer rolling surfaces of the double row on the outer periphery, and the inner member and the outer member. A double row of balls accommodated in a rollable manner via a cage between both rolling surfaces of the member and an opening of an annular space formed between the outer member and the inner member. The hub is formed by a crimped portion formed by plastically deforming an end portion of the small-diameter stepped portion radially outward. In the wheel bearing device in which the inner ring is fixed in the axial direction, the hub ring is formed by plastic working from a plate material or a pipe material, and the wheel mounting flange is formed to extend radially outward. The flange portion is formed of a disc-shaped pilot member that guides the wheel and the brake rotor and extends in the axial direction. The flange portion of the pilot member An inrow portion is integrally formed on the outer edge portion at a position corresponding to the flange portion, and the flange portion is externally fitted through a predetermined fitting clearance, and hub bolt insertion holes are formed at equal intervals in the circumferential direction of the flange portion and the pilot member. The hub bolts are press-fitted into the hub bolt insertion holes, and the pilot member is integrally joined to the flange portion.

以下、本発明の実施の形態を図面に基づいて詳細に説明する。
図１は、本発明に係る車輪用軸受装置の第１の実施形態を示す縦断面図、図２は、図１の側面図、図３は、図１のＡ部拡大図、図４（ａ）は、図１のＢ部拡大図、（ｂ）は、図１のＣ部拡大図、図５は、図１のハブ輪単体を示す縦断面図、図６は、図１の外方部材単体を示す縦断面図である。なお、以下の説明では、車両に組み付けた状態で車両の外側寄りとなる側をアウター側（図１の左側）、中央寄り側をインナー側（図１の右側）という。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
1 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention, FIG. 2 is a side view of FIG. 1, FIG. 3 is an enlarged view of a portion A in FIG. ) Is an enlarged view of part B in FIG. 1, FIG. 5B is an enlarged view of part C in FIG. 1, FIG. 5 is a longitudinal sectional view showing a single hub wheel in FIG. 1, and FIG. It is a longitudinal section showing a simple substance. In the following description, the side closer to the outer side of the vehicle when assembled to the vehicle is referred to as the outer side (left side in FIG. 1), and the side closer to the center is referred to as the inner side (right side in FIG. 1).

この車輪用軸受装置は従動輪側の第３世代構造と呼称され、内方部材１と外方部材２、および両部材１、２間に転動自在に収容された複列のボール３、３とを備えている。内方部材１は、ハブ輪４と、このハブ輪４に所定のシメシロを介して圧入された内輪５とからなる。   This wheel bearing device is referred to as a third generation structure on the driven wheel side, and includes a plurality of balls 3, 3, which are accommodated so as to roll between the inner member 1 and the outer member 2, and both members 1, 2. And. The inner member 1 includes a hub ring 4 and an inner ring 5 press-fitted into the hub ring 4 through a predetermined shimiro.

ハブ輪４は、アウター側の端部に車輪（図示せず）を取り付けるための車輪取付フランジ６を一体に有し、外周に一方（アウター側）の円弧状の内側転走面４ａと、この内側転走面４ａから肩部４ｂを介して軸方向に延びる円筒状の小径段部４ｃが形成されている。車輪取付フランジ６は、径方向外方に延出して形成されたフランジ部７と、このフランジ部７に一体に接合された別体のパイロット部材８とで構成されている。車輪取付フランジ６にはハブボルト６ａが周方向等配に植設されると共に、これらハブボルト６ａ間には円孔８ａが形成されている。この円孔８ａは軽量化に寄与できるだけでなく、装置の組立・分解工程において、レンチ等の締結治具をこの円孔８ａから挿入することができ作業を簡便化することができる。   The hub wheel 4 integrally has a wheel mounting flange 6 for mounting a wheel (not shown) at an end portion on the outer side, and one (outer side) arcuate inner rolling surface 4a on the outer periphery. A cylindrical small diameter step portion 4c extending in the axial direction from the inner rolling surface 4a via the shoulder portion 4b is formed. The wheel mounting flange 6 includes a flange portion 7 formed to extend outward in the radial direction, and a separate pilot member 8 integrally joined to the flange portion 7. Hub bolts 6a are planted on the wheel mounting flange 6 in a circumferentially uniform manner, and circular holes 8a are formed between the hub bolts 6a. The circular hole 8a not only contributes to weight reduction, but also a fastening jig such as a wrench can be inserted from the circular hole 8a in the assembly / disassembly process of the apparatus, and the work can be simplified.

フランジ部７は環状の基部７ａから放射状に延び、周方向等配にハブボルト挿通孔７ｂが打ち抜き加工によって形成されると共に、これらハブボルト挿通孔７ｂの近傍を除く部分を切欠いて４〜６つ（ここでは５つ）に分割されて形成されている（図２参照）。これにより、ハブ輪４の軽量化を図ることができる。一方、パイロット部材８は円板状に形成され、周方向等配にハブボルト挿通孔８ｂが形成されると共に、車輪およびブレーキロータ（図示せず）をガイドするパイロット部８ｃが軸方向に延出して形成されている。   The flange portion 7 extends radially from the annular base portion 7a, and hub bolt insertion holes 7b are formed in a circumferentially uniform manner by punching, and four to six portions are cut out except for the vicinity of the hub bolt insertion holes 7b (here) Then, it is divided into five) (see FIG. 2). Thereby, weight reduction of the hub ring 4 can be achieved. On the other hand, the pilot member 8 is formed in a disc shape, and hub bolt insertion holes 8b are formed in a circumferentially equidistant manner, and a pilot portion 8c for guiding a wheel and a brake rotor (not shown) extends in the axial direction. Is formed.

パイロット部材８は、図３に拡大して示すように、フランジ部７に対応する位置の外縁部にインロウ部９が一体に形成され、フランジ部７に所定の嵌合すきまを介して外嵌されている。このインロウ部９によってフランジ部７とパイロット部材８との組立精度を良くすることができると共に、ハブ輪４の回転精度を向上させることができる。インロウ部９は、フラット形状でも良いが、フランジ部７の外縁部の形状に沿った円弧状に形成することにより、フランジ部７とパイロット部材８との組立精度を一層良くすることができる。また、フランジ部７とパイロット部材８に形成されたボルト挿通孔７ｂ、８ｂにハブボルト６ａを圧入することによって他の固定手段を介すことなく２部材を固定することができると共に、ハブボルト６ａの圧入幅を確保することができ、長期間に亘ってハブボルト６ａが緩むのを防止して固定力を高めることができる。   As shown in an enlarged view in FIG. 3, the pilot member 8 is integrally formed with an inrow portion 9 at an outer edge portion at a position corresponding to the flange portion 7 and is externally fitted to the flange portion 7 via a predetermined fitting clearance. ing. The in-row portion 9 can improve the assembly accuracy of the flange portion 7 and the pilot member 8, and can improve the rotation accuracy of the hub wheel 4. Although the in-row part 9 may be flat, by forming it in an arc shape along the shape of the outer edge part of the flange part 7, the assembly accuracy of the flange part 7 and the pilot member 8 can be further improved. Further, by pressing the hub bolt 6a into the bolt insertion holes 7b, 8b formed in the flange portion 7 and the pilot member 8, the two members can be fixed without any other fixing means, and the hub bolt 6a is press-fitted. The width can be secured, and the fixing force can be increased by preventing the hub bolt 6a from loosening over a long period of time.

内輪５は、図１に示すように、外周に他方（インナー側）の円弧状の内側転走面５ａが形成されると共に、この内側転走面５ａの大径側から軸方向に延び、後述するシール２２の嵌合部となる円筒状の肩部１０と、この肩部１０から径方向内方に屈曲して形成された大端部１１、および内側転走面５ａの小径側から軸方向に延びる円筒状の小端部１２を備えている。そして、この小端部１２がハブ輪４の肩部４ｂに突合せ状態で小径段部４ｃに圧入されて背面合せタイプの複列アンギュラ玉軸受を構成すると共に、小径段部４ｃの端部を塑性変形させて形成した加締部４ｄによって所定の軸受予圧が付与された状態で軸方向に固定され、所謂セルフリテイン構造を構成している。このような構成を採用することにより、均一な肉厚で精度良く形成することができ、強度・剛性を高めることができると共に、所望の軸受予圧を容易に付与することができる。   As shown in FIG. 1, the inner ring 5 is formed with the other (inner side) arcuate inner rolling surface 5a on the outer periphery, and extends in the axial direction from the large diameter side of the inner rolling surface 5a. A cylindrical shoulder portion 10 serving as a fitting portion of the seal 22 to be engaged, a large end portion 11 formed by bending radially inward from the shoulder portion 10, and an axial direction from the small diameter side of the inner rolling surface 5a A cylindrical small end portion 12 is provided. The small end portion 12 is pressed into the small diameter step portion 4c in a state of abutting against the shoulder portion 4b of the hub wheel 4 to constitute a back-to-back type double row angular ball bearing, and the end portion of the small diameter step portion 4c is made plastic. It is fixed in the axial direction in a state where a predetermined bearing preload is applied by a deformed caulking portion 4d, thereby forming a so-called self-retaining structure. By adopting such a configuration, it is possible to form with a uniform thickness and high accuracy, to increase strength and rigidity, and to easily apply a desired bearing preload.

外方部材２は、インナー側の端部にナックル（図示せず）に取り付けられるための車体取付フランジ１３を一体に有し、内周に径方向内方に突出する環状凸部１４と、この環状凸部１４の両側に複列の円弧状の外側転走面２ａ、２ａが一体に形成されている。また、複列の外側転走面２ａ、２ａの両端部に後述するシール２１、２２の嵌合部１５、１６が形成される。   The outer member 2 integrally has a vehicle body mounting flange 13 to be attached to a knuckle (not shown) at an end on the inner side, an annular convex portion 14 projecting radially inward on the inner periphery, Double-row arc-shaped outer rolling surfaces 2 a and 2 a are integrally formed on both sides of the annular convex portion 14. Further, fitting portions 15 and 16 of seals 21 and 22 to be described later are formed at both ends of the double row outer rolling surfaces 2a and 2a.

車体取付フランジ１３は、径方向外方に延出して形成されたフランジ部１７と、このフランジ部１７に一体に接合された別体のパイロット部材１８とで構成されている。フランジ部１７は、環状の基部１７ａから放射状に延び、周方向等配に固定ボルト挿通孔１７ｂが打ち抜き加工によって穿設されると共に、これら固定ボルト挿通孔１７ｂの近傍を除く部分を切欠いて４つに分割されて形成されている（図２参照）。一方、パイロット部材１８は円板状に形成され、周方向等配に固定ボルト挿通孔１８ａが打ち抜き加工によって形成されると共に、ナックルが外嵌されるパイロット部１８ｂが軸方向に延出して形成されている。パイロット部材１８は、図４（ｂ）に示すように、車体取付フランジ１７に対応する位置の外縁部にインロウ部１９が一体に形成され、フランジ部１７に所定の嵌合すきまを介して外嵌されている。このインロウ部１９によってフランジ部１７とパイロット部材１８との組立精度を良くすることができる。   The vehicle body mounting flange 13 includes a flange portion 17 formed to extend radially outward, and a separate pilot member 18 integrally joined to the flange portion 17. The flange portion 17 extends radially from the annular base portion 17a, and fixing bolt insertion holes 17b are formed by punching in a circumferentially equidistant manner, and four portions are cut out except for the vicinity of the fixing bolt insertion holes 17b. (See FIG. 2). On the other hand, the pilot member 18 is formed in a disc shape, and the fixing bolt insertion holes 18a are formed by punching processing in a circumferentially uniform manner, and the pilot portion 18b in which the knuckle is fitted is formed to extend in the axial direction. ing. As shown in FIG. 4B, the pilot member 18 is integrally formed with an inrow portion 19 at an outer edge portion at a position corresponding to the vehicle body mounting flange 17 and is fitted to the flange portion 17 via a predetermined fitting clearance. Has been. The in-row portion 19 can improve the assembly accuracy of the flange portion 17 and the pilot member 18.

内方部材１と外方部材２の両転走面間には複列のボール３、３が収容され、保持器２０、２０によって転動自在に保持されている。そして、内方部材１と外方部材２との間に形成される環状空間の開口部にはシール２１、２２が装着され、軸受内部に封入されたグリースの外部への漏洩と、外部から雨水やダスト等が軸受内部に侵入するのを防止している。   Between both rolling surfaces of the inner member 1 and the outer member 2, double rows of balls 3 and 3 are accommodated and held by the cages 20 and 20 so as to be freely rollable. Seals 21 and 22 are attached to the opening of the annular space formed between the inner member 1 and the outer member 2, and leakage of grease sealed inside the bearing and rainwater from the outside And dust are prevented from entering the bearing.

アウター側のシール２１は、外方部材２のアウター側端部の内周に圧入される芯金２３と、この芯金２３に加硫接着により一体に接合されたシール部材２４とからなる一体型のシールで構成されている。芯金２３は、オーステナイト系ステンレス鋼鈑（ＪＩＳ規格のＳＵＳ３０４系等）や冷間圧延鋼鈑（ＪＩＳ規格のＳＰＣＣ系等）をプレス加工にて形成されている。   The outer-side seal 21 is an integrated type composed of a core metal 23 press-fitted into the inner periphery of the outer-side end portion of the outer member 2 and a seal member 24 integrally joined to the core metal 23 by vulcanization adhesion. It is composed of a seal. The core metal 23 is formed by pressing an austenitic stainless steel plate (JIS standard SUS304 type or the like) or a cold rolled steel plate (JIS standard SPCC type or the like).

一方、シール部材２４はＮＢＲ（アクリロニトリル−ブタジエンゴム）等の合成ゴムからなり、径方向外方に傾斜して形成されたサイドリップ２４ａとダストリップ２４ｂ、および軸受内方側に傾斜して形成されたグリースリップ２４ｃを一体に有している。そして、フランジ部７のインナー側の基部７ａは断面が円弧状の曲面に形成され、この基部７ａにサイドリップ２４ａとダストリップ２４ｂが所定のシメシロをもって摺接されると共に、グリースリップ２４ｃが所定の径方向すきまを介して対峙し、ラビリンスシールが構成されている。   On the other hand, the seal member 24 is made of synthetic rubber such as NBR (acrylonitrile-butadiene rubber), and is formed to be inclined to the side lip 24a and the dust lip 24b formed to be inclined outward in the radial direction, and to the inner side of the bearing. The grease lip 24c is integrally provided. The base portion 7a on the inner side of the flange portion 7 is formed into a curved surface having an arc-shaped cross section. The side lip 24a and the dust lip 24b are slidably contacted with the base portion 7a with a predetermined squeeze, and the grease lip 24c is A labyrinth seal is formed through the radial clearance.

一方、インナー側のシール２２は、図４（ａ）に拡大して示すように、互いに対向配置された環状のシール板２５とスリンガ２６とからなる、所謂パックシールで構成されている。シール板２５は、外方部材２の端部内周に圧入された芯金２７と、この芯金２７に加硫接着により一体に接合されたシール部材２８とからなる。芯金２７は、オーステナイト系ステンレス鋼鈑（ＪＩＳ規格のＳＵＳ３０４系等）や防錆処理された冷間圧延鋼鈑（ＪＩＳ規格のＳＰＣＣ系等）等の防錆能を有する鋼板からプレス加工にて断面略Ｌ字状に形成されている。   On the other hand, the seal 22 on the inner side is constituted by a so-called pack seal comprising an annular seal plate 25 and a slinger 26 which are arranged to face each other, as shown in an enlarged view in FIG. The seal plate 25 is composed of a core metal 27 press-fitted into the inner periphery of the end of the outer member 2 and a seal member 28 integrally joined to the core metal 27 by vulcanization adhesion. The core metal 27 is formed by pressing from a steel plate having rust prevention ability, such as an austenitic stainless steel plate (JIS standard SUS304 type or the like) or a rust-proof cold rolled steel plate (JIS standard SPCC type or the like). The cross section is substantially L-shaped.

シール部材２８はＮＢＲ等の合成ゴムからなり、径方向外方に傾斜して延びるサイドリップ２８ａと、二股状に形成されたグリースリップ２８ｂとダストリップ２８ｃとを有している。   The seal member 28 is made of a synthetic rubber such as NBR, and includes a side lip 28a extending obliquely outward in the radial direction, a grease lip 28b and a dust lip 28c formed in a bifurcated shape.

一方、スリンガ２６は、オーステナイト系ステンレス鋼鈑（ＪＩＳ規格のＳＵＳ３０４系等）や防錆処理された冷間圧延鋼鈑（ＪＩＳ規格のＳＰＣＣ系等）等の防錆能を有する鋼板からプレス加工によって断面略Ｌ字状に形成され、内輪５の肩部１０に圧入される円筒部２６ａと、この円筒部２６ａから径方向外方に延びる立板部２６ｂとを備えている。そして、シール部材２８のサイドリップ２８ａが立板部２６ｂに所定の軸方向シメシロを介して摺接されると共に、グリースリップ２８ｂとダストリップ２８ｃが円筒部２６ａに所定の径方向シメシロを介して摺接されている。さらに、スリンガ２６における立板部２６ｂは、シール板２５と僅かな径方向すきまを介して対峙し、ラビリンスシールが構成されている。   On the other hand, the slinger 26 is formed by pressing a steel plate having an antirust function such as an austenitic stainless steel plate (JIS standard SUS304 type or the like) or a rust-proof cold rolled steel plate (JIS standard SPCC type or the like). A cylindrical portion 26a that is formed in a substantially L-shaped cross section and is press-fitted into the shoulder portion 10 of the inner ring 5, and a standing plate portion 26b that extends radially outward from the cylindrical portion 26a. Then, the side lip 28a of the seal member 28 is slidably contacted with the upright plate portion 26b via a predetermined axial nip, and the grease lip 28b and the dust lip 28c are slid onto the cylindrical portion 26a via a predetermined radial nip. It is touched. Further, the standing plate portion 26b of the slinger 26 is opposed to the seal plate 25 through a slight radial clearance to form a labyrinth seal.

ハブ輪４は、図５に示すように、炭素量が比較的少ないＳＣｒ４２０やＳＣＭ４１５等の浸炭鋼からなる板材またはパイプ材をプレス加工または冷間のローリング加工（以下、塑性加工という）によって形成されている。具体的には、ハブ輪４の本体部分は、パイプ材からプレス加工および冷間のローリング加工によって形成され、パイロット部材８は、板材からプレス加工によって形成されている。また、塑性加工でバリが発生する両端面は加工後に旋削加工されるか、必要に応じて研削加工が施される。そして、少なくともハブ輪４の本体部分が浸炭焼入れによって表面硬さを５０〜６４ＨＲＣの範囲に硬化処理されている。なお、加締部４ｄは、防浸炭により素材硬さの生のままとされている。さらに、内側転走面４ａが、研削加工によって所定の寸法、精度に形成されている。その後、必要に応じて超仕上げ加工が施される。これにより、フランジ部７に負荷される回転曲げ荷重に対して充分な機械的強度を有し、小径段部４ｃの耐フレッティング性が向上してハブ輪４の耐久性が一段と向上すると共に、微小なクラック等の発生がなく加締部４ｄの塑性加工をスムーズに行うことができる。   As shown in FIG. 5, the hub wheel 4 is formed by pressing or cold rolling (hereinafter referred to as plastic working) a plate material or pipe material made of carburized steel such as SCr420 or SCM415 with a relatively small amount of carbon. ing. Specifically, the main body portion of the hub wheel 4 is formed from a pipe material by pressing and cold rolling, and the pilot member 8 is formed from a plate material by pressing. Further, both end faces where burrs are generated by plastic working are turned after the machining, or are ground if necessary. At least the main body portion of the hub wheel 4 is hardened by carburizing and quenching to a surface hardness of 50 to 64 HRC. Note that the caulking portion 4d is kept raw in raw material hardness by carburization prevention. Furthermore, the inner rolling surface 4a is formed with predetermined dimensions and accuracy by grinding. Thereafter, superfinishing is performed as necessary. Thereby, it has sufficient mechanical strength with respect to the rotational bending load applied to the flange portion 7, the fretting resistance of the small diameter step portion 4c is improved, and the durability of the hub wheel 4 is further improved. There is no occurrence of minute cracks and the like, and the plastic working of the crimped portion 4d can be performed smoothly.

ここで、ハブ輪４の材質としてこれ以外にも、ＳＣＭ４４０等の浸炭鋼、あるいは冷間圧延鋼鈑（ＪＩＳ規格のＳＰＣＣ系等）やＳ４５Ｃ等の炭素鋼を例示することができる。冷間圧延鋼鈑や炭素鋼の場合、内側転走面４ａをはじめ、アウター側のシールランド部となる基部７ａから小径段部４ｃに亙って高周波焼入れによって表面硬さを５０〜６４ＨＲＣの範囲に硬化処理が施される。   Here, as the material of the hub wheel 4, other than this, carburized steel such as SCM440, cold rolled steel plate (JIS standard SPCC system, etc.), and carbon steel such as S45C can be exemplified. In the case of cold-rolled steel or carbon steel, the surface hardness is in the range of 50 to 64 HRC by induction hardening from the inner rolling surface 4a to the small diameter step 4c from the base 7a serving as the outer seal land. Is cured.

外方部材２は、図６に示すように、ＳＣｒ４２０やＳＣＭ４１５等の浸炭鋼からなる板材およびパイプ材から塑性加工によって形成されている。具体的には、外方部材２の本体部分は、パイプ材からプレス加工および冷間のローリング加工によって形成され、パイロット部材１８は、板材からプレス加工によって形成されている。そして、少なくとも外方部材２の本体部分が浸炭焼入れによって表面硬さを５０〜６４ＨＲＣの範囲に硬化処理されている。外方部材２の材質としてこれ以外にも、ＳＣＭ４４０等の浸炭鋼、あるいは冷間圧延鋼鈑やＳ４５Ｃ等の炭素鋼を例示することができる。冷間圧延鋼鈑や炭素鋼の場合、少なくとも外方部材２の複列の外側転走面２ａ、２ａが高周波焼入れによって表面硬さを５０〜６４ＨＲＣの範囲に硬化処理が施されている。そして、複列の外側転走面２ａ、２ａが、研削加工によって所定の寸法、精度に形成されている。なお、その後、必要に応じて超仕上げ加工が施される。   As shown in FIG. 6, the outer member 2 is formed by plastic working from a plate material and a pipe material made of carburized steel such as SCr420 and SCM415. Specifically, the main body portion of the outer member 2 is formed from a pipe material by pressing and cold rolling, and the pilot member 18 is formed from a plate material by pressing. At least the main body portion of the outer member 2 is hardened by carburizing and quenching to a surface hardness of 50 to 64 HRC. Other examples of the material of the outer member 2 include carburized steel such as SCM440, or cold rolled steel or carbon steel such as S45C. In the case of cold-rolled steel or carbon steel, at least the double row outer raceway surfaces 2a and 2a of the outer member 2 are hardened by induction hardening in a range of 50 to 64 HRC. The double row outer rolling surfaces 2a, 2a are formed with predetermined dimensions and accuracy by grinding. After that, superfinishing is performed as necessary.

内輪５は、ＳＵＪ２等の軸受鋼やＳＣｒ４２０やＳＣＭ４１５等の浸炭鋼からなるパイプ材から塑性加工によって形成されている。そして、ズブ焼入れや浸炭焼入れによって表面硬さを５０〜６４ＨＲＣの範囲に硬化処理されている。そして、内側転走面５ａが、研削加工によって所定の寸法、精度に形成されている。なお、その後、必要に応じて超仕上げ加工が施される。内輪５の材質としてこれ以外にも、ＳＣＭ４４０等の浸炭鋼、あるいは冷間圧延鋼鈑やＳ４５Ｃ等の炭素鋼を例示することができる。冷間圧延鋼鈑や炭素鋼の場合、少なくとも内側転走面５ａが高周波焼入れによって表面硬さを５０〜６４ＨＲＣの範囲に硬化処理が施されている。   The inner ring 5 is formed by plastic working from a pipe material made of bearing steel such as SUJ2 or carburized steel such as SCr420 or SCM415. And the surface hardness is hardened in the range of 50 to 64 HRC by submerged quenching or carburizing quenching. The inner rolling surface 5a is formed with a predetermined size and accuracy by grinding. After that, superfinishing is performed as necessary. In addition to this, examples of the material of the inner ring 5 include carburized steel such as SCM440, or cold rolled steel or carbon steel such as S45C. In the case of a cold rolled steel plate or carbon steel, at least the inner rolling surface 5a is subjected to a hardening process in a range of 50 to 64 HRC by induction hardening.

このように、本実施形態では、ハブ輪４と内輪５および外方部材２が鋼板から塑性加工によって形成され、車輪取付フランジ６が、径方向外方に延出して形成されたフランジ部７と、円板状に形成された別体のパイロット部材８とで構成されると共に、フランジ部７とパイロット部材８の周方向等配にハブボルト挿通孔７ｂ、８ｂが形成され、これらハブボルト挿通孔７ｂ、８ｂにハブボルト６ａが圧入されてパイロット部材８がフランジ部７に一体に接合されているので、軽量・コンパクト化と共に、軸受の強度・耐久性の向上を図った車輪用軸受装置を提供することができる。   Thus, in this embodiment, the hub wheel 4, the inner ring 5, and the outer member 2 are formed from a steel plate by plastic working, and the wheel mounting flange 6 is formed by extending outward in the radial direction. And a separate pilot member 8 formed in a disc shape, and hub bolt insertion holes 7b, 8b are formed at equal intervals in the circumferential direction of the flange portion 7 and the pilot member 8, and these hub bolt insertion holes 7b, Since the hub bolt 6a is press-fitted into 8b and the pilot member 8 is integrally joined to the flange portion 7, it is possible to provide a wheel bearing device that is lightweight and compact and improves the strength and durability of the bearing. it can.

さらに、本実施形態では、塑性加工前に素材となる板材あるいはパイプ材が、Ａ１変態点以下の温度で加熱され、組織の板状Ｆｅ３Ｃ（パーライト）を分断して球状化、所謂球状化焼鈍されている。これにより、素材が軟化して塑性加工がし易くなり、高精度に仕上げることができる。また、塑性加工により発生した内部応力を減らすために、熱処理による硬化処理の前に、適切な速度で冷却する、所謂応力除去焼きなましが実施されている。これにより、塑性加工により発生した内部応力を減らすことができるため、熱処理による変形を抑えることができると共に、その後の研削加工等の取代を小さくすることができる。さらに、研削等の取代が小さいため、加工性が向上し、また、肉厚確保による強度アップを図ることができる。 Furthermore, in this embodiment, the plate material or pipe material used as a raw material before plastic working is heated at a temperature equal to or lower than the A1 transformation point, and the plate-like Fe 3 C (pearlite) in the structure is divided into spheroids, so-called spheroidization Has been annealed. Thereby, a raw material softens and it becomes easy to carry out plastic working, and it can finish with high precision. In order to reduce the internal stress generated by plastic working, so-called stress-relief annealing, in which cooling is performed at an appropriate rate, is performed before the hardening process by heat treatment. Thereby, since the internal stress generated by the plastic working can be reduced, the deformation due to the heat treatment can be suppressed and the machining allowance for the subsequent grinding or the like can be reduced. Furthermore, since a machining allowance for grinding or the like is small, workability is improved, and strength can be increased by securing a wall thickness.

図７は、本発明に係る車輪用軸受装置の第２の実施形態を示す縦断面図、図８は、図７のＤ部拡大図、図９は、図７のＥ部拡大図である。なお、この実施形態は、前述した実施形態（図１）と基本的には外方部材の構成が一部異なるだけで、その他同一部品同一部位あるいは同様の機能を有する部品や部位には同じ符号を付して詳細な説明を省略する。   FIG. 7 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention, FIG. 8 is an enlarged view of a portion D in FIG. 7, and FIG. 9 is an enlarged view of an portion E in FIG. Note that this embodiment basically differs from the above-described embodiment (FIG. 1) only in that the configuration of the outer member is partially different, and the same reference numerals are used for the same parts and parts having the same functions or the same functions The detailed description is omitted.

この車輪用軸受装置は従動輪側の第３世代構造と呼称され、内方部材１と外方部材２９、および両部材１、２９間に転動自在に収容された複列のボール３、３とを備えている。外方部材２９は、ＳＣｒ４２０やＳＣＭ４１５等の浸炭鋼からなる板材およびパイプ材から塑性加工によって形成され、浸炭焼入れによって表面硬さを５０〜６４ＨＲＣの範囲に硬化処理されている。そして、インナー側の端部に車体取付フランジ３０を一体に有し、内周に径方向内方に突出する環状凸部１４と、この環状凸部１４の両側に複列の円弧状の外側転走面２ａ、２ａが一体に形成されている。また、複列の外側転走面２ａ、２ａの両端部にシール２１、２２の嵌合部となる嵌合部１５、３１が形成されている。   This wheel bearing device is referred to as a third generation structure on the driven wheel side, and includes a double row of balls 3, 3, which are accommodated so as to roll between the inner member 1, the outer member 29, and both members 1, 29. And. The outer member 29 is formed by plastic working from a plate material and pipe material made of carburized steel such as SCr420 and SCM415, and has a surface hardness of 50 to 64 HRC by carburizing and quenching. Then, the vehicle body mounting flange 30 is integrally formed at the inner side end portion, and the annular convex portion 14 projecting radially inwardly on the inner periphery, and the double-row arc-shaped outer roll on both sides of the annular convex portion 14. The running surfaces 2a and 2a are integrally formed. In addition, fitting portions 15 and 31 which are fitting portions of the seals 21 and 22 are formed at both ends of the double row outer rolling surfaces 2a and 2a.

本実施形態では、車体取付フランジ３０は、径方向外方に延出して形成されたフランジ部１７と、このフランジ部１７に一体に接合された別体のパイロット部材３２とで構成されている。また、パイロット部材３２は円板状に形成され、周方向等配に固定ボルト挿通孔１８ａが形成されると共に、ナックルが外嵌されるパイロット部１８ｂが軸方向に延出して形成されている。そして、図８に示すように、フランジ部１７とパイロット部材３２の合せ面がシール２２のアウター側に配置されている。   In the present embodiment, the vehicle body mounting flange 30 includes a flange portion 17 formed to extend radially outward, and a separate pilot member 32 integrally joined to the flange portion 17. Further, the pilot member 32 is formed in a disc shape, a fixing bolt insertion hole 18a is formed in a circumferentially equidistant manner, and a pilot portion 18b into which a knuckle is fitted is formed to extend in the axial direction. As shown in FIG. 8, the mating surface of the flange portion 17 and the pilot member 32 is disposed on the outer side of the seal 22.

パイロット部材３２は、図９に示すように、フランジ部１７に対応する位置の外縁部にインロウ部１９が一体に形成され、フランジ部１７に所定の嵌合すきまを介して外嵌されている。このインロウ部１９によってフランジ部１７とパイロット部材３２とが精度良く一体化される。また、パイロット部材３２の合せ面３３に環状溝３４が形成され、この環状溝３４にＯリング等からなる弾性部材３５が弾性装着されている。これにより、軸受内部に封入されたグリースの外部への漏洩と、外部から雨水やダスト等が軸受内部に侵入するのを防止できると共に、外方部材２９を軸方向に軽量・コンパクト化することができる。なお、ここでは、パイロット部材３２の合せ面３３に環状溝３４が形成されたものを例示したが、これに限らず、図示はしないが、フランジ部１７の合せ面に環状溝が形成され、この環状溝に弾性部材を弾性装着させても良い。   As shown in FIG. 9, the pilot member 32 is integrally formed with an inrow portion 19 at an outer edge portion corresponding to the flange portion 17 and is externally fitted to the flange portion 17 via a predetermined fitting clearance. The flange portion 17 and the pilot member 32 are integrated with high accuracy by the inrow portion 19. An annular groove 34 is formed on the mating surface 33 of the pilot member 32, and an elastic member 35 made of an O-ring or the like is elastically attached to the annular groove 34. As a result, it is possible to prevent the grease enclosed in the bearing from leaking to the outside and prevent rainwater, dust, etc. from entering the bearing from the outside, and to make the outer member 29 lighter and more compact in the axial direction. it can. Here, an example in which the annular groove 34 is formed on the mating surface 33 of the pilot member 32 is illustrated. However, the present invention is not limited to this, but an annular groove is formed on the mating surface of the flange portion 17. An elastic member may be elastically attached to the annular groove.

図１０は、本発明に係る車輪用軸受装置の第３の実施形態を示す縦断面図、図１１は、図１０のＦ部拡大図、図１２は、図１０のＧ部拡大図、図１３は、図１０のハブ輪単体を示す縦断面図、図１４は、図１０の外方部材単体を示す縦断面図である。なお、この実施形態は、前述した実施形態（図１）と基本的にはパイロット部材の接合手段が異なるだけで、その他同一部品同一部位あるいは同様の機能を有する部品や部位には同じ符号を付して詳細な説明を省略する。   10 is a longitudinal sectional view showing a third embodiment of the wheel bearing device according to the present invention, FIG. 11 is an enlarged view of a portion F of FIG. 10, FIG. 12 is an enlarged view of a portion G of FIG. FIG. 14 is a longitudinal sectional view showing a single hub wheel of FIG. 10, and FIG. 14 is a longitudinal sectional view showing a single outer member of FIG. This embodiment basically differs from the above-described embodiment (FIG. 1) only in the means for joining the pilot members, and the same reference numerals are assigned to other parts and parts having the same function or the same function. Therefore, detailed description is omitted.

この車輪用軸受装置は従動輪側の第３世代構造と呼称され、内方部材３６と外方部材３７、および両部材３６、３７間に転動自在に収容された複列のボール３、３とを備えている。内方部材３６は、ハブ輪３８と、このハブ輪３８に所定のシメシロを介して圧入された内輪５とからなる。   This wheel bearing device is called a third-generation structure on the driven wheel side, and includes an inner member 36 and an outer member 37, and double-row balls 3, 3 accommodated so as to roll between both members 36, 37. And. The inner member 36 includes a hub ring 38 and an inner ring 5 that is press-fitted into the hub ring 38 through a predetermined shimiro.

ハブ輪３８は、アウター側の端部に車輪取付フランジ３９を一体に有し、外周に一方の円弧状の内側転走面４ａと、この内側転走面４ａから肩部４ｂを介して軸方向に延びる円筒状の小径段部４ｃが形成されている。車輪取付フランジ３９は、径方向外方に延出して形成されたフランジ部４０と、このフランジ部４０に一体に接合された別体のパイロット部材４１とで構成されている。   The hub wheel 38 integrally has a wheel mounting flange 39 at an end portion on the outer side, one arc-shaped inner rolling surface 4a on the outer periphery, and an axial direction from the inner rolling surface 4a via a shoulder portion 4b. A cylindrical small-diameter step portion 4c extending in the direction is formed. The wheel mounting flange 39 includes a flange portion 40 that is formed to extend radially outward, and a separate pilot member 41 that is integrally joined to the flange portion 40.

フランジ部４０は、環状の基部７ａから放射状に延び、ハブボルト挿通孔７ｂの近傍を除く部分を切欠いて５つに分割されて形成されている。一方、パイロット部材４１は円板状に形成され、周方向等配にハブボルト挿通孔８ｂが形成されると共に、車輪およびブレーキロータ（図示せず）をガイドするパイロット部８ｃが軸方向に延出して形成されている。   The flange portion 40 extends radially from the annular base portion 7a, and is formed by dividing the portion except for the vicinity of the hub bolt insertion hole 7b into five parts. On the other hand, the pilot member 41 is formed in a disk shape, and hub bolt insertion holes 8b are formed in a circumferentially uniform manner, and a pilot portion 8c that guides a wheel and a brake rotor (not shown) extends in the axial direction. Is formed.

本実施形態では、図１１に拡大して示すように、フランジ部４０とパイロット部材４１には貫通孔４０ａ、４１ａが打ち抜き加工によって穿設され、これら貫通孔４０ａ、４１ａに連結ピン４２が圧入されている。この連結ピン４２によってフランジ部４０とパイロット部材４１とを強固に一体化することができ、ハブ輪３８の強度・剛性を高めて耐久性を向上させることができる。   In the present embodiment, as shown in an enlarged view in FIG. 11, through holes 40a and 41a are formed by punching in the flange portion 40 and the pilot member 41, and a connecting pin 42 is press-fitted into these through holes 40a and 41a. ing. The flange portion 40 and the pilot member 41 can be firmly integrated by the connecting pin 42, and the strength and rigidity of the hub wheel 38 can be increased and the durability can be improved.

外方部材３７は、インナー側の端部に車体取付フランジ４３を一体に有し、内周に径方向内方に突出する環状凸部１４と、この環状凸部１４の両側に複列の円弧状の外側転走面２ａ、２ａが一体に形成されている。   The outer member 37 has a vehicle body mounting flange 43 integrally at the end on the inner side, an annular convex portion 14 projecting radially inward on the inner periphery, and double-row circles on both sides of the annular convex portion 14. Arc-shaped outer rolling surfaces 2a and 2a are integrally formed.

車体取付フランジ４３は、径方向外方に延出して形成されたフランジ部４４と、このフランジ部４４に一体に接合された別体のパイロット部材４５とで構成されている。フランジ部４４は、環状の基部４４ａから放射状に延び、固定ボルト挿通孔１７ｂの近傍を除く部分を切欠いて４つに分割されて形成されている。一方、パイロット部材４５は円板状に形成され、周方向等配に固定ボルト挿通孔１８ａが形成されると共に、ナックル（図示せず）が外嵌されるパイロット部１８ｂが軸方向に延出して形成されている。   The vehicle body mounting flange 43 includes a flange portion 44 that extends outward in the radial direction, and a separate pilot member 45 that is integrally joined to the flange portion 44. The flange portion 44 extends radially from the annular base portion 44a, and is divided into four parts by cutting out a portion excluding the vicinity of the fixing bolt insertion hole 17b. On the other hand, the pilot member 45 is formed in a disc shape, the fixing bolt insertion holes 18a are formed in a circumferentially uniform manner, and the pilot portion 18b in which a knuckle (not shown) is fitted is extended in the axial direction. Is formed.

本実施形態では、図１２に拡大して示すように、フランジ部４４とパイロット部材４５には貫通孔４４ａ、４５ａが穿設され、これら貫通孔４４ａ、４５ａに連結ピン４６が圧入されている。この連結ピン４６によってフランジ部４４とパイロット部材４５とを強固に一体化することができ、外方部材３７の強度・剛性を高めて耐久性を向上させることができる。   In the present embodiment, as shown in an enlarged view in FIG. 12, through holes 44a and 45a are formed in the flange portion 44 and the pilot member 45, and a connecting pin 46 is press-fitted into the through holes 44a and 45a. With this connecting pin 46, the flange portion 44 and the pilot member 45 can be firmly integrated, and the strength and rigidity of the outer member 37 can be increased and the durability can be improved.

ハブ輪３８は、図１３に示すように、Ｓ４５Ｃ等の炭素鋼からなる板材またはパイプ材から塑性加工によって形成されている。具体的には、ハブ輪３８の本体部分は、パイプ材からプレス加工および冷間のローリング加工によって形成され、パイロット部材４１は、板材からプレス加工によって形成されている。また、塑性加工でバリが発生する両端面は加工後に旋削加工されるか、必要に応じて研削加工が施される。そして、内側転走面４ａをはじめアウター側のシールランド部となる基部７ａから小径段部４ｃに亙って高周波焼入れによって表面硬さを５０〜６４ＨＲＣの範囲に硬化処理が施される。なお、加締部４ｄは素材硬さの生のままとされている。さらに、内側転走面４ａが、研削加工によって所定の寸法、精度に形成されている。その後、必要に応じて超仕上げ加工が施される。これにより、フランジ部４０に負荷される回転曲げ荷重に対して充分な機械的強度を有し、小径段部４ｃの耐フレッティング性が向上してハブ輪３８の耐久性が一段と向上すると共に、微小なクラック等の発生がなく加締部４ｄの塑性加工をスムーズに行うことができる。   As shown in FIG. 13, the hub wheel 38 is formed by plastic working from a plate material or pipe material made of carbon steel such as S45C. Specifically, the main body portion of the hub wheel 38 is formed from a pipe material by pressing and cold rolling, and the pilot member 41 is formed from a plate material by pressing. Further, both end faces where burrs are generated by plastic working are turned after the machining, or are ground if necessary. Then, the surface hardness is set in the range of 50 to 64 HRC by induction hardening from the inner rolling surface 4a to the small-diameter step portion 4c from the base portion 7a serving as the outer seal land portion. Note that the caulking portion 4d is kept as raw material hardness. Furthermore, the inner rolling surface 4a is formed with predetermined dimensions and accuracy by grinding. Thereafter, superfinishing is performed as necessary. Thereby, it has sufficient mechanical strength against the rotational bending load applied to the flange portion 40, the fretting resistance of the small diameter step portion 4c is improved, and the durability of the hub wheel 38 is further improved. There is no occurrence of minute cracks and the like, and the plastic working of the crimped portion 4d can be performed smoothly.

外方部材３７は、図１４に示すように、Ｓ４５Ｃ等の炭素鋼からなる板材またはパイプ材から塑性加工によって形成されている。具体的には、外方部材３７の本体部分は、パイプ材からプレス加工および冷間のローリング加工によって形成され、パイロット部材４５は板材からプレス加工によって形成されている。そして、少なくとも外方部材３７の複列の外側転走面２ａ、２ａが高周波焼入れによって表面硬さを５０〜６４ＨＲＣの範囲に硬化処理が施されている。そして、複列の外側転走面２ａ、２ａが、研削加工によって所定の寸法、精度に形成されている。なお、その後、必要に応じて超仕上げ加工が施される。   As shown in FIG. 14, the outer member 37 is formed by plastic working from a plate material or pipe material made of carbon steel such as S45C. Specifically, the main body portion of the outer member 37 is formed from a pipe material by pressing and cold rolling, and the pilot member 45 is formed from a plate material by pressing. Then, at least the double row outer rolling surfaces 2a, 2a of the outer member 37 are subjected to a hardening process in a range of 50 to 64 HRC by induction hardening. The double row outer rolling surfaces 2a, 2a are formed with predetermined dimensions and accuracy by grinding. After that, superfinishing is performed as necessary.

図１５は、本発明に係る車輪用軸受装置の参考例を示す縦断面図である。なお、この実施形態は、前述した実施形態（図１）と基本的には外方部材の構成が異なるだけで、その他同一部品同一部位あるいは同様の機能を有する部品や部位には同じ符号を付して詳細な説明を省略する。 FIG. 15 is a longitudinal sectional view showing a reference example of the wheel bearing device according to the present invention. This embodiment basically differs from the above-described embodiment (FIG. 1) only in the configuration of the outer member, and the same reference numerals are assigned to the same parts or parts having the same function. Therefore, detailed description is omitted.

この車輪用軸受装置は、内方部材１と、図示しないナックルに圧入固定される外方部材４６、および両部材１、４６間に転動自在に収容された複列のボール３、３とを備えている。外方部材４６は、ＳＣｒ４２０やＳＣＭ４１５等の浸炭鋼からなるパイプ材から塑性加工によって形成され、内周に径方向内方に突出する環状凸部１４と、この環状凸部１４の両側に複列の円弧状の外側転走面２ａ、２ａが一体に形成されている。そして、複列の外側転走面２ａ、２ａの両端部にシール２１、２２の嵌合部１５、１６が形成され、浸炭焼入れによって表面硬さを５０〜６４ＨＲＣの範囲に硬化処理されている。   This wheel bearing device includes an inner member 1, an outer member 46 that is press-fitted and fixed to a knuckle (not shown), and double-row balls 3 and 3 that are accommodated so as to roll between both members 1 and 46. I have. The outer member 46 is formed by plastic working from a pipe material made of carburized steel such as SCr420 and SCM415, and has an annular protrusion 14 projecting radially inward on the inner periphery, and double rows on both sides of the annular protrusion 14. Arc-shaped outer rolling surfaces 2a and 2a are integrally formed. And the fitting parts 15 and 16 of the seals 21 and 22 are formed in the both ends of the double row outer side rolling surfaces 2a and 2a, and the surface hardness is hardened in the range of 50-64 HRC by carburizing and quenching.

本実施形態では、複列の外側転走面２ａ、２ａをはじめ、この嵌合部１５、１６は、塑性加工後に研削加工によって所定の寸法、精度に形成される。これにより、従来の軸受と同等の精度や密封性を確保することができる。なお、塑性加工でバリが発生する両端面は加工後に旋削加工される。また、必要に応じて研削加工が施される。   In the present embodiment, the fitting portions 15 and 16 including the double row outer rolling surfaces 2a and 2a are formed with predetermined dimensions and accuracy by grinding after plastic working. Thereby, the precision and sealing performance equivalent to the conventional bearing can be ensured. Note that both end surfaces where burrs are generated by plastic working are turned after machining. Moreover, a grinding process is given as needed.

ここで、外側転走面２ａから環状凸部１４の肩高さを適切に確保するために、外方部材４６の塑性加工時、環状凸部１４の内径をフラット形状に形成すると共に、外方部材４６の軸方向中央部を凹ませて環状凹部４７を形成し肩部１４ａに素材を充足させるようにしている。   Here, in order to appropriately secure the shoulder height of the annular convex portion 14 from the outer rolling surface 2a, the inner diameter of the annular convex portion 14 is formed in a flat shape during plastic processing of the outer member 46, and the outer side The central portion of the member 46 in the axial direction is recessed to form an annular recess 47 to fill the shoulder 14a with the material.

そして、外方部材４６の外径と環状凹部４７との繋ぎ部４７ａの曲率半径Ｒが所定の範囲になるように設定されている。具体的には、ボール３の半径をＲｗとした時、この曲率半径Ｒは、Ｒ＝１．５〜２．５Ｒｗの範囲になるように設定されている。これにより、この部位の肉厚が略均等に形成できると共に、肩部１４ａに亀裂が発生するのを防止し、かつ、旋回モーメント負荷時にボール３の接触楕円が肩部１４ａを乗り上げてエッジロードが発生するのを防止することができる適切な肩高さを確保することができ、軸受の耐久性を向上させることができる。ここで、略均等とは、成形前のパイプ材の肉厚が均等であり、繋ぎ部４７ａも円弧を形成する目的以外に特に塑性流動させることなく成形を行った結果得られた形状の肉厚の状態を意味し、繋ぎ部４７ａの円弧を形成する際の材料の肉の変位により僅かに肉薄となったり肉厚となる状態は含むことを意味する。   The radius of curvature R of the connecting portion 47a between the outer diameter of the outer member 46 and the annular recess 47 is set within a predetermined range. Specifically, when the radius of the ball 3 is Rw, the radius of curvature R is set to be in a range of R = 1.5 to 2.5Rw. As a result, the thickness of this portion can be formed substantially evenly, and the shoulder portion 14a can be prevented from cracking, and the contact ellipse of the ball 3 rides on the shoulder portion 14a when a turning moment is applied, and the edge load is reduced. An appropriate shoulder height that can be prevented from occurring can be secured, and the durability of the bearing can be improved. Here, “substantially equal” means that the thickness of the pipe material before molding is uniform, and the thickness of the shape obtained as a result of molding without any plastic flow especially for the purpose of forming the connecting portion 47a other than the purpose of forming an arc. This means that a state in which the thickness of the connecting portion 47a is slightly reduced or increased due to the displacement of the thickness of the material when forming the arc of the connecting portion 47a is included.

繋ぎ部４７ａの曲率半径Ｒがボール３の半径Ｒｗの１．５倍より小さい場合、肉厚が薄くなり剛性が低下して旋回モーメント負荷時の応力に耐えられず、また、ボール３の半径Ｒｗの２．５倍を超えた場合、肉厚が厚くなり塑性加工の加工性が低下するだけでなく、従来の鍛造成形品と大差ない形状となって軽量・コンパクト化に総じて寄与しなくなるためである。   When the radius of curvature R of the connecting portion 47a is smaller than 1.5 times the radius Rw of the ball 3, the wall thickness becomes thin and the rigidity is lowered, so that it cannot withstand the stress at the time of turning moment load. If it exceeds 2.5 times the thickness, not only will the wall thickness increase and the workability of plastic working will decrease, but the shape will not greatly differ from conventional forged products, and it will not contribute to light weight and compactness in general. is there.

図１６は、本発明に係る車輪用軸受装置の第４の実施形態を示す縦断面図である。なお、この実施形態は、前述した第１の実施形態（図１）と基本的にはエンドキャップの有無が一部異なるだけで、その他同一部品同一部位あるいは同様の機能を有する部品や部位には同じ符号を付して詳細な説明を省略する。 FIG. 16 is a longitudinal sectional view showing a fourth embodiment of the wheel bearing device according to the present invention. This embodiment is basically different from the first embodiment (FIG. 1) described above except for the presence or absence of an end cap. For other parts and parts having the same function or similar functions, The same reference numerals are assigned and detailed description is omitted.

この車輪用軸受装置は従動輪側の第３世代構造と呼称され、内方部材１’と外方部材２、および両部材１’、２間に転動自在に収容された複列のボール３、３とを備えている。内方部材１’は、ハブ輪４と、このハブ輪４に所定のシメシロを介して圧入された内輪５とからなる。   This wheel bearing device is referred to as a third generation structure on the driven wheel side, and is composed of a double row of balls 3 accommodated in a freely rolling manner between the inner member 1 ′, the outer member 2, and both members 1 ′, 2. 3 are provided. The inner member 1 ′ includes a hub ring 4 and an inner ring 5 that is press-fitted into the hub ring 4 through a predetermined scissors.

ここで、本実施形態では、ハブ輪４の両端開口部にエンドキャップ４８、４９が装着されている。これらのエンドキャップ４８、４９は、防錆能を有する鋼鈑、例えば、オーステナイト系ステンレス鋼鈑（ＪＩＳ規格のＳＵＳ３０４系等）や防錆処理された冷間圧延鋼鈑（ＪＩＳ規格のＳＰＣＣ系等）をプレス加工にて断面が略コの字状に形成されている。アウター側の開口部に装着されたエンドキャップ４８は、ハブ輪４のパイロット部材８におけるパイロット部８ｃに内嵌される円筒部４８ａと、この円筒部４８ａのアウター側の端部から径方向内方に延びる底部４８ｂとからなる。一方、インナー側の開口部に装着されたエンドキャップ４９は、ハブ輪４の小径段部４ｃに内嵌される円筒部４９ａと、この円筒部４９ａのインナー側の端部から径方向内方に延びる底部４９ｂとからなる。   Here, in the present embodiment, end caps 48 and 49 are attached to both end openings of the hub wheel 4. These end caps 48 and 49 are rust preventive steel plates, such as austenitic stainless steel plates (JIS standard SUS304, etc.) and rust-proof cold rolled steel plates (JIS standard SPCC, etc.) ) Is formed by pressing to have a substantially U-shaped cross section. The end cap 48 attached to the opening on the outer side includes a cylindrical portion 48a fitted into the pilot portion 8c of the pilot member 8 of the hub wheel 4, and a radially inner portion from the outer end portion of the cylindrical portion 48a. And a bottom portion 48b extending to the bottom. On the other hand, the end cap 49 attached to the opening on the inner side has a cylindrical portion 49a fitted into the small-diameter step portion 4c of the hub wheel 4 and radially inward from the inner side end of the cylindrical portion 49a. The bottom portion 49b extends.

このように、ハブ輪４の両端開口部がエンドキャップ４８、４９によって閉塞されているので、外部から雨水やダスト等が中空のハブ輪４の内部に侵入するのを防止でき、発錆するのを防止して耐久性を向上させることができる。なお、これらエンドキャップ４８、４９の少なくとも外部の露出した表面にＮＢＲ等の合成ゴムを被着させることにより、発錆をさらに防止することができると共に、高価なステンレス鋼鈑を使用することなく廉価で加工性が良好な冷間圧延鋼鈑を使用することができ、低コスト化を図ることができる。   As described above, since the opening portions at both ends of the hub wheel 4 are closed by the end caps 48 and 49, rainwater, dust and the like can be prevented from entering the hollow hub wheel 4 from the outside, and rusting occurs. Can be prevented and durability can be improved. In addition, by attaching a synthetic rubber such as NBR to at least the externally exposed surfaces of these end caps 48 and 49, it is possible to further prevent rusting and at a low price without using an expensive stainless steel plate. Therefore, it is possible to use a cold-rolled steel plate with good workability, and to reduce the cost.

図１７は、本発明に係る車輪用軸受装置の第５の実施形態を示す縦断面図である。なお、この実施形態は、前述した第１の実施形態（図１）と基本的にはハブ輪と外方部材の構成が一部異なるだけで、その他同一部品同一部位あるいは同様の機能を有する部品や部位には同じ符号を付して詳細な説明を省略する。 FIG. 17 is a longitudinal sectional view showing a fifth embodiment of the wheel bearing device according to the present invention. This embodiment is basically the same as the first embodiment (FIG. 1) described above except that the configuration of the hub wheel and the outer member is only partially different, and other parts having the same parts or similar functions. The same reference numerals are given to the parts and the detailed description is omitted.

この車輪用軸受装置は従動輪側の第３世代構造で、内方部材１”と外方部材２’、および両部材１”、２’間に転動自在に収容された複列のボール３、３とを備えている。内方部材１”は、ハブ輪４’と、このハブ輪４’に所定のシメシロを介して圧入された内輪５とからなる。   This wheel bearing device has a third generation structure on the driven wheel side, and includes an inner member 1 ″ and an outer member 2 ′, and a double row of balls 3 accommodated so as to roll between the members 1 ″ and 2 ′. 3 are provided. The inward member 1 ″ is composed of a hub ring 4 ′ and an inner ring 5 press-fitted into the hub ring 4 ′ via a predetermined scissors.

ハブ輪４’は、アウター側の端部に車輪取付フランジ６’を一体に有し、外周に一方（アウター側）の円弧状の内側転走面４ａと、この内側転走面４ａから肩部４ｂを介して軸方向に延びる円筒状の小径段部４ｃが形成されている。車輪取付フランジ６’は、径方向外方に延出して形成されたフランジ部７と、このフランジ部７に一体に接合された別体のパイロット部材８’とで構成されている。   The hub wheel 4 ′ has a wheel mounting flange 6 ′ integrally at the outer end portion, one (outer side) arcuate inner rolling surface 4 a on the outer periphery, and a shoulder portion from the inner rolling surface 4 a. A cylindrical small diameter step portion 4c extending in the axial direction through 4b is formed. The wheel mounting flange 6 ′ includes a flange portion 7 that is formed to extend radially outward, and a separate pilot member 8 ′ that is integrally joined to the flange portion 7.

ここで、本実施形態では、パイロット部材８’はカップ状に形成され、周方向等配にハブボルト挿通孔８ｂが形成されると共に、パイロット部８ｃから径方向内方に延びる底部８ｄが一体に形成されている。   Here, in the present embodiment, the pilot member 8 ′ is formed in a cup shape, the hub bolt insertion holes 8b are formed in a circumferentially uniform manner, and the bottom portion 8d extending radially inward from the pilot portion 8c is integrally formed. Has been.

また、外方部材２’は、インナー側の端部に車体取付フランジ１３’を一体に有し、内周に径方向内方に突出する環状凸部１４と、この環状凸部１４の両側に複列の円弧状の外側転走面２ａ、２ａが一体に形成されている。車体取付フランジ１３’は、径方向外方に延出して形成されたフランジ部１７と、このフランジ部１７に一体に接合された別体のパイロット部材１８’とで構成されている。そして、パイロット部材１８’はカップ状に形成され、周方向等配に固定ボルト挿通孔１８ａが打ち抜き加工によって形成されると共に、パイロット部１８ｂから径方向内方に延びる底部１８ｃが一体に形成されている。   Further, the outer member 2 ′ has a vehicle body mounting flange 13 ′ integrally at the end on the inner side, an annular protrusion 14 protruding radially inward on the inner periphery, and both sides of the annular protrusion 14. Double-row arc-shaped outer rolling surfaces 2a and 2a are integrally formed. The vehicle body mounting flange 13 ′ includes a flange portion 17 formed to extend outward in the radial direction, and a separate pilot member 18 ′ integrally joined to the flange portion 17. The pilot member 18 ′ is formed in a cup shape, the fixing bolt insertion holes 18 a are formed in a circumferentially uniform manner by punching, and the bottom portion 18 c extending inward in the radial direction from the pilot portion 18 b is integrally formed. Yes.

このように、本実施形態では、ハブ輪４’を構成する別体のパイロット部材８’と外方部材２’を構成する別体のパイロット部材１８’がカップ状に形成され、ハブ輪４’の両端開口部が閉塞されているので、外部から雨水やダスト等が中空のハブ輪４’の内部に侵入するのを防止でき、発錆するのを防止して耐久性を向上させることができる。   Thus, in the present embodiment, the separate pilot member 8 ′ constituting the hub wheel 4 ′ and the separate pilot member 18 ′ constituting the outer member 2 ′ are formed in a cup shape, and the hub wheel 4 ′. Since the opening portions at both ends are closed, it is possible to prevent rainwater, dust and the like from entering the inside of the hollow hub wheel 4 ′ from the outside, to prevent rusting and to improve durability. .

以上、本発明の実施の形態について説明を行ったが、本発明はこうした実施の形態に何等限定されるものではなく、あくまで例示であって、本発明の要旨を逸脱しない範囲内において、さらに種々なる形態で実施し得ることは勿論のことであり、本発明の範囲は、特許請求の範囲の記載によって示され、さらに特許請求の範囲に記載の均等の意味、および範囲内のすべての変更を含む。   The embodiment of the present invention has been described above, but the present invention is not limited to such an embodiment, and is merely an example, and various modifications can be made without departing from the scope of the present invention. Of course, the scope of the present invention is indicated by the description of the scope of claims, and further, the equivalent meanings described in the scope of claims and all modifications within the scope of the scope of the present invention are included. Including.

本発明に係る車輪用軸受装置は、車輪取付フランジを一体に有するハブ輪と、このハブ輪に圧入される内輪とからなる内方部材を備えた車輪用軸受装置に適用できる。   The wheel bearing device according to the present invention can be applied to a wheel bearing device including an inner member including a hub ring integrally having a wheel mounting flange and an inner ring press-fitted into the hub ring.

１、１’、１”、３６ 内方部材
２、２’、２９、３７、４６ 外方部材
２ａ 外側転走面
３ ボール
４、４’、３８ ハブ輪
４ａ、５ａ 内側転走面
４ｂ、１０、１４ａ 肩部
４ｃ 小径段部
４ｄ 加締部
５ 内輪
６、６’、３９ 車輪取付フランジ
６ａ ハブボルト
７、１７、４０、４４ フランジ部
７ａ、１７ａ 基部
７ｂ、８ｂ ハブボルト挿通孔
８、８’、１８、１８’、３２、４１、４５ パイロット部材
８ａ 円孔
８ｂ ハブボルト挿通孔
８ｃ、１８ｂ パイロット部
８ｄ、１８ｃ、４８ｂ、４９ｂ 底部
９、１９ インロウ部
１１ 大端部
１２ 小端部
１３、１３’、３０、４３ 車体取付フランジ
１４ 環状凸部
１５、１６、３１ 嵌合部
１７ｂ、１８ａ 固定ボルト挿通孔
２０ 保持器
２１ アウター側のシール
２２ インナー側のシール
２３、２７ 芯金
２４、２８ シール部材
２４ａ、２８ａ サイドリップ
２４ｂ、２８ｃ ダストリップ
２４ｃ、２８ｂ グリースリップ
２５ シール板
２６ スリンガ
２６ａ、４８ａ、４９ａ 円筒部
２６ｂ 立板部
３３ 合せ面
３４ 環状溝
３５ 弾性部材
４０ａ、４１ａ、４４ａ、４５ａ 貫通孔
４２、４６ 連結ピン
４７ 環状凹部
４７ａ 繋ぎ部
４８、４９ エンドキャップ
５０ 車輪用軸受装置
５１ ハブ輪
５１ａ、５８ａ 内側転走面
５２ 複列アンギュラ玉軸受
５３ 軸部
５３ａ 小径段部
５４、６１ 切り起し片
５５、６２ 舌片
５５ａ 膨出部
５６ ハブボルト
５７ 外方部材
５７ａ 外側転走面
５８ 内輪
５９ 保持器
６０ ボール
Ｒｗ ボールの半径
Ｒ 繋ぎ部の曲率半径 1, 1 ', 1 ", 36 Inner member 2, 2', 29, 37, 46 Outer member 2a Outer rolling surface 3 Balls 4, 4 ', 38 Hub wheel 4a, 5a Inner rolling surface 4b, 10 14a Shoulder portion 4c Small diameter step portion 4d Clamping portion 5 Inner ring 6, 6 ', 39 Wheel mounting flange 6a Hub bolt 7, 17, 40, 44 Flange portion 7a, 17a Base portion 7b, 8b Hub bolt insertion hole 8, 8', 18 , 18 ', 32, 41, 45 Pilot member 8a Circular hole 8b Hub bolt insertion hole 8c, 18b Pilot part 8d, 18c, 48b, 49b Bottom part 9, 19 Inner part 11 Large end part 12 Small end part 13, 13', 30 , 43 Car body mounting flange 14 Annular convex portions 15, 16, 31 Fitting portions 17b, 18a Fixing bolt insertion hole 20 Retainer 21 Outer side seal 22 Inner side seal 23, 27 Core metal 24, 28 Seal Material 24a, 28a Side lip 24b, 28c Dustrip 24c, 28b Grease lip 25 Seal plate 26 Slinger 26a, 48a, 49a Cylindrical portion 26b Standing plate portion 33 Matching surface 34 Annular groove 35 Elastic members 40a, 41a, 44a, 45a Through hole 42, 46 Connecting pin 47 Annular recess 47a Connecting portion 48, 49 End cap 50 Wheel bearing device 51 Hub wheel 51a, 58a Inner rolling surface 52 Double row angular contact ball bearing 53 Shaft portion 53a Small diameter step portion 54, 61 Pieces 55, 62 tongue piece 55a bulging portion 56 hub bolt 57 outer member 57a outer rolling surface 58 inner ring 59 cage 60 ball Rw radius of ball R radius of curvature of joint

Claims (16)

内周に複列の円弧状の外側転走面が一体に形成された外方部材と、
アウター側の端部に車輪を取り付けるための車輪取付フランジを一体に有し、外周に前記複列の転走面の一方に対向する円弧状の内側転走面と、この内側転走面から軸方向に延びる円筒状の小径段部が形成されたハブ輪、およびこのハブ輪の小径段部に所定のシメシロを介して圧入され、外周に前記複列の外側転走面の他方に対向する円弧状の内側転走面が形成された内輪からなる内方部材と、
この内方部材と前記外方部材の両転走面間に保持器を介して転動自在に収容された複列のボールと、
前記外方部材と内方部材との間に形成された環状空間の開口部に装着されたシールとを備え、
前記小径段部の端部を径方向外方に塑性変形させて形成した加締部によって、前記ハブ輪に対して前記内輪が軸方向に固定された車輪用軸受装置において、
前記ハブ輪が板材またはパイプ材から塑性加工によって形成され、前記車輪取付フランジが、径方向外方に延出して形成されたフランジ部と、円板状に形成され、前記車輪およびブレーキロータをガイドするパイロット部が軸方向に延出して形成された別体のパイロット部材とで構成されると共に、
前記フランジ部とパイロット部材の周方向等配にボルト挿通孔が形成され、これらボルト挿通孔にハブボルトが圧入されて前記パイロット部材が前記フランジ部に一体に接合され、かつ、前記外方部材が板材またはパイプ材から塑性加工によって形成され、インナー側の端部にナックルに取り付けられるための車体取付フランジを一体に有し、この車体取付フランジが、径方向外方に延出して形成されたフランジ部と、円板状に形成され、前記ナックルに内嵌されるパイロット部が軸方向に延出して形成された別体のパイロット部材とで構成され、前記フランジ部とパイロット部材の周方向等配にボルト挿通孔が形成されていることを特徴とする車輪用軸受装置。 An outer member in which a double-row arc-shaped outer rolling surface is integrally formed on the inner periphery;
A wheel mounting flange for mounting the wheel on the outer end is integrated, and an arcuate inner rolling surface facing one of the double row rolling surfaces on the outer periphery, and an axis extending from the inner rolling surface. A hub wheel formed with a cylindrical small-diameter step portion extending in the direction, and a circle that is press-fitted into the small-diameter step portion of the hub wheel through a predetermined shimoshiro and that opposes the other of the double-row outer rolling surfaces on the outer periphery An inner member composed of an inner ring formed with an arc-shaped inner rolling surface;
A double row of balls accommodated between the rolling surfaces of the inner member and the outer member via a retainer between the rolling surfaces;
A seal attached to an opening of an annular space formed between the outer member and the inner member;
In the wheel bearing device in which the inner ring is fixed in the axial direction with respect to the hub wheel by a crimping portion formed by plastically deforming an end portion of the small-diameter stepped portion radially outwardly,
The hub wheel is formed by plastic working from a plate material or a pipe material, and the wheel mounting flange is formed in a disk shape with a flange portion formed to extend radially outward, and guides the wheel and the brake rotor. And a separate pilot member formed to extend in the axial direction, and
Bolt insertion holes are formed at equal intervals in the circumferential direction of the flange portion and the pilot member, hub bolts are press-fitted into the bolt insertion holes, the pilot member is integrally joined to the flange portion , and the outer member is a plate material Alternatively, it is formed from a pipe material by plastic working, and has a body mounting flange integrally attached to the knuckle at the end on the inner side, and this body mounting flange is formed by extending radially outward. And a separate pilot member formed in the shape of a disk and fitted in the knuckle to extend in the axial direction. A wheel bearing device in which a bolt insertion hole is formed . 前記フランジ部とパイロット部材の合せ面が前記インナー側のシールのアウター側に配置されると共に、前記フランジ部とパイロット部材の合せ面のうちどちらか一方の合せ面に環状溝が形成され、この環状溝に弾性部材が装着されている請求項１に記載の車輪用軸受装置。 The mating surface of the flange portion and the pilot member is disposed on the outer side of the inner seal, and an annular groove is formed on one of the mating surfaces of the flange portion and the pilot member. a bearing device for a wheel according to claim 1 in which the elastic member is mounted in the groove. 前記外方部材の外径の軸方向中央部を凹ませて環状凹部が形成され、内周に環状凸部がフラット形状に形成されると共に、前記外径と環状凹部の繋ぎ部が所定の曲率半径からなる円弧状に形成され、この部位が略均等な肉厚に設定されている請求項１に記載の車輪用軸受装置。 An annular recess is formed by denting the axially central portion of the outer diameter of the outer member, the annular protrusion is formed in a flat shape on the inner periphery, and the joint between the outer diameter and the annular recess has a predetermined curvature. The wheel bearing device according to claim 1 , wherein the wheel bearing device is formed in a circular arc shape having a radius, and the portion is set to have a substantially uniform thickness. 前記繋ぎ部の曲率半径Ｒが、前記ボールの半径をＲｗとした時、Ｒ＝１．５〜２．５Ｒｗの範囲になるように設定されている請求項３に記載の車輪用軸受装置。 4. The wheel bearing device according to claim 3 , wherein a radius of curvature R of the joint portion is set to be in a range of R = 1.5 to 2.5 Rw, where Rw is a radius of the ball. 5. 前記フランジ部が環状の基部から放射状に延び、前記ボルト挿通孔の近傍を除く部分を切欠いて４〜６つに分割されて形成されている請求項１に記載の車輪用軸受装置。 2. The wheel bearing device according to claim 1 , wherein the flange portion extends radially from an annular base portion, and is divided into four to six portions by cutting out a portion excluding the vicinity of the bolt insertion hole. 前記パイロット部材の前記フランジ部に対応する位置の外縁部にインロウ部が一体に形成され、当該フランジ部に所定の嵌合すきまを介して外嵌されている請求項１または２に記載の車輪用軸受装置。 The wheel part according to claim 1 or 2 , wherein an in-row part is integrally formed at an outer edge part of the pilot member at a position corresponding to the flange part, and is fitted onto the flange part via a predetermined fitting clearance. Bearing device. 前記インロウ部が前記フランジ部の外縁部の形状に沿った円弧状に形成されている請求項６に記載の車輪用軸受装置。 The wheel bearing device according to claim 6 , wherein the inrow portion is formed in an arc shape along a shape of an outer edge portion of the flange portion. 前記フランジ部とパイロット部材に貫通孔が打ち抜き加工によって穿設され、これら貫通孔に連結ピンが圧入されている請求項１、２、６、７いずれかに記載の車輪用軸受装置。 The wheel bearing device according to claim 1, wherein through holes are formed in the flange portion and the pilot member by punching, and connection pins are press-fitted into the through holes. 前記内輪が板材またはパイプ材から塑性加工によって形成され、前記内側転走面の大径側から軸方向に延び、前記インナー側のシールの嵌合部または摺接部となる円筒状の肩部と、この肩部から径方向内方に屈曲して形成された大端部、および前記内側転走面の小径側から軸方向に延びる円筒状の小端部を備え、この小端部が前記ハブ輪の肩部に突合せ状態で前記小径段部に圧入されると共に、当該内輪が前記加締部によって所定の軸受予圧が付与された状態で軸方向に固定されている請求項１に記載の車輪用軸受装置。 The inner ring is formed by plastic working from a plate material or a pipe material, extends in the axial direction from the large diameter side of the inner rolling surface, and a cylindrical shoulder portion serving as a fitting portion or a sliding contact portion of the inner side seal; A large end formed by bending inward in the radial direction from the shoulder, and a cylindrical small end extending in the axial direction from the small diameter side of the inner rolling surface, the small end being the hub while being pressed in a state abutting the shoulder of the ring to the cylindrical portion, the wheel of claim 1 in which a predetermined bearing preload the inner ring by the caulked portion is fixed in the axial direction while being granted Bearing device. 前記板材またはパイプ材が、塑性加工前にＡ１変態点以下の温度で加熱され、組織の板状のパーライトを分断して球状化焼鈍されている請求項１または９に記載の車輪用軸受装置。 10. The wheel bearing device according to claim 1, wherein the plate member or the pipe member is heated at a temperature equal to or lower than the A1 transformation point before plastic working, and the plate-like pearlite of the structure is divided and spheroidized and annealed. 前記ハブ輪が、熱処理前に所定の温度へ加熱または均熱した後、所定の速度で冷却する応力除去焼きなましが実施されている請求項１または９に記載の車輪用軸受装置。 The wheel bearing device according to claim 1 or 9, wherein the hub wheel is subjected to stress relief annealing in which the hub wheel is heated or soaked to a predetermined temperature before heat treatment and then cooled at a predetermined speed. 前記ハブ輪の少なくともアウター側の端部が閉塞されている請求項１、９、１１いずれかに記載の車輪用軸受装置。 The wheel bearing device according to any one of claims 1, 9, and 11, wherein at least an outer end portion of the hub wheel is closed. 前記ハブ輪のパイロット部材のパイロット部に、防錆能を有する鋼鈑からプレス加工によって形成されたエンドキャップが内嵌されている請求項１２に記載の車輪用軸受装置。 The wheel bearing device according to claim 12 , wherein an end cap formed by press working from a steel plate having antirust performance is fitted into a pilot portion of a pilot member of the hub wheel . 前記エンドキャップの少なくとも外部の露出した表面に合成ゴムが被着されている請求項１３に記載の車輪用軸受装置。 The wheel bearing device according to claim 13 , wherein a synthetic rubber is attached to at least an exposed surface of the end cap. 前記ハブ輪のパイロット部材がカップ状に形成され、前記パイロット部から径方向内方に延びる底部が一体に形成されている請求項１２に記載の車輪用軸受装置。 The wheel bearing device according to claim 12 , wherein a pilot member of the hub wheel is formed in a cup shape, and a bottom portion extending radially inward from the pilot portion is integrally formed. 前記外方部材のパイロット部材がカップ状に形成され、前記パイロット部から径方向内方に延びる底部が一体に形成されている請求項１に記載の車輪用軸受装置。 Pilot member of the outer member is formed into a cup shape, a wheel bearing apparatus of claim 1 in which the bottom portion extending radially inward from said pilot portion is formed integrally.
JP2010077968A 2009-04-02 2010-03-30 Wheel bearing device Expired - Fee Related JP5476178B2 (en)

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